Steam distillation apparatus, method, and system

Abstract

To provide a steam distillation system for producing clean water by purifying water.SOLUTION: A fluid steam distillation system is provided, the system comprises: a control system for controlling the fluid steam distillation device, the control system comprising, a release valve, a raw material flow controller for controlling a raw material flow rate valve, and a discharge level sensor connected to the release controller and the raw material flow rate controller. The discharge level sensor transmits a signal related to a discharge level to the discharge controller and the raw material flow rate controller which indicates the discharge level, the raw material flow rate controller drives the raw material flow rate valve on the basis of at least the discharge level sensor signal. The discharge controller drives the discharge valve on the basis of at least the discharge level sensor signal, and the discharge level and the raw material flow rate level are held by using the discharge level sensor signal as input.SELECTED DRAWING: Figure 75

Description

[Technical Field]

[0001] The present invention relates to water distillation, and more specifically to steam distillation apparatus, methods, and systems. [Background technology]

[0002] Reliable sources of clean water are difficult to secure for the majority of humanity. For example, Canada's Agency for International Development reports that approximately 1.2 billion people lack access to safe drinking water. The report estimates that millions of deaths each year, the majority of which are children, are attributable to waterborne diseases. Many water purification technologies are well-known, including carbon filters, chlorine treatment, pasteurization, and reverse osmosis. Many of these technologies are significantly affected by water quality fluctuations and do not address a wide variety of common contaminants, such as bacteria, viruses, organic matter, arsenic, lead, mercury, and pesticides, which may be found in water supplies in the developing world and elsewhere. Some of these systems require the use of consumables such as filters or chemicals. Furthermore, some of these technologies are only suitable for centralized, large-scale water systems that require both considerable infrastructure and highly trained operators. The ability to produce reliable clean water at smaller, more decentralized scales, regardless of the water source, without the need for consumables and constant maintenance, is highly desirable, especially in the developing world. [Overview of the Initiative] [Problems that the invention aims to solve]

[0003] The use of steam compression distillation for water purification is well known and can address many of these concerns. However, limited financial resources, limited technological assets, and low population density that makes it unfeasible to construct centralized, large-scale water systems in much of the developing world also limit the availability of inexpensive and reliable electricity sufficient to operate steam compression distillation systems, as well as hindering the ability to properly maintain such systems. In such circumstances, improved steam compression distillation systems and related components can offer solutions, increasing efficiency and production capacity while reducing the amount of electricity costs required for system operation and the amount of system maintenance required. [Means for solving the problem]

[0004] According to one aspect of the present invention, a fluid vapor distillation system is disclosed. The system includes a control system for controlling a fluid vapor distillation apparatus, which includes a discharge controller for controlling a discharge valve, a raw material flow controller for controlling a raw material flow valve, and a discharge level sensor connected to the discharge controller and the raw material flow controller, wherein the discharge level sensor sends a signal relating to the discharge level to the discharge controller and the raw material flow controller which displays the discharge level, the raw material flow controller drives the raw material flow valve based at least on the discharge level sensor signal, and the discharge level and raw material flow level are maintained by using the discharge level sensor signal as input.

[0005] In some embodiments of this aspect of the present invention, the control system includes at least one controller, and the control system includes one or more of the following states: an idle state in which the at least one controller is not operating; an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid vapor distillation apparatus; a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature; a heat exchanger maximum state in which the raw material valve is opened and a predetermined load cycle is set; a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started; and an operating state in which the fluid vapor distillation apparatus produces product water. The system further includes a raw material fluid inlet, an evaporator / condenser apparatus having a substantially cylindrical housing, and several tubes within the housing, the raw material fluid inlet being fluidically connected to the evaporator / condenser which converts the raw material fluid into steam and the compressed steam into a product fluid, a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet, this heat exchanger including an outer tube and at least one inner tube, a regenerative blower fluidly connected to the evaporator / condenser which compresses the steam, the compressed steam flows to the evaporator / condenser and the compressed steam is converted into a product fluid. The heat exchanger is positioned around the housing of the evaporator / condenser. The outer tube included in the heat exchanger is the raw material fluid flow path, and at least one inner tube is the product fluid flow path. The heat exchanger further includes at least three inner tubes, these at least three inner tubes twisted together to form a substantially helical shape. The heat exchanger includes two ends, each fitted with a connector which forms a joint with the evaporator / condenser. The evaporator / condenser tubes further include packing inside the tubes. The packing is rods. The evaporator / condenser further includes a steam chamber which is fluidly connected to a plurality of tubes. The regenerative blower further includes an impeller assembly which is driven by a magnetically driven coupling. The control system includes at least two processors, namely a motor-controlled engine processor and an ARM® processor. The fluid vapor distillation apparatus further includes a conductivity meter and conductivity cell for measuring the conductivity of the production fluid.

[0006] In another aspect of the present invention, a fluid vapor distillation apparatus is disclosed. The apparatus comprises a feed fluid inlet, an evaporator-condenser apparatus having a substantially cylindrical housing, and a plurality of tubes within the housing, wherein the feed fluid inlet is fluidly connected to the evaporator-condenser, the evaporator-condenser converts feed fluid into vapor and converts compressed vapor into product fluid, a heat exchanger is fluidly connected to the feed fluid inlet and the product fluid outlet, the heat exchanger comprises an outer tube and at least one inner tube, a regeneration blower is fluidly connected to the evaporator-condenser, the regeneration blower compresses the vapor, the compressed vapor flows to the evaporator-condenser, and the compressed vapor is converted into product fluid, a control system for controlling the fluid vapor distillation apparatus comprises a discharge controller configured to control a discharge valve, a feed flow rate controller configured to control a feed flow rate valve, and a discharge level sensor in communication with the discharge controller and the feed flow rate controller, the discharge level sensor transmits a signal relating to a discharge level to the discharge controller and the feed flow rate controller that displays the discharge level, the feed flow rate controller drives the feed flow rate valve based at least on the signal from the discharge level sensor, and the discharge controller drives the discharge valve based at least on the signal from the discharge level sensor, whereby the discharge level and the feed flow rate level are maintained using the signal from the discharge level sensor as an input.

[0007] In some embodiments of this aspect of the present invention, the present invention includes one or more of the following states: at least one controller; an idle state in which the at least one controller is not operating; an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid vapor distillation apparatus; a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature; a heat exchanger peak state in which the raw material valve is opened and set to a predetermined load cycle; a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started; and an operating state in which the fluid vapor distillation apparatus produces product water. The heat exchanger is arranged around the housing of the evaporator-condenser. The outer tubes included in the heat exchanger are raw material fluid passages, and at least one inner tube is a product fluid passage. The heat exchanger further includes at least three inner tubes. These at least three inner tubes are twisted together to form a substantially helical shape. The heat exchanger includes two ends, each end of which is fitted with a connector that forms a joint with the evaporator-condenser. The tubes of the evaporator-condenser further include packing inside the tubes. The packing is rods. The evaporator / condenser further includes a steam chamber fluidly connected to a plurality of tubes. The regenerative blower further includes an impeller assembly driven by a magnetically driven coupling. The control system includes at least two processors, namely a motor-controlled engine processor and an ARM® processor. The fluid vapor distillation apparatus further includes a conductivity meter and a conductivity cell for measuring the conductivity of the production fluid.

[0008] According to one aspect of the present invention, a fluid vapor distillation apparatus is disclosed. This apparatus includes a raw material fluid inlet, an evaporator-condenser apparatus having a substantially cylindrical housing, and a plurality of tubes in the housing, the raw material fluid inlet being fluidically connected to the evaporator-condenser which converts the raw material fluid into vapor and the compressed vapor into a product fluid, a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet which includes an outer tube and at least one inner tube, a regenerative blower fluidly connected to the evaporator-condenser which compresses the vapor, the compressed vapor flows to the evaporator-condenser which the compressed vapor is converted into a product fluid, and the apparatus also includes a control system for controlling the fluid vapor distillation apparatus.

[0009] Some embodiments of this aspect of the invention include one or more of the following. That is, the control system includes a discharge controller that controls a discharge valve, a raw material flow controller that controls a raw material flow valve, and a discharge level sensor that communicates with the discharge controller and the raw material flow controller, wherein the discharge level sensor sends a signal regarding the discharge level to the discharge controller and the raw material flow controller which display the discharge level, the raw material flow controller drives the raw material flow valve based on at least the signal from the discharge level sensor, and the discharge controller drives the discharge valve based on at least the signal from the discharge level sensor, thereby maintaining the discharge level and raw material flow level using the signal from the discharge level sensor as input. The control system includes at least one controller, and the states include an idle state in which at least one controller is not operating, an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid vapor distillation apparatus, a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature, a heat exchanger maximum state in which the raw material valve is opened and set to a predetermined load cycle, a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started, and an operating state in which the fluid vapor distillation apparatus produces product water. The heat exchanger is arranged around the housing of the evaporator and condenser. The heat exchanger includes an outer tube which is a raw material fluid passage and at least one inner tube which is a product fluid passage. The heat exchanger further includes at least three inner tubes which are joined together to form a substantially helical shape. The heat exchanger further includes two ends to which connectors are attached to form joints with the evaporator / condenser. The evaporator / condenser tubes further include packing inside the tubes which is a rod. The evaporator / condenser further includes a steam chamber which is fluidly connected to multiple tubes. The regenerative blower further includes an impeller assembly which is driven by a magnetically driven coupling. The control system includes at least two processors, namely a motor-controlled engine processor and an ARM® processor. The fluid vapor distillation apparatus further includes a conductivity meter and conductivity cell for measuring the conductivity of the product fluid.

[0010] According to one aspect of the present invention, a steam distillation system is disclosed. The system includes a steam distillation apparatus including a raw material fluid inlet, an evaporator-condenser apparatus including a substantially cylindrical housing, and a plurality of tubes in the housing, the raw material fluid inlet being fluidically connected to the evaporator-condenser, the evaporator-condenser converting the raw material fluid into steam and the compressed steam into a product fluid, the system further includes a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet, the heat exchanger including an outer tube and at least one inner tube, and the system includes a regenerative blower fluidly connected to the evaporator-condenser, the regenerative blower compressing steam, the compressed steam flowing to the evaporator-condenser, the compressed steam being converted into a product fluid, and the system also includes a control system for controlling the steam distillation apparatus, and a Stirling engine electrically connected to the steam distillation apparatus, the Stirling engine supplying power to the steam distillation apparatus at least partially.

[0011] Some embodiments of this aspect of the present invention include one or more of the following cases. That is, the control system includes a discharge controller that controls a discharge valve, a raw material flow controller that controls a raw material flow valve, and a discharge level sensor that communicates with the discharge controller and the raw material flow controller, wherein the discharge level sensor sends a signal regarding the discharge level to the discharge controller and the raw material flow controller which display the discharge level, the raw material flow controller drives the raw material flow valve based on at least the signal from the discharge level sensor, and the discharge controller drives the discharge valve based on at least the signal from the discharge level sensor, thereby maintaining the discharge level and raw material flow level using the signal from the discharge level sensor as input. The system that controls the apparatus further includes at least one controller, and the system includes an idle state in which this at least one controller is not operating, an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid vapor distillation apparatus, a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature, a heat exchanger maximum state in which the raw material valve is opened and set to a predetermined load cycle, a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started, and an operating state in which the fluid vapor distillation apparatus produces product water. The Stirling engine includes at least one locking drive mechanism including a locking beam having a rocker pivot, at least one cylinder, and at least one piston, the piston being housed in each cylinder and capable of substantially linearly reciprocating motion within each cylinder, and further includes at least one coupling assembly having a proximal end and a distal end, the proximal end being connected to the piston and the distal end being connected to the locking beam by an end pivot, the linear motion of the piston being converted into rotational motion of the locking beam, and further includes a crankcase housing the locking beam and a first part of the coupling assembly, a crankshaft connected to the locking beam by a connecting rod, the rotational motion of the locking beam being transmitted to the crankshaft, and further includes an operating space housing at least one cylinder, at least one piston, and a second part of the coupling assembly, and a seal for sealing the operating space from the crankcase.

[0012] In some embodiments of this system, one or more of the following cases are included: namely, when the seal is a rolling diaphragm; when the coupling assembly further includes a piston rod and a link rod, and the piston rod and the link rod are coupled together by coupling means; and when the system further includes a lubrication fluid pump in the crankcase.

[0013] Various embodiments of the system include one or more of the following cases: namely, when the heat exchanger is positioned around the housing of the evaporator / condenser; when the outer tube of the heat exchanger is a raw material fluid passage and at least one inner tube is a product fluid passage; or when the heat exchanger further comprises at least three inner tubes.

[0014] According to one aspect of the present invention, a steam distillation apparatus is disclosed. The apparatus includes a discharge controller for controlling a discharge valve, a raw material flow controller for controlling a raw material flow valve, and a discharge level sensor that communicates with the discharge controller and the raw material flow controller, the discharge level sensor sending signals relating to the discharge level to the discharge controller and the raw material flow controller which display the discharge level, the raw material flow controller driving the raw material flow valve based at least on the signals from the discharge level sensor, and the discharge controller driving the discharge valve based at least on the signals from the discharge level sensor, thereby maintaining the discharge level and raw material flow level using the signals from the discharge level sensor as input.

[0015] Some embodiments of this aspect of the present invention include one or more of the following cases: namely, the apparatus further includes at least one controller, and the apparatus includes an idle state in which the at least one controller is not operating; an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid vapor distillation apparatus; a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature; a heat exchanger maximum state in which the raw material valve is opened and set to a predetermined load cycle; a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started; and an operating state in which the fluid vapor distillation apparatus produces product water. The apparatus includes a raw material fluid inlet, an evaporator / condenser apparatus including a substantially cylindrical housing, and a number of tubes within the housing, the raw material fluid inlet being fluidically connected to the evaporator / condenser, the evaporator / condenser converting the raw material fluid into steam and the compressed steam into a product fluid, and the apparatus further includes a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet, the heat exchanger including an outer tube and at least one inner tube, and the apparatus includes a regenerative blower fluidly connected to the evaporator / condenser, the regenerative blower compressing steam, the compressed steam flowing to the evaporator / condenser, and the compressed steam being converted into a product fluid. The heat exchanger is positioned around the housing of the evaporator / condenser. The outer tube included in the heat exchanger is a raw material fluid passage, and at least one inner tube is a product fluid passage. The heat exchanger further includes at least three inner tubes, and these at least three inner tubes are twisted together to form a substantially helical shape. The heat exchanger includes two ends, each end of which is fitted with a connector, the connectors forming a joint with the evaporator / condenser. The evaporator / condenser tubes further include packing material inside the tubes, if the packing material is rods. The evaporator / condenser further includes a steam chamber that is fluidly connected to multiple tubes. The regenerative blower further includes an impeller assembly driven by a magnetically driven coupling. The control system includes at least two processors, namely a motor-controlled engine processor and an ARM® processor. The fluid vapor distillation apparatus further includes a conductivity meter and conductivity cell for measuring the conductivity of the production fluid.

[0016] According to one aspect of the present invention, a steam distillation apparatus is disclosed. The apparatus includes a control system for controlling the steam distillation apparatus, the control system including at least one controller, an idle state in which the at least one controller is not operating, an injection state in which the raw material valve is open and the raw material fluid enters the reservoir of the fluid steam distillation apparatus, a heating state in which the heater in the reservoir is set to maximum output until the fluid in the reservoir reaches a predetermined temperature, a heat exchanger maximum state in which the raw material valve is opened and set to a predetermined load cycle, a start pump state in which the bearing feed pump is driven at a predetermined speed and the discharge motor is started, and an operating state in which the fluid steam distillation apparatus produces product water.

[0017] Some embodiments of this aspect of the present invention include one or more of the following: namely, the control system further includes a discharge controller that controls a discharge valve, a raw material flow controller that controls a raw material flow valve, and a discharge level sensor that communicates with the discharge controller and the raw material flow controller, wherein the discharge level sensor sends a signal relating to the discharge level to the discharge controller and the raw material flow controller which display the discharge level, the raw material flow controller drives the raw material flow valve based on at least the signal from the discharge level sensor, and the discharge controller drives the discharge valve based on at least the signal from the discharge level sensor, thereby maintaining the discharge level and the raw material flow level using the signal from the discharge level sensor as input. The apparatus includes a raw material fluid inlet, an evaporator / condenser apparatus including a substantially cylindrical housing, and a number of tubes within the housing, the raw material fluid inlet being fluidically connected to the evaporator / condenser, the evaporator / condenser converting the raw material fluid into steam and the compressed steam into a product fluid, and the apparatus further includes a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet, the heat exchanger including an outer tube and at least one inner tube, and the apparatus includes a regenerative blower fluidly connected to the evaporator / condenser, the regenerative blower compressing steam, the compressed steam flowing to the evaporator / condenser, and the compressed steam being converted into a product fluid. The heat exchanger is positioned around the housing of the evaporator / condenser. The outer tube included in the heat exchanger is a raw material fluid passage, and at least one inner tube is a product fluid passage. The heat exchanger further includes at least three inner tubes, and these at least three inner tubes are twisted together to form a substantially helical shape. If the heat exchanger further includes two ends, each end of which is fitted with a connector, the connectors forming a joint with the evaporator / condenser. If the evaporator / condenser tubes further include packing inside the tubes, the packing being rods. If the evaporator / condenser further includes a steam chamber that is fluidly connected to multiple tubes. If the regenerative blower further includes an impeller assembly driven by a magnetically driven coupling. If the control system includes at least two processors, namely a motor control engine processor and an ARM® processor.This is the case when the fluid vapor distillation apparatus further includes a conductivity meter and a conductivity cell for measuring the conductivity of the production material.

[0018] According to one aspect of the present invention, a fluid vapor distillation apparatus is disclosed. This apparatus includes a raw material fluid inlet and an evaporator-condenser apparatus. The evaporator-condenser apparatus includes a substantially cylindrical housing and a plurality of tubes within the housing. The raw material fluid inlet is fluidically connected to the evaporator-condenser, which converts the raw material fluid into vapor and the compressed vapor into a product fluid. The fluid vapor distillation apparatus also includes a heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet. The heat exchanger includes an outer tube and at least one inner tube. The fluid vapor distillation apparatus also includes a regenerative blower fluidly connected to the evaporator-condenser. The regenerative blower compresses the vapor, which flows to the evaporator-condenser, where the compressed vapor is converted into a product fluid. The fluid vapor distillation apparatus also includes a control system.

[0019] Some embodiments of this aspect of the present invention include one or more of the following: the heat exchanger is positioned around the housing of an evaporator / condenser, the heat exchanger further includes a heat exchanger in which the outer tube is a fluid passage and at least one inner tube is a product fluid passage; the heat exchanger further includes at least three inner tubes, in which the at least three inner tubes are wound to form a substantially helical shape; the heat exchanger further includes two ends, at which connectors are attached, forming a connection to the evaporator / condenser; the evaporator / condenser tube further includes an inner packing, in which the packing is a rod; the evaporator / condenser further includes a steam chamber that is fluidly connected to a plurality of tubes; and the regenerative blower further includes an impeller assembly driven by a magnetically driven coupling.

[0020] In another aspect of the present invention, a steam distillation system is disclosed. The steam distillation system comprises a raw material fluid input section and an evaporator-condenser apparatus. The evaporator-condenser apparatus includes a substantially cylindrical housing and a plurality of tubes within the housing. The raw material fluid input section is fluidically connected to the evaporator-condenser, which converts the raw material fluid into steam and the compressed steam into a product fluid. The steam distillation apparatus also includes a heat exchanger fluidly connected to the raw material fluid input section and the product fluid output section. The heat exchanger includes an outer tube and at least one inner tube. The steam distillation apparatus also includes a regenerative blower fluidly connected to the evaporator-condenser. The regenerative blower compresses the steam, which flows to the evaporator-condenser, where the compressed steam is converted into a product fluid.

[0021] The steam distillation system also includes a Stirling engine electrically connected to the steam distillation apparatus. The Stirling engine supplies power to the steam distillation apparatus, at least partially.

[0022] Some embodiments of this aspect of the present invention include cases in which a Stirling engine includes at least one locking drive mechanism, the locking drive mechanism includes a locking beam having a rocker pivot, at least one cylinder, and at least one piston. The piston is housed in each cylinder. The piston is capable of substantially linear reciprocating motion within each cylinder. The drive mechanism also includes at least one coupling assembly having a proximal end and a distal end. The proximal end is connected to the piston, and the distal end is connected to the locking beam by an end pivot. The linear motion of the piston is converted into rotational motion of the locking beam. Also included is a crankcase that houses the locking beam and a first part of the coupling assembly. Also included is a crankshaft connected to the locking beam by a connecting rod. The rotational motion of the locking beam is transmitted to the crankshaft. The machine also includes an operating space that houses at least one cylinder, at least one piston, and a second part of a coupling assembly. A seal is included to seal the operating space away from the crankcase.

[0023] In addition, some embodiments of this aspect of the present invention include one or more of the following: the seal is a rolling diaphragm; the coupling assembly further includes a piston rod and a link rod; the piston rod and the link rod are coupled together by a coupling means; the heat exchanger is arranged around the housing of the evaporator / condenser; the heat exchanger further includes an outer tube which is a fluid passage and at least one inner tube which is a product fluid passage; the heat exchanger further comprises at least three inner tubes; the evaporator / condenser further comprises a steam chamber which is fluidly connected to a plurality of tubes; and the regenerative blower further comprises an impeller assembly which is driven by a magnetically driven coupling.

[0024] These aspects of the present invention are not intended to be exclusive, and other features, aspects, and advantages of the present invention will be readily apparent to those skilled in the art when read in conjunction with the accompanying claims and drawings. [Brief explanation of the drawing]

[0025] These and other features and advantages of the present invention will be better understood by reading the following embodiments for carrying out the invention in conjunction with the drawings. [Figure 1] Figure 1 is an isometric view of a steam distillation apparatus. [Figure 1A] Figure 1A is an exploded view of an exemplary embodiment of the present disclosure. [Figure 1B] Figure 1B is a cross-sectional view of an exemplary embodiment. [Figure 1C] Figure 1C is a cross-sectional view of an exemplary embodiment. [Figure 1D] Figure 1D is an assembly diagram of an exemplary embodiment. [Figure 1E] Figure 1E is a detail view of an exemplary embodiment of the frame. [Figure 1F] Figure 1F is an assembly diagram of an alternative embodiment. [Figure 1G] Figure 1G is an assembly diagram of an alternative embodiment. [Figure 1H] Figure 1H is an assembly diagram of an alternative embodiment. [Figure 2] Figure 2 is an assembly diagram of an exemplary embodiment of a tube-in-tube heat exchanger assembly. [Figure 2A] Figure 2A is an exploded view of one embodiment of a tube-in-tube heat exchanger. [Figure 2B] Figure 2B is a rear isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2C] Figure 2C is an isometric view from the front of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2D] Figure 2D is a cross-sectional view of one embodiment of a tube-in-tube heat exchanger. [Figure 2E] Figure 2E is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger. [Figure 2F] Figure 2F is a cross-sectional view of one embodiment of a tube-in-tube heat exchanger, illustrating the helical arrangement of the inner tubes. [Figure 2G] Figure 2G is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger. [Figure 2H] Figure 2H is an isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2I] Figure 2I is an isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2J] Figure 2J is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2K] Figure 2K is an assembly diagram of an alternative embodiment of the tube-in-tube heat exchanger configuration. [Figure 2L] Figure 2L is an assembly diagram of an alternative embodiment of the tube-in-tube heat exchanger configuration. [Figure 2M] Figure 2M is a detailed diagram of an alternative embodiment of the tube-in-tube heat exchanger configuration. [Figure 2N] Figure 2N is a detailed diagram of an alternative embodiment of the tube-in-tube heat exchanger configuration. [Figure 2O]Figure 2O is a schematic diagram of an alternative embodiment of the tube-in-tube heat exchanger configuration. [Figure 2P] Figure 2P is an assembly diagram of an alternative embodiment of the heat exchanger. [Figure 2Q] Figure 2Q is an exploded view of an alternative embodiment of the heat exchanger. [Figure 2R] Figure 2R is a cross-sectional view of an alternative embodiment of the heat exchanger. [Figure 3] Figure 3 is an exploded view of a connector for a mounting assembly that is installed on a tube-in-tube heat exchanger. [Figure 3A] Figure 3A is a cross-sectional view of the mounting assembly for a tube-in-tube heat exchanger. [Figure 3B] Figure 3B is a cross-sectional view of the mounting assembly for a tube-in-tube heat exchanger. [Figure 3C] Figure 3C is an isometric view of an exemplary embodiment of the first connector. [Figure 3D] Figure 3D is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3E] Figure 3E is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3F] Figure 3F is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3G] Figure 3G is an isometric view of an exemplary embodiment of the second connector. [Figure 3H] Figure 3H is a cross-sectional view of the mounting assembly for a tube-in-tube heat exchanger. [Figure 3I] Figure 3I is a cross-sectional view of an exemplary embodiment of the second connector. [Figure 3J] Figure 3J is a cross-sectional view of an exemplary embodiment of the second connector. [Figure 4] Figure 4 is an isometric view of an exemplary embodiment of the evaporator / condenser assembly. [Figure 4A] Figure 4A is a cross-sectional view of an exemplary embodiment of the evaporator / condenser assembly. [Figure 4B] Figure 4B is an isometric cross-sectional view of an exemplary embodiment of the evaporator / condenser. [Figure 4C] Figure 4C is an isometric view of an alternative embodiment of the evaporator / condenser assembly. [Figure 5] Figure 5 is an assembly diagram of an exemplary embodiment of a water reservoir. [Figure 5A] Figure 5A is an exploded view of an exemplary embodiment of a water reservoir. [Figure 6] Figure 6 is an isometric detail view of the flange for the water reservoir assembly. [Figure 7] Figure 7 is an exploded view of an exemplary embodiment of the evaporator / condenser. [Figure 7A] Figure 7A is a top view of an exemplary embodiment of the evaporator / condenser assembly. [Figure 7B] Figure 7B shows the percentage of the evaporator's distillate output as a function of pressure for several liquid boiling modes. [Figure 8] Figure 8 is an isometric view of an exemplary embodiment of tubing for an evaporator / condenser. [Figure 9] Figure 9 is an exploded view of the tubing and rod configuration for the evaporator / condenser. [Figure 9A] Figure 9A is an isometric view of an exemplary embodiment of a rod for an evaporator / condenser. [Figure 10] Figure 10 is an isometric view of an exemplary embodiment of a water reservoir plate. [Figure 10A] Figure 10A is an isometric view of an exemplary embodiment of the upper tube sheet. [Figure 11] Figure 11 is a detailed view of the top cap for the evaporator / condenser. [Figure 12] Figure 12 is an isometric view of an exemplary embodiment of a steam chamber. [Figure 12A] Figure 12A is an isometric view of an exemplary embodiment of a steam chamber. [Figure 12B] Figure 12B is a cross-sectional view of an exemplary embodiment of a steam chamber. [Figure 12C] Figure 12C is an exploded view of an exemplary embodiment of a steam chamber. [Figure 12D] Figure 12D is an isometric view of an alternative embodiment. [Figure 12E]Figure 12E is a cross-sectional view of an exemplary embodiment of a steam chamber. [Figure 12F] Figure 12F is a cross-sectional view of an exemplary embodiment of a steam chamber. [Figure 13] Figure 13 is an assembly diagram of an alternative embodiment of the evaporator / condenser. [Figure 13A] Figure 13A is a cross-sectional view of an alternative embodiment of the evaporator / condenser. [Figure 13B] Figure 13B is an assembly diagram of an alternative embodiment of the evaporator / condenser, illustrating the arrangement of the tubing. [Figure 13C] Figure 13C is a cross-sectional view of an alternative embodiment of the evaporator / condenser, illustrating the arrangement of the tubing. [Figure 13D] Figure 13D is an isometric view of an alternative embodiment of an evaporator / condenser without a water reservoir. [Figure 13E] Figure 13E is an exploded view of an alternative embodiment of the evaporator / condenser. [Figure 14] Figure 14 is an isometric view of the mist removal assembly. [Figure 14A] Figure 14A is an isometric view of the outside of the cap for the mist remover. [Figure 14B] Figure 14B is an isometric view of the inside of the cap for the mist remover. [Figure 14C] Figure 14C is a cross-sectional view of the mist remover assembly. [Figure 14D] Figure 14D is a cross-sectional view of the mist remover assembly. [Figure 15] Figure 15 is an assembly diagram of an exemplary embodiment of a regeneration blower. [Figure 15A] Figure 15A is a bottom view of an exemplary embodiment of a regeneration blower assembly. [Figure 15B] Figure 15B is a top view of an exemplary embodiment of a regeneration blower assembly. [Figure 15C] Figure 15C is an exploded view of an exemplary embodiment of a regenerative blower. [Figure 15D] Figure 15D is a detail view of the upper outer surface of the housing for an exemplary embodiment of the regenerative blower. [Figure 15E]Figure 15E is a detailed view of the upper inner surface of the housing for an exemplary embodiment of the regenerative blower. [Figure 15F] Figure 15F is a detailed view of the inner surface of the lower part of the housing for an exemplary embodiment of the regenerative blower. [Figure 15G] Figure 15G is a detailed view of the lower outer surface of the housing for an exemplary embodiment of the regenerative blower. [Figure 15H] Figure 15H is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15I] Figure 15I is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15J] Figure 15J is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15K] Figure 15K is a schematic diagram of an exemplary embodiment of a regeneration blower assembly. [Figure 15L] Figure 15L is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 16] Figure 16 is a detail view of the impeller assembly of an exemplary embodiment of a regenerating blower. [Figure 16A] Figure 16A is a cross-sectional view of the impeller assembly. [Figure 17] Figure 17 is an assembly diagram of an alternative embodiment of the regenerative blower. [Figure 17A] Figure 17A is an assembly diagram of an alternative embodiment of the regenerative blower. [Figure 17B] Figure 17B is a cross-sectional view of an alternative embodiment of the regenerative blower assembly. [Figure 17C] Figure 17C is a cross-sectional view of an alternative embodiment of the regenerative blower assembly. [Figure 17D] Figure 17D is a cross-sectional view of an alternative embodiment of the regenerative blower assembly. [Figure 17E] Figure 17E is an exploded view of an alternative embodiment of the regenerative blower. [Figure 17F] Figure 17F is an assembly diagram of the impeller housing. [Figure 17G] Figure 17G is an exploded view of the impeller housing. [Figure 17H]Figure 17H ​​is a cross-sectional view of an alternative embodiment of the impeller housing assembly. [Figure 17I] Figure 17I is a cross-sectional view of an alternative embodiment of the impeller housing assembly. [Figure 17J] Figure 17J is a bottom view of the lower part of the impeller housing. [Figure 17K] Figure 17K is a detailed view of the inner surface of the lower part of the impeller housing. [Figure 17L] Figure 17L is a top view of the upper part of the impeller housing assembly. [Figure 17M] Figure 17M is a top view of the upper part of the housing for the impeller assembly without the cover installed. [Figure 17N] Figure 17N is a detailed view of the upper inner surface of the housing for the impeller assembly. [Figure 18] Figure 18 is a detailed view of the impeller assembly for an alternative embodiment of the regenerative blower. [Figure 18A] Figure 18A is a cross-sectional view of the impeller assembly. [Figure 19] Figure 19 is an assembly diagram of the level sensor assembly. [Figure 19A] Figure 19A is an exploded view of an exemplary embodiment of a level sensor assembly. [Figure 19B] Figure 19B is a cross-sectional view of the sedimentation tank inside the level sensor housing. [Figure 19C] Figure 19C is a cross-sectional view of the discharge sensor and product level sensor storage section within the level sensor housing. [Figure 19D] Figure 19D is an assembly diagram of an alternative embodiment of the level sensor assembly. [Figure 19E] Figure 19E is an exploded view of an alternative embodiment of the level sensor assembly. [Figure 19F] Figure 19F is a cross-sectional view of an alternative embodiment of the level sensor assembly. [Figure 19G] Figure 19G is a schematic diagram of the operation of the level sensor assembly. [Figure 19H] Figure 19H shows an alternative embodiment of the level sensor assembly. [Figure 20] Figure 20 is an isometric view of the level sensor assembly. [Figure 20A] Figure 20A is a cross-sectional view of the level sensor assembly. [Figure 21] Figure 21 is an isometric view of the front of the bearing water supply pump. [Figure 21A] Figure 21A is an isometric view of the back of the bearing water supply pump. [Figure 22] Figure 22 is a schematic diagram of the source water flow path for an exemplary embodiment of a steam distillation apparatus. [Figure 22A] Figure 22A is a schematic diagram of the source water entering the heat exchanger. [Figure 22B] Figure 22B is a schematic diagram of the source water passing through the heat exchanger. [Figure 22C] Figure 22C is a schematic diagram of the source water exiting the heat exchanger. [Figure 22D] Figure 22D is a schematic diagram of the source water passing through the regeneration blower. [Figure 22E] Figure 22E is a schematic diagram of the source water exiting and entering the regeneration blower. [Figure 23] Figure 23 is a schematic diagram of the discharge water flow path for an exemplary embodiment of a steam distillation apparatus. [Figure 23A] Figure 23A is a schematic diagram of discharged water exiting the evaporator / condenser assembly and entering the level sensor housing. [Figure 23B] Figure 23B is a schematic diagram of the discharged water filling the sedimentation tank inside the level sensor housing. [Figure 23C] Figure 23C is a schematic diagram of the discharge water filling the discharge level sensor storage section within the level sensor housing. [Figure 23D] Figure 23D is a schematic diagram of the discharged water exiting the level sensor housing and entering the strainer. [Figure 23E] Figure 23E is a schematic diagram of discharged water exiting the strainer and entering the heat exchanger. [Figure 23F] Figure 23F is a schematic diagram of the discharged water passing through the heat exchanger. [Figure 23G]Figure 23G is a schematic diagram of the discharged water exiting the heat exchanger. [Figure 24] Figure 24 is a schematic diagram of the water flow path for an exemplary embodiment of a steam distillation apparatus. [Figure 24A] Figure 24A is a schematic diagram of the produced water exiting the evaporator / condenser assembly and entering the level sensor housing. [Figure 24B] Figure 24B is a schematic diagram showing the production water entering the product level sensor storage section within the level sensor housing. [Figure 24C] Figure 24C is a schematic diagram of the produced water exiting the product level sensor storage unit and entering the heat exchanger. [Figure 24D] Figure 24D is a schematic diagram of the produced water passing through the heat exchanger. [Figure 24E] Figure 24E is a schematic diagram of the produced water exiting the heat exchanger. [Figure 24F] Figure 24F is a schematic diagram of the production water entering the bearing water supply storage section within the level sensor housing. [Figure 24G] Figure 24G is a schematic diagram of the produced water exiting the level sensor housing and entering the bearing-driven water supply pump. [Figure 24H] Figure 24H is a schematic diagram of the produced water exiting the bearing water supply pump and entering the regeneration blower. [Figure 24I] Figure 24I is a schematic diagram of the produced water exiting the regeneration blower and entering the level sensor housing. [Figure 25] Figure 25 is a schematic diagram of a vent passage for an exemplary embodiment of a steam distillation apparatus. [Figure 25A] Figure 25A is a schematic diagram of the ventilation path that allows air to exit the release sensor storage unit and enter the evaporator condenser. [Figure 25B] Figure 25B is a schematic diagram of the ventilation passage that allows air to exit the product sensor storage unit and enter the evaporator / condenser. [Figure 25C] Figure 25C is a schematic diagram of the vent that allows air to exit the evaporator / condenser assembly. [Figure 26]Figure 26 is a schematic diagram of low-pressure steam entering the tubing of the evaporator / condenser assembly from the reservoir. [Figure 26A] Figure 26A is a schematic diagram of low-pressure steam passing through the tubing of the evaporator / condenser assembly. [Figure 26B] Figure 26B is a schematic diagram of moist low-pressure steam exiting the evaporator / condenser assembly tubing and entering the steam chamber. [Figure 26C] Figure 26C is a schematic diagram of moist low-pressure steam flowing through the steam chamber of the evaporator / condenser assembly. [Figure 26D] Figure 26D is a schematic diagram of the generation of discharged water as low-pressure steam passing through the steam chamber. [Figure 26E] Figure 26E is a schematic diagram of dry, low-pressure steam exiting the steam chamber and entering the regenerative blower. [Figure 26F] Figure 26F is a schematic diagram of dry low-pressure steam passing through a regenerative blower. [Figure 26G] Figure 26G is a schematic diagram of the high-pressure steam exiting the regenerative blower. [Figure 26H] Figure 26H is a schematic diagram of high-pressure steam entering a steam pipe. [Figure 26I] Figure 26I is a schematic diagram of high-pressure steam exiting the steam pipe and entering the evaporator / condenser chamber. [Figure 26J] Figure 26J is a schematic diagram of the production of water from high-pressure steam condensing in the evaporator / condenser chamber. [Figure 27] Figure 27 is a graph illustrating the relationship between the differential pressure across the regenerative blower and the amount of energy required to produce one liter of product. [Figure 28] Figure 28 is a graph illustrating the relationship between the product yield and the number of heat transfer tubes in the evaporator / condenser assembly. [Figure 29] Figure 29 is a graph illustrating the production rate of produced water from an evaporator / condenser assembly as a function of the amount of heat transfer surface area associated with the evaporator / condenser chamber. [Figure 30]Figure 30 is a graph illustrating the efficiency of the heat transfer surface to a fluctuating amount of heat transfer tubes in the evaporator / condenser assembly as it relates to the pressure change across the regenerative blower. [Figure 31] Figure 31 is a graph illustrating the amount of energy consumed by the evaporator / condenser assembly at different pressure differences across the production rate and regenerative blower. [Figure 32] Figure 32 is a cross-sectional top view of a rotor and stator according to a specific embodiment, showing the support structure for the input section, the blades and the chambers between the blades, and the rotary drive shaft. [Figure 32A] Figure 32A is a side and top view of the rotor and stator, corresponding to the embodiment shown in Figure 32, showing the support structure for the input and output sections, the blades, the eccentric configuration within the housing unit, and the drive shaft. [Figure 32B] Figure 32B is a top view of the rotor and stator, corresponding to the embodiments shown in Figures 32 and 32A, showing the support structures for the input and output sections, the blades, the eccentric configuration within the housing unit, and the drive shaft. [Figure 32C] Figure 32C is a cross-sectional view of the rotor and stator, corresponding to the embodiments shown in Figures 32, 32A, and 32B, showing the blades, drive shaft, and bearings. [Figure 32D] Figure 32D is a cross-sectional view of a liquid-sealed pump according to one embodiment, showing a volume sensor. [Figure 32E] Figure 32E is a cross-sectional view of a liquid-sealed pump according to one embodiment, showing an eccentric rotor, rotor blades, drive shaft with bearings, rotating housing unit for a liquid-sealed pump, stationary housing, and the cyclone effect from steam and the resulting mist and water droplets. [Figure 32F] Figure 32F is a schematic diagram of an alternative embodiment of a liquid-sealed pump. [Figure 32G] Figure 32G is a top view of an alternative embodiment of a rotor, showing multiple blades and chambers between the blades, and the intake and exit holes of each individual chamber. [Figure 32H]Figure 32H shows further details of the liquid-sealed pump, including the static intake port and rotary drive shaft, rotor, and housing unit. [Figure 32I] Figure 32I shows a seal that may be present between the stationary and rotor sections of a liquid-sealed pump, separating the outlet from the inlet. [Figure 33] Figure 33 is a side view of a back pressure regulator according to one embodiment. [Figure 33A] Figure 33A is a diagonal view of the back pressure regulator shown. [Figure 33B] Figure 33B is a side view of an alternative embodiment of a back pressure regulator having vertically arranged ports. [Figure 33C] Figure 33C is a diagonal view of the back pressure regulator shown. [Figure 33D] Figure 33D is a magnified view of section C of Figure 33D, depicting the port cutout of the back pressure regulator. [Figure 33E] Figure 33E is a close-up view of section C in Figure 33D, depicting the ports of the back pressure regulator. [Figure 33F] Figure 33F is a cross-sectional side view of one embodiment of a back pressure regulator. [Figure 33G] Figure 33G is an enlarged view of section E of Figure 33F, depicting the small opening of the back pressure regulator port. [Figure 34] Figure 34 is a schematic diagram of a back pressure regulator implemented within the device. [Figure 35] Figure 35 is a schematic diagram of an alternative embodiment of a steam distillation apparatus. [Figure 35A] Figure 35A is a detailed schematic diagram of an alternative embodiment of the level sensor housing, depicting an external connection valve between the raw material and discharge fluid lines. [Figure 36] Figure 36 is a view of one side of the fluid distribution manifold on the pump side. [Figure 36A] Figure 36A is a view of the second side of the fluid distribution manifold on the pump side. [Figure 36B] Figure 36B is a view of one side of the fluid distribution manifold on the evaporator / condenser side. [Figure 36C]Figure 36C is a view of the second side of the fluid distribution manifold, on the evaporator / condenser side. [Figure 37] Figure 37 is a top view of a coupler in an alternative embodiment of the mounting hardware assembly. [Figure 37A] Figure 37A is a side view of an alternative embodiment of the mounting hardware assembly shown in Figure 37. [Figure 38] Figure 38 is a cross-sectional view of an alternative embodiment of the evaporator / condenser having individual heating layers and ribs. [Figure 38A] Figure 38A is a cross-sectional detail of an alternative embodiment of the evaporator / condenser, showing how the ribs effectively separate the liquid / condensed layer from the vapor / evaporation layer. [Figure 39] Figure 39 is a schematic diagram of an alternative embodiment of the heat exchanger. [Figure 39A] Figure 39A is a schematic diagram of an alternative embodiment of the heat exchanger. [Figure 40] Figure 40 is a schematic overview of an alternative embodiment of a steam distillation apparatus, including pressure measurement of a system using a cold air sensor. [Figure 41] Figure 41 shows a flip filter with intake and discharge flows through the filter units, where each filter unit rotates around a pivot joint around a central axis. [Figure 41A] Figure 41A shows the flip filter housing. [Figure 41B] Figure 41B is a detailed view of the flip filter shown in Figure 41. [Figure 41C] Figure 41C shows an alternative embodiment of the composite flip filter. [Figure 41D] Figure 41D is a schematic diagram of an alternative embodiment of the flip filter. [Figure 41E] Figure 41E is a schematic diagram of the flow path in one embodiment of a flip filter. [Figure 41F] Figure 41F is a schematic diagram illustrating the manual switches for changing the water flow through the individual units of the flip filter shown in Figure 41E. [Figure 42] Figure 42 depicts a monitoring system for a decentralized public facility. [Figure 43] Figure 43 depicts a distribution system for public facilities. [Figure 44] Figure 44 is a conceptual flowchart of a possible embodiment of a system incorporating an alternative steam distillation apparatus. [Figure 44A] Figure 44A is a schematic block diagram of a power supply for use with the system shown in Figure 44. [Figure 45A] Figure 45A illustrates the operating principle of a Stirling cycle machine. [Figure 45B] Figure 45B illustrates the operating principle of a Stirling cycle machine. [Figure 45C] Figure 45C illustrates the operating principle of a Stirling cycle machine. [Figure 45D] Figure 45D illustrates the operating principle of a Stirling cycle machine. [Figure 45E] Figure 45E illustrates the operating principle of a Stirling cycle machine. [Figure 46] Figure 46 shows a diagram of a rocking beam drive according to one embodiment. [Figure 47] Figure 47 shows a diagram of a rocking beam drive according to one embodiment. [Figure 48] Figure 48 shows a diagram of an engine according to one embodiment. [Figure 49A] Figure 49A illustrates various diagrams of a rocking beam drive according to one embodiment. [Figure 49B] Figure 49B illustrates various diagrams of a rocking beam drive according to one embodiment. [Figure 49C] Figure 49C illustrates various diagrams of a rocking beam drive according to one embodiment. [Figure 49D] Figure 49D illustrates various diagrams of a rocking beam drive according to one embodiment. [Figure 50] Figure 50 shows a bearing-type rod connector according to one embodiment. [Figure 51A] Figure 51A shows a bent portion according to one embodiment. [Figure 51B]Figure 51B shows a bent portion according to one embodiment. [Figure 52] Figure 52 shows a four-cylinder double-locking beam drive configuration according to one embodiment. [Figure 53] Figure 53 shows a cross-section of a crankshaft according to one embodiment. [Figure 54A] Figure 54A shows a diagram of an engine according to one embodiment. [Figure 54B] Figure 54B shows a crankshaft coupling according to one embodiment. [Figure 54C] Figure 54C shows a diagram of a sleeve rotor according to one embodiment. [Figure 54D] Figure 54D shows a diagram of a crankshaft according to one embodiment. [Figure 54E] Figure 54E shows a cross-section of a sleeve rotor and spline shaft according to one embodiment. [Figure 54F] Figure 54F shows a cross-section of a crankshaft and a spline shaft according to one embodiment. [Figure 54G] Figure 54G shows various diagrams of a sleeve rotor, crankshaft, and spline shaft according to one embodiment. [Figure 55] Figure 55 shows the operation of an engine piston according to one embodiment. [Figure 56A] Figure 56A shows a schematic diagram of the workspace and cylinder in their unpackaged state according to one embodiment. [Figure 56B] Figure 56B shows a schematic diagram of a cylinder, heater head, and regenerator according to one embodiment. [Figure 56C] Figure 56C shows a cylinder head according to one embodiment. [Figure 57A] Figure 57A shows a rolling diaphragm along with the uppermost support seal piston and the bottom seal piston according to one embodiment. [Figure 57B] Figure 57B is an exploded view of a rocking beam driven engine according to one embodiment. [Figure 57C]Figure 57C shows a diagram of a cylinder, heater head, regenerator, and rolling diaphragm according to one embodiment. [Figure 57D] Figure 57D shows various diagrams of a rolling diaphragm in operation according to one embodiment. [Figure 57E] Figure 57E shows various diagrams of a rolling diaphragm in operation according to one embodiment. [Figure 57F] Figure 57F shows a schematic diagram of the workspace and cylinder in their unpackaged state according to one embodiment. [Figure 57G] Figure 57G shows a diagram of an external combustion engine according to one embodiment. [Figure 58A] Figure 58A shows diagrams of various embodiments of rolling diaphragms. [Figure 58B] Figure 58B shows diagrams of various embodiments of rolling diaphragms. [Figure 58C] Figure 58C shows diagrams of various embodiments of rolling diaphragms. [Figure 58D] Figure 58D shows diagrams of various embodiments of rolling diaphragms. [Figure 58E] Figure 58E shows diagrams of various embodiments of rolling diaphragms. [Figure 59A] Figure 59A shows a metal bellows, along with an associated piston rod and piston, according to one embodiment. [Figure 59B] Figure 59B shows a diagram of a metal bellows diaphragm according to one embodiment. [Figure 59C] Figure 59C shows a diagram of a metal bellows diaphragm according to one embodiment. [Figure 59D] Figure 59D shows a diagram of a metal bellows diaphragm according to one embodiment. [Figure 59E] Figure 59E shows diagrams of metal bellows according to various embodiments. [Figure 59F] Figure 59F shows diagrams of metal bellows according to various embodiments. [Figure 59G] Figure 59G shows diagrams of metal bellows according to various embodiments. [Figure 59H] Figure 59H shows a schematic diagram of a rolling diaphragm that identifies various load regions. [Figure 59I] Figure 59I shows a schematic diagram of a rolling diaphragm that identifies the rotational region. [Figure 60] Figure 60 shows a diagram of a piston and piston seal according to one embodiment. [Figure 61] Figure 61 shows a diagram of a piston rod and a piston rod seal according to one embodiment. [Figure 62A] Figure 62A shows a piston seal backing ring according to one embodiment. [Figure 62B] Figure 62B shows a pressure diagram of the backing ring according to one embodiment. [Figure 62C] Figure 62C shows a piston seal according to one embodiment. [Figure 62D] Figure 662D shows a piston seal according to one embodiment. [Figure 62E] Figure 62E shows a piston rod seal according to one embodiment. [Figure 62F] Figure 62F shows a piston rod seal according to one embodiment. [Figure 63A] Figure 63A shows a piston seal backing ring according to one embodiment. [Figure 63B] Figure 63B shows a pressure diagram of a piston seal backing ring according to one embodiment. [Figure 64A] Figure 64A shows a piston rod seal backing ring according to one embodiment. [Figure 64B] Figure 64B shows a pressure diagram of a piston rod seal backing ring according to one embodiment. [Figure 65] Figure 65 shows a diagram of a piston guide ring according to one embodiment. [Figure 66] Figure 66 shows a schematic diagram of the workspace and cylinder in their unpackaged state according to one embodiment. [Figure 67A] Figure 67A shows a diagram of an engine according to one embodiment. [Figure 67B] Figure 67B shows a diagram of an engine according to one embodiment. [Figure 68] Figure 68 shows a diagram of a crankshaft according to one embodiment. [Figure 69A] Figure 69A shows various configurations of the pump drive unit according to various embodiments. [Figure 69B] Figure 69B shows various configurations of the pump drive unit according to various embodiments. [Figure 69C] Figure 69C shows various configurations of the pump drive unit according to various embodiments. [Figure 70A] Figure 70A shows various diagrams of an oil pump according to one embodiment. [Figure 70B] Figure 70B shows a diagram of an engine according to one embodiment. [Figure 70C] Figure 70C shows another diagram of the engine depicted in Figure 70B. [Figure 71A] Figure 71A shows a diagram of an engine according to one embodiment. [Figure 71B] Figure 71B shows a diagram of an engine according to one embodiment. [Figure 71C] Figure 71C shows a diagram of a connecting joint according to one embodiment. [Figure 71D] Figure 71D shows a diagram of the crankshaft and spline shaft of an engine according to one embodiment. [Figure 72A] Figure 72A shows an explanatory diagram of a generator connected to one embodiment of the device. [Figure 72B] Figure 72B shows a schematic diagram of an auxiliary power unit for supplying power and heat to a steam distillation apparatus. [Figure 72C] Figure 72C shows a schematic diagram of the system according to one embodiment. [Figure 73] Figure 73 is a schematic diagram of the flow path in one embodiment of a steam distillation apparatus. [Figure 74] Figure 74 is an isometric view of one embodiment of a tube-in-tube heat exchanger with one embodiment of a connector attached. [Figure 74A]Figure 74A is an isometric view of one embodiment of the connector shown in Figure 74. [Figure 74B] Figure 74B is a cross-sectional view of one embodiment of the connector shown in Figure 74. [Figure 74C] Figure 74C is an end view of one embodiment of the connector shown in Figure 74. [Figure 75] Figure 75 is a flowchart showing the flow of water. [Figure 76] Figure 76 is a schematic diagram of a communication system with at least one steam distillation apparatus according to one embodiment. [Modes for carrying out the invention]

[0026] Definitions. As used in this description and the attached claims, the following terms shall have the meanings indicated unless the context requires otherwise.

[0027] The term "fluid" is used herein to include any type of fluid, including water. Thus, while exemplary embodiments and various other embodiments are described herein in relation to water, the scope of apparatus, systems, and methods includes any type of fluid. Furthermore, in this specification, the term “liquid” may be used to indicate exemplary embodiments in which the fluid is a liquid.

[0028] The term "evaporator-condenser" is used herein to refer to a device that is a combined evaporator and condenser. Therefore, a structure is called an evaporator-condenser when the structure itself performs both functions. Evaporator-condenser structures are referred herein as evaporator / condenser, evaporator-condenser, or evaporator and condenser. Furthermore, wherever either an evaporator or a condenser is referred to individually, the term should be understood to refer to an evaporator-condenser structure, and not limiting it.

[0029] The term "dirty water" is used herein to refer to any water that is desirable to be purified before consumption.

[0030] In this specification, "cleaner water" refers to water that is cleaner as a product rather than as a source water.

[0031] The term "source water" refers to any water that enters the device.

[0032] The term "production water" refers to the cleaner water that exits the equipment.

[0033] As used herein and in any appended claims, the term “purify step” means a step of reducing the concentration of one or more contaminants, or a step of altering the concentration of one or more contaminants.

[0034] As used herein, the term “specified level” refers to a desired level of concentration established by the user for a particular application. An example of a specified level may be a step to limit the level of a contaminant in a fluid in order to carry out an industrial or commercial process. One example is the step of eliminating the level of a contaminant in a solvent or reactant to an acceptable level that allows for industrially significant benefits in a chemical reaction (e.g., polymerization). Another example of a specified level may be a level of a contaminant in a fluid that is defined by a government or intergovernmental agency for safety or health reasons. Examples may include the concentration of one or more contaminants in water used for drinking or certain health or medical purposes, or concentration levels defined by organizations such as the World Health Organization or the U.S. Environmental Protection Agency.

[0035] As used herein, the term “system” may refer to any combination of elements, including but not limited to a steam distillation apparatus (which may also be called a water system or steam distillation system) and a steam distillation apparatus with a power source such as a Stirling engine.

[0036] This specification discloses an apparatus for distilling contaminated water, known as source water, into cleaner water, known as production water. The apparatus purifies the source water by evaporating the water and separating particulate matter from it. As used herein and in any appended claims, the term “purifying step” means a step of substantially reducing the concentration of one or more contaminants to below a specified level, or a step of substantially altering the concentration of one or more contaminants to within a specified range.

[0037] The source water may first pass through a backflow tube-in-tube heat exchanger to raise its temperature. Raising the source water temperature reduces the amount of thermal energy required to evaporate the water in the evaporator / condenser. The source water may also receive thermal energy from other fluid flows present in the heat exchanger. Typically, these other flows have a higher temperature than the source water, transferring thermal energy from the higher-temperature flows to the lower-temperature source water.

[0038] The evaporator region of the evaporator / condenser assembly receives the heated source water. This assembly evaporates the source water to separate contaminants from the water. Thermal energy may be supplied using a heating element and high-pressure steam. Typically, the heating element is used during initial startup, and therefore, under normal operating conditions, thermal energy is supplied by high-pressure steam. The source water fills the inner tubes of the evaporator region of the evaporator / condenser. As high-pressure steam condenses on the outer surfaces of these tubes, thermal energy is conducted to the source water. This thermal energy evaporates some of the source water into low-pressure steam. After the source water has been converted to low-pressure steam, the steam exits through the tube outlet and may pass through a separator. The separator removes any remaining water droplets in the steam and ensures that the low-pressure steam is dry before entering the compressor.

[0039] As the low-pressure steam exits the evaporator / condenser, it enters the compressor. The compressor generates high-pressure steam by compressing the low-pressure steam. As the steam is compressed, its temperature rises. Once the steam reaches the increased temperature and pressure, it exits the compressor.

[0040] High-pressure steam enters the condenser area of ​​the evaporator / condenser. As the steam fills the internal cavity, it condenses on the tube contained within the cavity. The high-pressure steam transfers thermal energy to the source water inside the tube. This heat transfer causes the steam to condense on the outer surface of the tube, producing product water. The product water is collected at the base of the condenser area of ​​the evaporator / condenser. The product water exits the evaporator area of ​​the evaporator / condenser and enters the level sensor housing.

[0041] The level sensor housing contains level sensors for determining the amount of production water and discharged water within the device. These sensors allow the operator to adjust the amount of production water being produced or the amount of inflow source water according to the water level within the device.

[0042] Steam distillation apparatuses, as described herein in relation to various embodiments, may also be used in conjunction with a Stirling engine to form a steam distillation system. The power required by the steam distillation apparatus may be supplied by a Stirling engine electrically connected to the steam distillation apparatus.

[0043] Referring to Figure 1, one embodiment of the steam distillation apparatus 100 is shown. For the purposes of this description, the embodiment shown in Figure 1 is referred to as an exemplary embodiment. Other embodiments are considered, some of which are discussed herein. The apparatus 100 may include a heat exchanger 102, an evaporator / condenser assembly 104, a regenerative blower 106, a level sensor assembly 108, a bearing feedwater pump 110, and a frame 112. For additional diagrams and cross-sections of the steam distillation apparatus 100, see also Figures 1A-E.

[0044] Referring to Figures 1F-H, these figures illustrate alternative embodiments of the steam distillation apparatus 100. Figure 1F shows apparatus 120 with an alternative configuration of the evaporator / condenser assembly 122. Similarly, Figure 1G discloses apparatus with another configuration of the evaporator / condenser assembly 132. Similarly, Figure 1H illustrates another embodiment of the apparatus without the level sensor assembly 108 and bearing feedwater pump 110 from Figure 1-1E. (heat exchanger) Referring here to Figure 2-2A, in an exemplary embodiment of the steam distillation apparatus, the heat exchanger may be a backflow tube-in-tube heat exchanger semblé 200. In this embodiment, the heat exchanger assembly 200 may include an outer tube 202, a plurality of inner tubes 204, and a pair of connectors 206, as shown in Figure 2A. Alternative embodiments of the heat exchanger assembly 200 may omit the connectors 206.

[0045] Referring again to Figure 2-2A, the heat exchanger assembly 200 may include several independent fluid paths. In an exemplary embodiment, the outer tube 202 contains source water and four inner tubes 204. Three of these inner tubes 204 may contain product water generated by the apparatus. The fourth inner tube may contain discharge water.

[0046] Referring again to Figure 2-2A, the heat exchanger assembly 200 increases the temperature of the inflow source water and decreases the temperature of the outflow product water. When the source water comes into contact with the outer surface of the inner tube 204, thermal energy is transferred through the wall of the inner tube 204 from the higher temperature outflow water to the lower temperature source water. Since the higher temperature source water requires less energy to evaporate, increasing the temperature of the source water improves the efficiency of the steam distillation apparatus 100. In addition, by reducing the temperature of the product water, the water is prepared for use by consumers.

[0047] Referring again to Figure 2-2A, in the exemplary embodiment, the heat exchanger 200 is a tube-in-tube heat exchanger having an outer tube 202 having several functions. Firstly, the outer tube 202 protects and contains the inner tube 204. The outer tube 202 protects the inner tube 204 from corrosion by acting as a barrier between the inner tube 204 and the surrounding environment. In addition, the outer tube 202 also improves the efficiency of the heat exchanger 200 by preventing the exchange of thermal energy to the surrounding environment. The outer tube 202 insulates the inner tube 204, reducing heat transfer back and forth to the surrounding environment. Similarly, the outer tube 202 may improve the efficiency of the heat exchanger 200 by resisting heat transfer from the inner tube 204, thereby concentrating heat transfer to the source water.

[0048] Referring again to Figure 2-2A, the outer tube 202 may be made of any material, but low thermal conductivity is desirable. Low thermal conductivity is important because the outer tube 202 insulates the inner tube 204 from the surrounding environment. Low thermal conductivity of the outer tube improves the efficiency of the heat exchanger because thermally conductive materials reduce the loss or gain of thermal energy to the surrounding environment. In addition, low thermal conductivity materials reduce the amount of thermal energy that may be transferred from the inner tube 204 to the outer tube 202. This resistance to heat transfer allows more thermal energy to be transferred to the source water rather than leaking out of the device through the outer tube 202. Therefore, an outer tube 202 made of a material with low thermal conductivity allows more thermal energy to be transferred to the source water rather than lost or gained to the surrounding environment.

[0049] Referring again to Figure 2-2A, in the exemplary embodiment, the outer tube 202 is made of transparent silicone. In addition to having low thermal conductivity, silicone material is also corrosion resistant. This is an important property for preventing corrosion of the heat exchanger 200. The source water in the outer tube 202 may contain chemicals and / or other highly reactive materials. These materials may decompose the outer tubes 202 made of other materials, reducing the service life of the heat exchanger 200. In alternative embodiments, the outer tube 202 may be made of other materials such as plastic or rubber that have high temperature resistance. Also, in one embodiment, the outer tube 202 is made of folded tubing to improve mixing, which increases heat transfer efficiency.

[0050] Referring here to Figure 2B-C, another desirable characteristic is that the outer tubing 202 is elastic enough to support the installation of the heat exchanger 200 within the steam distillation apparatus 100. In some applications, the space for the distillation apparatus may be limited by other environmental or circumstances. For example, in the exemplary embodiment, the heat exchanger 200 encloses the evaporator / condenser. In other embodiments, the heat exchanger may also be incorporated into the insulating cover of the steam distillation apparatus to minimize heat loss or gain from the environment. In exemplary embodiments, the heat exchanger 200 may be configured in a coil shape as shown in Figures 2B-C. To achieve this configuration, the inner tube 204 is slid into the outer tube 202 and then wound around a mandrel. The elastic outer tube 202 assists in positioning the end of the heat exchanger 200 at a specific location within the apparatus. Therefore, having the elastic outer tube 202 may facilitate the installation of the heat exchanger 200 within the steam distillation apparatus 100.

[0051] Referring again to Figure 2B-C, the elasticity of the outer tube material 202 can also be affected by the wall thickness. Tubes with thicker walls have less flexibility. However, thicker walls can improve the thermal properties of the tubes because they have better heat transfer resistance. In addition, the wall thickness of the tubes must be sufficient to withstand the internal pressure generated by the source water within the tubes. However, tubes with increased wall thickness have reduced elasticity and increase the size of the heat exchanger assembly. Tubes with thicker walls require a larger bending radius, which affects the installation of the heat exchanger 200. Conversely, tubes with too thin walls tend to twist during installation. This deformation of the tubes can restrict the flow of source water through the outer tube 202, potentially leading to a reduction in the efficiency of the heat exchanger 200.

[0052] The diameter of the outer tube 202 may be any diameter that allows for the inclusion of multiple inner tubes 204. However, the larger the diameter, the less flexible the tubes become. This reduced flexibility may negatively affect the installation of the heat exchanger in the steam distillation apparatus 100. In an exemplary embodiment, the diameter of the outer tube 202 is 1 inch. This diameter allows the tube-in-tube heat exchanger 200 to be wound around the evaporator / condenser 104 during final installation and includes four inner tubes 204 for transporting the product water and discharge water. In an alternative embodiment, the heat exchanger may have only two inner tubes 204. Similarly, in other embodiments, the heat exchanger may have five or more inner tubes 204.

[0053] Referring here to Figures 2A and 2D, the inner tubes 204 may provide separate flow paths for source water, produced water, and discharged water. In exemplary embodiments, these tubes contain produced water and discharged water. However, in other embodiments, the inner tubes may contain additional fluid flows. The inner tubes 204 separate clean, safe produced water from contaminated, unhealthy source water and discharged water. In exemplary embodiments, there are three inner tubes 204 for produced water and one inner tube 204 for discharge. The source water moves through the outer tube 202 of the heat exchanger 200. In various other embodiments, the number of inner tubes may vary, i.e., there may be more or fewer inner tubes.

[0054] Referring again to Figures 2A and 2D, the inner tube 204 conducts thermal energy through its walls. The thermal energy flows through the walls from the high-temperature production water and discharged water within the inner tube 204 to the lower-temperature source water. Therefore, the inner tube 204 is preferably made of a material having high thermal conductivity, and in addition, preferably a corrosion-resistant material. In exemplary embodiments, the inner tube 204 is made of copper. The inner tube 204 may also be made of other materials such as brass or titanium, depending on the preference for these other materials having high thermal conductivity and corrosion resistance. For applications where the source water and discharged water, such as seawater, are highly concentrated, the inner tube 204 may be made of copper-nickel, titanium, or thermally conductive plastic, but is not limited to these.

[0055] In addition to the material of the tubing, the diameter and thickness of the tubing can also affect the thermal energy transfer coefficient. Increasing the wall thickness of the tubing also increases the resistance to heat transfer, so inner tubing 204 with greater wall thickness may have lower thermal efficiency. In the exemplary embodiment, inner tubing 204 has an outer diameter of 0.25 inches. Thinner wall thickness increases the thermal transfer coefficient, but the wall thickness must be sufficient to form or create without deformation. Tubes with thinner walls are more likely to twist, pinch, or collapse during formation. In addition, the wall thickness of inner tubing 204 must be sufficient to withstand the internal pressure generated by the water passing through the tube.

[0056] Referring again to Figures 2A and 2D, additional methods for improving the heat transfer coefficient of the inner tube 204 may include a non-uniform inner tube diameter and expanded surfaces on the inner tube to enhance heat transfer (fins, pins, ribs, etc.). In addition, the outer tube 202 may have a woven inner surface to create turbulence in the source water flow and enhance heat transfer. The woven surface increases the thermal conductivity by creating turbulence within the tube 202. The turbulence increases the amount of water in contact with the outer surface of the inner tube 204 where heat transfer occurs. In contrast, without a woven surface, the water can flow more laminarly. This laminar flow allows only a limited amount of water to contact the outer surface of the inner tube 204. Since convective heat transfer between the water near the inner tube and the remaining water is not as efficient as heat transfer near the outer surface of the inner tube 204, the remaining water not in contact with the inner tube 204 does not absorb much thermal energy. Some examples of the woven surface may include, but are not limited to, depressions, fins, ridges, or grooves. In another embodiment, it may be reduced to fit the outer tube to increase the shell-side flow velocity and thus enhance heat conduction.

[0057] Referring here to Figure 2E, typically the inner tubes 204 are arranged parallel to each other. However, in some embodiments, the inner tubes 204 are woven together or wound to form a spiral or substantially helical shape, as shown in Figures 2F-G. Because the length of the inner tubes 204 is longer than that of inner tubes 204 arranged in parallel, the spiral shape increases the amount of surface area for heat transfer. The increased surface area provides further area for heat transfer and therefore increases the efficiency of the heat exchanger 200. In addition, the helical shape can cause turbulence of the source water within the outer tubes 202, thereby improving the heat transfer efficiency as described above. In an exemplary embodiment, the heat exchanger 200 has four inner tubes 204 arranged in a spiral shape, as shown in Figure 2H-I.

[0058] The overall length of the tube-in-tube heat exchanger 200 is determined by the desired efficiency of the device. A longer heat exchanger 200 will produce better efficiency. In an exemplary embodiment, the heat exchanger 200 is about 50 feet long, which produces an efficiency of about 90%. Alternatively, a length of 25 feet produces an efficiency of about 84%.

[0059] Referring here to Figures 2, 2J, and 2K, the heat exchanger assembly 200 may also include connectors 206 at either end of the heat exchanger 200. In exemplary embodiments, the heat exchanger 200 has two connectors located at either end of the assembly. These connectors 206 along the outer tube 202 define an internal cavity for containing source water. In addition, the connectors attach to the end of the inner tube 204 and provide separate fluid paths for production water and discharge water to enter and / or exit the heat exchanger 200. The connectors 206 allow the heat exchanger assembly to be mechanically connected to the evaporator / condenser and other device components. In some embodiments, extensions 207 may be included within the heat exchanger 200 to provide additional ports for removing or supplying water to the heat exchanger 200.

[0060] Referring here to Figure 2L-O, these figures illustrate an alternative embodiment of the heat exchanger 200 having three inner tubes 204 passing through a connector 208. The connector 208 is sealed and fitted to the inner tubes 204 and outer tube 202 at either end of the heat exchanger 200, so that the outer tube 202 contains source water inside. An O-ring may be installed inside the connector 208 to seal the interface between the connector 208 and the inner tubes 204. This type of seal may allow the inner tubes 204 to move freely and independently of the connector 208. Furthermore, the inner tubes 204 may be arranged in a helical shape as shown in Figure 2N. Referring here to Figures 74-74C, other embodiments of the connector 7400 are shown, which may be used in any embodiment described herein.

[0061] Referring to Figures 2P-R, these figures illustrate alternative embodiments of the heat exchanger 210. In this embodiment, the heat exchanger 210 is a flat plate heat exchanger having metal plates 212 and plastic plates 214. The metal plates 212 may be made of any metallic material such as stainless steel. Other embodiments may include, but are not limited to, plates made of titanium or a metal alloy. The plastic plates 214 are made of any type of plastic that is capable of functioning. In one embodiment, the flat plate heat exchanger 210 is made of alternating metal plates and plastic plates. In other embodiments, the metal plates 212 may be followed by two or more plastic plates 214, as shown in Figure 2R. The flat plate heat exchanger 210 may begin and / or end with plates 216 made of the same or different material as the preceding plates. In alternative embodiments, the flat plates 216 may be made of a metallic or plastic material. The metal plates 212 consist of two metal plates laminated together, as shown in Figure 2R, forming a channel for fluid flow.

[0062] Referring here to Figure 3, an exemplary embodiment of the backflow tube-in-tube heat exchanger 200 may include a mounting assembly 300. The mounting assembly supports the installation of the heat exchanger 200 within the steam distillation apparatus 100. In addition, the mounting assembly 300 allows the heat exchanger 200 to be easily separated from the apparatus for maintenance. The assembly may consist of a first connector 302 (also identified as connector 206 in Figure 2) and a second connector 310, as shown in Figure 3. See also Figures 3A-B for a cross-sectional view of the mounting assembly 300.

[0063] Referring again to Figure 3, in the exemplary embodiment, the fitting assembly 300 is made of brass. Other materials, including but not limited to stainless steel, plastic, copper, copper-nickel, or titanium, may be used to manufacture the fitting assembly 300. For installation purposes, it is preferable to have a fitting assembly made of the same material as the tubing to be fitted to the assembly. The same material allows the assembly to be installed in the steam distillation apparatus using soldering or welding techniques. The fitting assembly 300 is preferably made of a corrosion-resistant and heat-resistant (250°F) material. In addition, the material preferably allows for a fluid-tight connection when the assembly is installed. For applications where the source water and discharge water are of high concentration, such as seawater, the fitting assembly 300 may be made of copper-nickel or titanium, but is not limited to these.

[0064] Referring again to Figure 3, the first connector 302 includes a first end 304 and a second end 306. The first end 304 is attached to the heat exchanger 200 as shown in Figure 2-2A. The connector may also be attached to the heat exchanger 200 by using a hose clamp to fasten the outer tube 202 to the outer surface of the first end 304 of the connector 302. The inner tube 204 of the heat exchanger 200 may also be connected to the connector 302 at the first end 304. These tubes are soldered to the heat exchanger side of the connector 302. Other attachment methods may include, but are not limited to, welding, press-fitting, mechanical fastening, or insert molding. See also Figure 3A-3B for a cross-sectional view of the mounting assembly 300.

[0065] Referring now to Figure 3C, in this embodiment, the first end 304 of the connector 302 may have five ports. Three of the ports may be fluid-connected to one another, as shown in Figures 3D-E. This configuration may integrate multiple production water flows into a single flow. Multiple production water flows increase the amount of heat transferred from the production water to the source water, as there is more production water in the heat exchanger to provide thermal energy to the source water. The remaining ports are separate and provide fluid paths for discharge water and source water, as illustrated in Figures 3E-F. Alternative embodiments may not have ports that are fluid-connected to one another.

[0066] Referring again to Figure 3C, connector 302 has a second end 306 for meshing with a second connector 310. This second end 306 may have three ports providing pathways for production water, source water, and discharge water. The production pathway may include an extension 308. The extension 308 assists in the step of assembling connectors 302 and 310 together, as it allows for an O-ring groove within the body of the second connector 310 rather than on the meshing surface 310. Having an O-ring groove within the body of the second connector 310 allows pathways through the connector assembly to be located near each other without having overlapping sealed areas.

[0067] Referring here to Figure 3G-H, the second connector 310 includes a first end 312 and a second end 314. The first end 312 engages with the first connector 302 as shown in Figure 3. This end may also include an extension 316 as shown in Figure 3G. The extension 316 allows the O-ring groove to be located within the body of the first connector 302 rather than within the surface of the end 306 of the first connector 302. In addition, the connector may have a leak passage 318 on the first end 312. This passage is located around the port for production water to prevent source water or discharge water from entering the production logistics. Discharge water and source water may contain contaminants that affect the quality and safety of the production water. The leak passage allows discharge water and source water to exit the fixture rather than enter the production logistics through the drain 320 shown in Figure 3G-I. In addition to the drain section 320, exemplary embodiments may include three independent fluid paths within the connector 310, as shown in Figure 3I-J.

[0068] The first connector 302 may be assembled to the second connector 310 using a Marmon clamp to enable the usability of the device. This type of clamp provides even clamping force and ease of disconnection / reassembly of the connection. Other methods of assembling the connectors together include, but are not limited to, the step of using C-clamps or fasteners (i.e., bolts and nuts). In addition, the circumferences of the connectors 302 and 310 may be tapered as shown in Figures 3E-F and 3I-J to receive the clamp during installation of the mounting fixture assembly 300. In other embodiments, the mounting fixture assembly 300 may be permanently joined by welding or soldering the connectors together. (Evaporator / Condenser) Referring here to Figure 4-4B, an exemplary embodiment of the evaporator / condenser (also referred to herein as “evaporator / condenser”) assembly 400 may consist of an evaporator / condenser chamber 402 having a top and bottom. The chamber 402 may include an outer structure 410, an upper tube sheet 414, and a lower tube sheet 412. A reservoir assembly 404 for holding inflow source water is attached to the lower tube sheet 412. Similarly, an upper flange 406 is attached to the upper tube sheet 414. This flange connects the steam chamber 408 to the evaporator / condenser chamber 402. Within the evaporator / condenser chamber 402 are several rods 416, each rod surrounded by a tube 418, as shown in Figures 4A and 4B. The tubes 418 are fluidly connected to the reservoir 404 and the upper flange 406. See also Figure 4C, which illustrates an alternative embodiment of the evaporator / condenser assembly 420.

[0069] Referring here to Figure 5, the water reservoir assembly 500 (also identified as 404 in Figure 4) may include an upper housing 502, a lower housing 504, a drain pipe fitting 506, a drain pipe 508, and a heating element 510. See also Figure 5A for an exploded view of the water reservoir assembly 500 and Figure 6 for a detailed view of the upper housing 502. The water reservoir assembly 500 contains and heats the source water and collects particulate matter carried by the source water. As the source water changes state from fluid to steam, the particulate matter remains and is collected in the water reservoir assembly 500.

[0070] Referring again to Figure 5-5A, the reservoir assembly 500 may be made from a material that is corrosion-resistant and high-temperature resistant. Since the reservoir is exposed to high temperature, moisture, and corrosive source water, a corrosion-resistant material is preferred. In exemplary embodiments, the reservoir is made of stainless steel. In alternative embodiments, the reservoir may be made of RADEL® or other high-temperature plastics, in conjunction with an alternative configuration for mounting the heating element 510. For applications where the source water may be highly concentrated, such as seawater, the reservoir assembly 500 may be made of titanium, copper-nickel, naval brass, or high-temperature plastics, but is not limited to these.

[0071] Referring again to Figure 5-5A, the source water may be heated using the heating element 510 of the water reservoir assembly 500. The heating element 510 raises the temperature of the source water during the initial startup of the steam distillation apparatus 100. This element provides additional thermal energy to change the source water from fluid to steam. In an exemplary embodiment, the heating element 510 may be a 120-volt / 1200-watt resistor-type electric heater.

[0072] Referring again to Figure 5-5A, the water reservoir assembly 500 may include a bottom housing 504 having an angled bottom surface to assist in the collection of particulate matter. The bottom housing 504 may have any angle sufficient to collect particulate matter into one area of ​​the housing. In an exemplary embodiment, the bottom housing 504 has a bottom surface angled at 17 degrees. In other embodiments, the bottom housing 504 may have a flat bottom.

[0073] Referring again to Figure 5-5A, the exemplary embodiment may include a drain pipe assembly comprising a drain pipe fitting 506 and a drain pipe 508. The drain pipe assembly provides access to the inside of the evaporator / condenser to remove particulate matter buildup without requiring disassembly of the apparatus. The drain pipe assembly may be located near the bottom of the reservoir to reduce debris (particulate matter buildup) on the pipe inside the evaporator / condenser. Debris buildup is prevented by allowing periodic removal of flakes in the reservoir assembly 500. Fewer particulate matter in the reservoir assembly 500 reduces the likelihood of particulate matter flowing into the evaporator / condenser pipe. In the exemplary embodiment, the drain pipe assembly is positioned to receive particulate matter from the angled bottom surface of the bottom housing 504. The drain pipe assembly may be mounted on the bottom housing 504 and may be made of any material that is corrosion-resistant and heat-resistant. In the exemplary embodiment, the drain pipe fitting 506 is a flanged sanitary fitting made of stainless steel. Referring to Figure 73, the fluid path of the water reservoir drainage 7302 is shown. In some embodiments, the fluid path of the water reservoir drainage 7302 can be used to facilitate cleaning or flushing of the apparatus 100. In some embodiments, the fluid path of the water reservoir drainage 7302 may be sealed from the surrounding environment by, for example, a valve, but the seal is not limited to a valve. In some embodiments, the valve may not be a manual valve, but may be, for example, a differential valve controlled by a control system, and in some embodiments, cleaning and flushing may be automated at least partially.

[0074] Referring again to Figure 5-5A, a drain pipe 508 may be attached to the drain pipe fitting 506. The drain pipe 508 provides a fluid path for particulate matter to move from the drain pipe fitting 506 out of the evaporator / condenser assembly 400. The drain pipe 508 may be manufactured from any material, depending on the preference that the material is corrosion-resistant and heat-resistant and can be attached to the drain pipe fitting 506. In an exemplary embodiment, the drain pipe 508 is manufactured from stainless steel. The diameter of the drain pipe 508 is preferably sufficient to allow the removal of particulate matter from the reservoir assembly 500. A larger diameter pipe is desirable because it is less likely that the drain pipe 508 will become clogged with particles while the reservoir assembly 500 is being discharged.

[0075] Referring here to Figure 7, an exemplary embodiment of the evaporator / condenser chamber 700 (also identified as 402 in Figure 4) may include an outer structure 702 (also identified as 410 in Figures 4A-B), a lower flange 704 (also identified as 502 in Figure 5 and 600 in Figure 6), a lower tube sheet 706 (also identified as 412 in Figures 4A-B), a plurality of connecting rods 708, a plurality of tubes 710 (also identified as 418 in Figures 4A-B), an upper flange 712 (also identified as 406 in Figure 4), and an upper tube sheet 714 (also identified as 414 in Figures 4A-B). See also Figure 7A for an assembly diagram of the evaporator / condenser chamber 700.

[0076] Referring again to Figure 7, the outer structure 702 defines an internal cavity through which thermal energy is transferred from high-pressure steam to source water. This heat transfer assists in the phase change of the source water from fluid to steam. In addition, the heat transfer also condenses the inflowing steam into the production water. The outer structure 702 may be made of any material having sufficient corrosion resistance and strength properties. In an exemplary embodiment, the outer structure 702 is made of fiberglass. The outer structure preferably has an inner diameter sufficient to accommodate a desired number of tubes 710. Within the internal cavity of the outer structure are several tubes 710, each having a surface area for transferring thermal energy from the high-pressure steam entering the chamber to the source water in the tubes 710.

[0077] Still referring to FIG. 7, the evaporator / condenser chamber 700 defines an internal cavity for condensing high-pressure steam. Within this cavity, there are a plurality of tubes 710 that transfer thermal energy from the high-pressure steam to source water inside the tubes as steam condenses on the outer surfaces of the tubes. As described in U.S. Patent Application Publication No. 2005 / 0183832A1, published Aug. 25, 2005, entitled "Method and Apparatus for Phase Change Enhancement", the content of which is incorporated herein by reference, heat transfer through the tube wall causes the source water to undergo a phase change via a process called thin film evaporation.

[0078] Still referring to FIG. 7, within the evaporator / condenser tubes 710, Taylor bubbles may be developed that have an outer surface including a thin film in contact with the inner surface of the tubes 710. The Taylor bubbles are heated as they rise through the tubes, causing the fluid in the thin film to transition to vapor within the bubbles.

[0079] Referring now to FIG. 7B, typically the evaporator operates in one of two modes, a pool boiling mode or a thin film mode. In thin film boiling, a thin film of fluid is created on the inner wall of the tube, facilitating heat transfer from the tube wall to the free surface of the fluid. The efficiency of phase change is typically increased in the thin film mode compared to the pool boiling mode. FIG. 7B shows the difference in distillate production flow rate as a function of condenser pressure for pool boiling and thin film boiling under similar conditions for a representative evaporator. The lowermost curve 70 corresponds to pool boiling, while the middle curve 75 corresponds to thin film boiling. As can be seen from these two curves, the thin film boiling mode provides significantly higher efficiency than the pool boiling mode. However, thin film boiling is more difficult to maintain than pool boiling. Thin film evaporation is typically achieved using devices that include very small openings. Such devices can easily become clogged, especially when the feed fluid contains contaminants. In addition, in thin film mode, the water level is typically held marginally above the top of the tubes in a vertical tube evaporator. For these reasons, the device may also be sensitive to movement and positioning of the device.

[0080] Referring again to FIG. 7, in an exemplary embodiment, the tube 710 has an outer diameter of 0.75 inches and may be made of copper. In alternative embodiments, the tube 710 may be made of other materials, including but not limited to nickel-copper or other composite materials. In various other embodiments, the diameter of the tube may be different, that is, it may be smaller or larger. For possible applications where the source water may be seawater, the tube 710 may be made of copper-nickel or titanium materials. These materials have high corrosion resistance to maintain the heat transfer characteristics of the tube when exposed to high-concentration source water such as saline. The diameter of the tube 710 may also vary depending on many variables. The diameter of the tube 710 may be limited by the inner diameter of the outer shell structure 702 and a desired amount of heat transfer efficiency. Another constraint may be usability. Since a reduced diameter limits access to the inner surface of the tube wall, it is difficult to remove scale from smaller diameter tubes. The length of the tube 710 may be determined by the length of the internal cavity defined by the outer shell structure 702 and the thicknesses of the tube sheets 706 and 714. In an exemplary embodiment, the tube 710 may extend beyond the ends of the tube sheets into the lower flange 704 and the upper flange 712.

[0081] Referring now to FIG. 8, in an exemplary embodiment, the tube 800 (also identified as 710 in FIGS. 7A-B) has a bead 802 near each end. The bead 802 prevents the tube 800 from sliding through the openings of the lower tube sheet 706 and the upper tube sheet 714.

[0082] Referring here to Figure 9, improved efficiency of the phase change operation may be achieved by providing packing within the evaporator / condenser tube 904. The introduction of such packing may allow the evaporator to exhibit some of the characteristics of a thin-film mode through the interaction between the fluid, the packing, and the tube 904. The packing may be any molded material such that the material preferentially fills the volume of the tube 904 near the longitudinal axis of the tube, relative to the volume near the inner wall of the tube. Such packing material works to concentrate the vapor near the tube wall for efficient heat exchange. For example, in an exemplary embodiment, the packing may comprise rods 902. Each rod 902 may have any cross-sectional shape, including cylindrical or rectangular. The cross-sectional area of ​​each packing rod 902 may be any area that fits within the cross-section of the tube. The cross-sectional area of ​​each rod 902 may vary along the length of the rod. A given rod 902 may extend the length of a given evaporator tube 904 or any part thereof. The rod material is preferably hydrophobic and capable of repeated heat circulation. In exemplary embodiments, the rod 902 is made of glass fiber-filled RYTON® or glass fiber-filled polypropylene.

[0083] Referring again to Figure 9, each rod 902 may be positioned anywhere within the tube 904, preferentially included in the upper portion of the tube. In one specific embodiment, each rod is approximately half the length of the associated tube and is positioned almost entirely in the upper half of the tube. The top curve 80 in Figure 7B shows an increase in the boiling efficiency of thin-film boiling for a typical evaporator in which the evaporator tube contains packing material in the upper half of the tube. Such packing also favorably increases the phase change efficiency to changes in the fluid level above the tube, the orientation of the tube relative to the vertical line, the supply pressure to the tube, and other operating parameters of the evaporator. In an exemplary embodiment, the rod 902 has approximately the same length as the tube 904.

[0084] Referring here to Figure 9A, in an exemplary embodiment, the rod 902 may have a plurality of members 906 extending outward from the center of the rod 902 and along the longitudinal axis of the rod 902. These members 906 maintain the rod 902 in the center of the pipe 904, creating the most efficient flow path for the source water. Any number of members may be used, but it is preferable to have a sufficient number to maintain the rod 902 in the center of the pipe 904. In an alternative embodiment, the rod 902 may not have members 906. In an alternative embodiment, the rod 902 may be supported in place within the pipe 904 by wrapping the rod 902 in a wire or in intersecting boreholes within the rod 902, thereby assisting in the installation of pins that position the rod 902 within the pipe 904.

[0085] Referring again to Figure 7, the pipe 710 (also identified as 800 in Figure 8 and 904 in Figure 9) is secured in place by a pair of tube sheets 706 and 714. These sheets are secured to each end of the outer structure 702 using connecting rods 708. The tube sheets 706 and 714 have multiple openings that provide pathways for source water to enter and exit the pipe 710. When the pipe 710 is installed in the chamber 700, the openings in the tube sheets 706 and 714 receive the ends of the pipe 710. The lower tube sheet 706 (also identified as 1002 in Figure 10) is attached to the bottom of the outer structure 702. See Figure 10 for a detailed view of the lower tube sheet. The upper tube sheet 714 (also identified as 1004 in Figure 10A) is attached to the top of the outer structure 702. See Figure 10A for a detailed view of the upper tube sheet. Both tube sheets have similar dimensions, except that the upper tube sheet 714 has an additional opening located in the center of the sheet. This opening provides an opening for high-pressure steam to enter the evaporator / condenser chamber 700.

[0086] Referring again to Figure 7, in the exemplary embodiment, the upper tube sheet 714 and the lower tube sheet 706 may be manufactured from RADEL®. This material has low creep, hydrolysis stability, thermal stability, and low thermal conductivity. Furthermore, tube sheets manufactured from RADEL® may be formed by machining or injection molding. In alternative embodiments, the tube sheets may be manufactured from other materials, including but not limited to G10.

[0087] Referring again to Figure 7, the size of the multiple openings in the tube sheets 706 and 714 for receiving the tube 710 is determined by the outer diameter of the tube 710. These openings must be sufficient to receive the end of the tube 710 and also to include a seal. Typically, an O-ring groove is provided in the tube sheet to receive an O-ring. This O-ring provides a watertight seal between the inner tube 710 and the tube sheets 706 and 714. This type of seal also simplifies the structure, facilitates the use of dissimilar materials in the evaporator / condenser, and allows the tube 710 to move during repeated thermal cycles. This seal prevents the production water from entering the reservoir 500 in Figure 5, or the source water from entering the chamber 700. In alternative embodiments, the tube 710 may be installed within the openings of tube sheets 706 and 714 by using methods such as soldering, welding, press-fitting, bonding (i.e., silicone, RTV, epoxy, etc.), brazing, or swaging, depending on the tube sheet material.

[0088] Referring now to Figure 10, in the exemplary embodiment, the O-ring grooves are located in tube sheets 1002 and 1004 at various depths. The different depths of the O-ring grooves allow the tubes 710 to be positioned more closely together, as the O-ring grooves from adjacent tubes do not overlap with each other. Overlapping O-ring grooves do not provide sufficient sealing, and therefore each O-ring groove must be independent of other O-ring grooves in the tube sheet. As a result of varying the location of the O-ring grooves at different depths in the tube sheet, adjacent O-ring grooves do not overlap with each other, allowing the tubes to be positioned more closely together. Thus, having tubes 710 positioned more closely together allows more tubes to be placed in the evaporator / condenser chamber 700.

[0089] Referring again to Figure 7, tube sheets 706 and 714 are also secured to the lower flange 704 and upper flange 712 using connecting rods 708. The lower flange 704 (also identified as 502 in Figure 5 and 600 in Figure 6) connects the reservoir 500 in Figure 5 to the evaporator / condenser chamber 700 in Figure 7. In addition, the lower flange 704 provides a fluid connection for the raw material in the reservoir to the inlet of the tube 710, which is located on the lower tube sheet 706. The lower flange 704 may be of any height, depending on the preference that the height is sufficient to allow even distribution of the source water entering the tube 710. Typically, a flange with a height of 1 to 2 inches provides even distribution of the source water into the tube 710. In alternative embodiments, the height of the flange may be greater to increase the reservoir's ability to collect particles.

[0090] Referring again to Figure 7, the upper flange 712 (also identified as 1100 in Figure 11) provides a fluid connection between the outlet of pipe 710 and the steam chamber 408 in Figure 4. In addition, the upper flange 712 collects source water removed from the low-pressure steam as the steam passes through the steam chamber 408. This water is then transferred out of the apparatus through a discharge port 1102 located on the side of the upper flange 1100 in Figure 11.

[0091] Referring again to Figure 7, the lower flange 704 and the upper flange 712 may be manufactured from any material having sufficient structural strength, corrosion resistance, and heat resistance. In one embodiment, the flange may be manufactured from RADEL®. In an exemplary embodiment, the flange may be manufactured from nickel-plated aluminum. In other embodiments, the lower flange may be manufactured from a material including, but not limited to, stainless steel, titanium, and copper-nickel.

[0092] Referring to Figure 7-7A, multiple openings for receiving connecting rods 708 are located near the outer edges of the lower flange 704 and the upper flange 712. These rods are positioned longitudinally along the outer circumference of the outer structure 702, on a bolt circle concentric with the outer structure 702. The length of the connecting rods 708 is determined by the length of the outer structure 702, as well as the thickness of the lower tube sheet 706, the lower flange 704, the upper flange 712, and the upper tube sheet 714. The connecting rods 708 may have threaded ends on each end of the rod for attaching screw fasteners, thereby integrally fixing the components of the evaporator / condenser. In addition, the connecting rods 708 may be manufactured from any material that is sufficiently strong for the purpose, such as stainless steel. The connecting rods 708 may be manufactured from other materials, including, but not limited to, bronze, titanium, fiberglass composites, and carbon steel. In exemplary embodiments, the connecting rod 708 may have machined flat sections near each end to provide a surface for receiving a device that supports the rod in place during installation.

[0093] Referring here to Figure 12-12C, a steam chamber 1200 (also identified as 408 in Figure 4) may be connected to the upper flange 1100 (also identified as 712 in Figure 7). In an exemplary embodiment, the steam chamber 1200 may include a base 1202, a steam separator assembly 1204, a cap 1206, and a steam pipe 1208. The base 1202 defines an internal cavity for receiving low-pressure steam generated in the pipe 710 of the evaporator area of ​​the evaporator / condenser chamber 700. The base 1202 may have any height so as to have sufficient space to allow water droplets contained in the steam to be separated. The height of the steam chamber allows water droplets carried by the steam and forced out of the outlet of the pipe 710 by the rapid discharge of steam bubbles to slow down and recede toward the upper flange 712 (also identified as 1100 in Figure 11).

[0094] Referring again to Figure 12-12C, a steam separator assembly 1204 may be located within the base 1202. This assembly consists of a basket and a mesh (not shown in Figure 12-12C). The basket contains a large amount of wire mesh. In an exemplary embodiment, the steam separator assembly 1204 removes water droplets from the inflowing low-pressure steam by manipulating the steam through a layer of wire mesh. As the steam passes through the mesh, water droplets begin to collect on the surface of the mesh. These water droplets may contain contaminants or particulate matter. As the water droplets increase in size, the water falls to the bottom of the basket. Multiple openings may be located at the bottom of the basket to allow the water to collect within the upper flange 712. In addition, these openings provide a fluid path for the low-pressure steam to enter the steam separator assembly 1204. In addition, the wire mesh provides a barrier from splashing discharge water located within the upper flange 712 of the evaporator / condenser.

[0095] Referring again to Figure 12-12C, in an alternative embodiment, the steam separator assembly 1204 may include a series of plates for collecting water droplets from low-pressure steam as steam passes through or around each plate. The plates manipulate the steam to collect the water droplets on the plates. The plates are positioned to create sharp bends in the steam flow path so that the water collects in the assembly. These bends reduce the velocity of the steam and change the direction of the steam. The water droplets may persist along their initial trajectories due to their momentum. The water droplets may then collide with the walls or plates of the assembly from which they are collected. Once a sufficient amount of water droplets have collected on the walls or plates of the assembly, the water droplets may fall toward the upper flange 406 of the evaporator / condenser.

[0096] Referring again to Figure 12-12C, the base 1202 may also have an observation window 1210. This window allows operators of the device to visually observe the inside of the steam chamber and determine whether the device is functioning properly. In other embodiments, the steam chamber 1200 may not include the observation window 1210. This alternative embodiment is shown in Figure 12D. In yet other embodiments, the size and shape of the window may vary. In some embodiments, the steam chamber may include multiple windows.

[0097] In exemplary embodiments, the steam separator assembly may be made of stainless steel. However, other materials may be used depending on the preference for materials that have corrosion resistance and high temperature resistance. Other types of materials may include, but are not limited to, RADEL®, titanium, copper-nickel, plated aluminum, fiber composites, and high-temperature plastics.

[0098] Referring again to Figure 12-12C, the cap 1206 is attached to the base 1202. The cap and base define an internal cavity for separating water from low-pressure steam. In addition, the cap 1206 may have two ports, an outlet port 1211 and an inlet port 1212, as shown in Figures 12B, 12E, and 12F. The outlet port provides a fluid path for dry low-pressure steam to exit the steam chamber 1200. In an exemplary embodiment, the outlet port 1211 is located near the top surface of the cap 1206 to promote drier steam by positioning the port away from the outlet of the evaporator / condenser tube 710. However, in an alternative embodiment, the outlet port 1211 may have a different location within the cap 1206. Similarly, the inlet port 1212 provides a fluid path for high-pressure steam to enter the high-pressure steam tube 1208 in the steam chamber 1200. In the exemplary embodiment, the inlet port 1212 is located near the top surface of the cap 1206. In alternative embodiments, the inlet port 1212 may be located in a different place within the cap 1206. In the exemplary embodiment, the cap 1206 is made of plated aluminum. Other types of materials may include, but are not limited to, stainless steel, plastic, titanium, and copper-nickel. The size of these ports may affect the pressure drop in the compressor.

[0099] Referring again to Figure 12-12C, a steam pipe 1208 is connected to the inlet port 1212 in the steam chamber 1200. This pipe provides a fluid path for high-pressure steam to pass through the steam chamber and enter the condenser in the evaporator / condenser chamber. The inner diameter of the steam pipe 1208 may be of any size so as not to adversely affect the flow of high-pressure steam from the regenerative blower to the evaporator / condenser chamber. In exemplary embodiments, the steam pipe 1208 may be made of stainless steel. Other materials may be used to manufacture the steam pipe 1208, but these materials must have sufficient corrosion resistance and high temperature resistance. Such materials may include, but are not limited to, plated aluminum, plastic, titanium, and copper-nickel. For applications where the source water may be highly concentrated, such as seawater, the steam chamber 1200 may be made of, but are not limited to, titanium, nickel, bronze, nickel-copper, and copper-nickel.

[0100] Referring here to Figure 13-13C, an alternative embodiment of the evaporator / condenser assembly 1300 is shown. In this embodiment, the evaporator / condenser assembly 1300 includes a reservoir 1302, an evaporator / condenser chamber 1304, a mist remover assembly 1306, a plurality of connecting rods 1308, a lower flange 1310, and an upper flange 1312. For a detailed drawing of the evaporator / condenser assembly without the reservoir 1302, see Figure 13D.

[0101] Referring now to FIG. 13E, the evaporator / condenser chamber includes an outer shell structure 1314, a plurality of tubes 1316, a lower flange 1310, and an upper flange 1312. The evaporator / condenser chamber 1304 defines an internal cavity for condensing high-pressure steam. The tubes 1316 transfer thermal energy from the high-pressure steam to source water inside the tubes as the steam condenses on the outer surfaces of the tubes 1316. In this embodiment, the tubes 1316 have an outer diameter of 0.75 inches and may be made of copper. In alternative embodiments, the tubes 1316 may be made of other materials, including but not limited to nickel-copper or other composite materials. The diameter of the tubes 1316 may also vary depending on a number of variables. Reference is made to the preceding discussion in the exemplary embodiments regarding tube diameters. The length of the tubes 1316 may be determined by the length of the cavity defined by the outer shell structure 1314 and the thicknesses of the lower flange 1310 and the upper flange 1312.

[0102] Still referring to FIG. 13E, the tubes 1316 are supported within the internal cavity defined by the outer shell structure 1314 between the lower flange 1310 and the upper flange 1312, as shown in FIGS. 13B, 13C, and 13E. Each flange has a plurality of openings positioned axially around the center of the flange. These openings may receive the ends of the tubes 1316. In addition, the lower flange 1310 and the upper flange 1312 also secure the outer shell structure 1314 in place and provide a passage to the water sump 1302 and the mist eliminator assembly 1306. As the source water fills the water sump 1302, some water begins to fill the tubes 1316 positioned within the internal cavity of the outer shell structure 1314. As thermal energy is transferred to the source water in the tubes 1316, the water begins to evaporate. The source water steam travels through the tubes 1316 into the mist eliminator assembly 1306. The steam enters the mist eliminator through an opening located in the upper flange 1312.

[0103] Referring again to Figure 13E, the outer casing structure 1314 is secured to the lower flange 1310 and upper flange 1312 using a number of connecting rods 1308. These connecting rods are positioned axially outward around the outer circumference of the outer casing structure 1314. In addition, the connecting rods 1308 also secure the mist remover 1306 to the upper flange 1312 and the water reservoir 1302 to the lower flange 1310. The length of the connecting rods is determined by the length of the outer casing structure 1314, as well as the thickness of the lower flange 1310, upper flange 1312, water reservoir 1302, and mist remover 1306. The connecting rods 1308 may have threaded ends on each end of the rod for attaching screw fasteners, thereby securing the evaporator / condenser components together. In addition, the connecting rods 1308 may be made of any material with sufficient strength, such as stainless steel. The connecting rod 1308 may be made of other materials, including but not limited to bronze, titanium, fiberglass composites, and carbon steel.

[0104] Referring again to Figure 13E, in the exemplary embodiment, the outer structure 1314 is made of fiberglass. Other materials may be used, depending on the preference for materials that are corrosion-resistant, have low thermal conductivity, and have sufficient structural strength to withstand the internal pressures that arise during the operation of the evaporator / condenser assembly 1300. See the discussion of exemplary embodiments regarding the size of the inner diameter of the outer structure.

[0105] Referring again to Figure 13E, the reservoir 1302 is connected to the lower flange 1310 and is fluidly connected to the tube 1316 of the evaporator / condenser assembly chamber 1304. The reservoir 1302 collects incoming source water from the heat exchanger. The source water enters the reservoir 1302 through an inlet port located within the side wall of the reservoir. In other embodiments, the inlet port may be located in a different location (i.e., at the bottom). In this embodiment, the reservoir 1302 is made of a composite material such as G10 plastic. In other embodiments, the reservoir 1302 may be made of any other material having sufficient corrosion resistance and high temperature resistance. Other materials include, but are not limited to, aluminum RADEL® and stainless steel. The reservoir 1302 may also include a heating element to provide thermal energy to the source water. This thermal energy assists in the conversion of the source water from fluid to steam.

[0106] Referring here to Figures 14-14C, the mist remover assembly 1400 (also identified as 1306 in Figure 13) is mounted on the upper flange 1312. This assembly may consist of a cap 1402, a steam pipe 1404, and a mist separator 1406, as illustrated in Figure 14. The cap 1402 contains the low-pressure steam produced from the evaporator of the evaporator / condenser. The cap 1402 may have three ports 1408, 1410, and 1412, as shown in Figures 14A-C. See the discussion of the steam chamber in the exemplary embodiment regarding the volume height for removing water droplets. In addition, the cap 1402 defines a cavity containing the mist separator 1406, as shown in Figures 14, 14C, and 14D.

[0107] Referring again to Figure 14-14C, the first port 1408 may be located in the center of the upper surface of the cap 1402 and is for receiving the first end of the steam pipe 1404. This port allows the high-pressure steam generated by the compressor to re-enter the evaporator / condenser through the first end of the steam pipe 1404. The steam pipe 1404 provides a fluid path for the high-pressure steam to enter the evaporator / condenser through the mist purifier assembly 1400 without mixing with the low-pressure steam entering the mist purifier assembly 1400. In this embodiment, the steam pipe 1404 is made of stainless steel. In other embodiments, the steam pipe may be made of a material including, but not limited to, plated aluminum, RADEL®, copper nickel, and titanium. The length of the steam pipe 1404 must be sufficient to connect to the compressor and to pass through the entire mist purifier assembly 1400. The second end of the steam pipe is received in a port located in the center of the upper flange 1312. The inner diameter of the steam pipe 1404 may affect the pressure drop across the compressor. Another effect on the system is that the steam pipe 1404 reduces the effective volume in the mist remover, thereby removing water droplets from the low-pressure steam.

[0108] Referring again to Figure 14-14C, the steam pipe 1404 may also have a plurality of external grooves for receiving mist separators 1406. The mist separator 1406 is an annular plate with an opening. This opening allows low-pressure steam to pass through the plate. In one embodiment, a plurality of mist separators are installed in the grooves of the steam pipe 1404. These plates are oriented so that their openings are 180° from the aforementioned plates. In addition, the plate closest to the outlet port 1410 is oriented so that its opening is 180° from the port. In an alternative embodiment, the plates may include grooves on the upper surface of the plate to collect water droplets. These grooves may taper so that the collected water flows off the plate and falls towards the base of the mist remover assembly 1400. The mist separators 1406 may be secured to the steam pipe 1404 using a pair of snap rings and corrugated washers.

[0109] Referring again to Figure 14-14C, the second port 1410 may also be located on the upper surface of the cap 1402, allowing dry low-pressure steam to exit the mist remover assembly 1400. For exemplary embodiments regarding the size and location of the outlet port, see the previous discussion.

[0110] Referring again to Figure 14-14C, a third port 1412 may be located within the side wall of the cap 1402. This port allows water removed from the low-pressure steam to exit the device. The port is preferably located at a height that allows the discharged water to exit the mist remover assembly 1400 without excessive accumulation of discharged water within the assembly. In addition, the port height is preferably not too low, but rather sufficient to maintain a level of discharged water covering the outlet of the tube. In the exemplary embodiment, the tube may be connected to port 1412, and the discharged water may pass through the level sensor housing 108 and the heat exchanger 102 before exiting the device 100.

[0111] Referring again to Figure 14-14C, the mist purifier assembly 1400 may be manufactured from any material having sufficient corrosion resistance and high temperature resistance. In this embodiment, the mist purifier assembly is manufactured from stainless steel. The assembly may be manufactured from other materials, including but not limited to RADEL®, stainless steel, titanium, and copper-nickel. (Compressor) The steam distillation apparatus 100 may include a compressor 106. In an exemplary embodiment, the compressor is a regenerative blower. Other types of compressors may be implemented, but for the purposes of this application, a regenerative blower is shown and described in relation to the exemplary embodiment. The purpose of the regenerative blower is to compress the low-pressure steam exiting the evaporator area of ​​the evaporator / condenser to produce high-pressure steam. Increasing the pressure of the steam increases the temperature of the steam. This temperature increase is desirable because when the high-pressure steam condenses on the tubing in the condenser area of ​​the evaporator / condenser, thermal energy is transferred to the inflow source water. This heat transfer is important because the thermal energy transferred from the high-pressure steam supplies low-pressure steam to the regenerative blower.

[0112] The pressure change between low-pressure and high-pressure steam is determined by the desired output of the produced water. The output of the produced water is related to the flow velocity of the high-pressure steam. If the steam velocity of the high-pressure steam from the compressor to the condenser region of the evaporator / condenser is greater than the capacity of the condenser receiving the steam, the steam may be superheated. Conversely, if the evaporator side of the evaporator / condenser produces more steam than the compressor can compress, the condenser side of the evaporator / condenser may not operate at full capacity due to the limited flow velocity of the high-pressure steam from the compressor.

[0113] Referring here to Figure 15-15G, the exemplary embodiment may include a regenerative blower assembly 1500 for compressing low-pressure steam from the evaporator area of ​​the evaporator / condenser. The regenerative blower assembly 1500 includes an upper housing 1502 and a lower housing 1504 that define an internal cavity, as shown in Figure 15C. For detailed drawings of the upper housing 1502 and the lower housing 1504, see Figures 15D-G. An impeller assembly 1506 is located within the internal cavity defined by the upper housing 1502 and the lower housing 1504. The housing may be made of various plastics, including RYTON®, ULTEM®, or polysulfone. Alternatively, the housing may be made of materials including, but not limited to, titanium, copper-nickel, and aluminum-nickel bronze. In the exemplary embodiment, the upper housing 1502 and the lower housing 1504 are made of aluminum. In alternative embodiments, other materials may be used, depending on the preference that the material has high temperature resistance and corrosion resistance, does not absorb water, and has sufficient structural strength. The housing is preferably large enough to accommodate the impeller assembly and associated internal passages. Furthermore, the housing preferably provides sufficient clearance between the stationary housing and the rotating impeller to avoid sliding contact and prevent leakage from occurring between the two stages of the blower. In addition to the clearance, the upper housing 1502 and the lower housing 1504 may be mirror images of each other.

[0114] Referring here to Figure 15D-F, the upper housing 1502 and the lower housing 1504 may have an inlet port 1510 and an outlet port 1512. Low-pressure steam from the evaporator / condenser enters the blower assembly 1500 through the inlet port 1510. In an exemplary embodiment, the inlet port is shaped to generate a helical flow around an annular flow channel in the upper housing 1502 and the lower housing 1504. After compressing the low-pressure steam, high-pressure steam is discharged through the outlet port 1512. The gap between the inlet port 1510 and the outlet port 1512 of the upper housing 1502 and the lower housing 1504 is reduced to prevent mixing of high-pressure steam exiting the blower assembly and low-pressure steam entering the assembly. An exemplary embodiment may include a stripper plate 1516. In this plate, the open flow channels provided in the upper housing 1502 and the lower housing 1504 allow only the high-pressure steam inside the impeller blade to pass through the region near the inlet port 1510, which is called the inlet region.

[0115] Referring again to Figure 15D-F, the carryover of high-pressure steam into the inlet region through the stripper plate 1516 may irreversibly mix with the incoming low-pressure steam entering the blower assembly 1500 from the inlet port 1510. The mixing of steam may cause an increase in the temperature of the incoming low-pressure steam. The carryover of high-pressure steam may also block the inflow of low-pressure steam due to the expansion of the high-pressure steam in the inlet region. The pressure reducing conduits 1514 in the upper housing 1502 and lower housing 1504 may extract the compressed steam sealed in the impeller blade and release the steam into the inlet region to block the inflow of low-pressure steam.

[0116] Referring again to Figure 15D-F, the distance between the inlet port 1510 and the outlet port 1512 is controlled by the size of the stripper plate 1516. In an exemplary embodiment, the stripper plate area is optimized to reduce the amount of high-pressure steam carried into the inlet area and to maximize the working flow channels in the upper housing 1502 and the lower housing 1504.

[0117] Referring here to Figure 15H-K, in an exemplary embodiment, the shaft 1514 is pressed into the impeller assembly 1506 and supported by a pressurized water supply bearing 1516, which is supported by the shaft 1514. In this embodiment, the bearing may be made of graphite. In alternative embodiments, the bearing may be made of materials including, but not limited to, Teflon composites and bronze alloys.

[0118] Referring again to Figure 15H-K, the water supplied to the pressurized water supply bearing 1516 when water may enter the compression chamber of the blower assembly 1500 is preferably clean water. When water enters the compression chamber, it will likely mix with pure steam. Contaminated water mixing with pure steam results in contaminated high-pressure steam. In the exemplary embodiment, the production water is supplied to the bearing.

[0119] For the high-speed blower bearing 1516 of the exemplary embodiment, hydrodynamic lubrication is desired. In hydrodynamic operation, the rotating bearing rests on a film of lubricant and does not come into contact with the stationary shaft. This mode of lubrication provides the lowest coefficient of friction, and since there is no physical contact between the components, wear is essentially absent.

[0120] Operation in other lubrication conditions, such as mixed film lubrication and boundary lubrication, results in higher power loss and higher wear rates than hydrodynamic operation. In exemplary embodiments, the blower may operate with hydrodynamic lubrication, film lubrication, or a combination of both. The operating clearance between the rotating bearing and the stationary shaft, the rotational speed of the bearing, and the lubrication fluid pressure and flow may influence the bearing lubrication mode.

[0121] Referring here to Figure 15H-K, in a hydrodynamic bearing, the limiting load factor may be affected by the heat dissipation capacity. Compared to unlubricated (or boundary lubricated) bearings, hydrodynamic bearings have an additional mechanism for dissipating heat. The most effective way for a hydrodynamic bearing to dissipate heat is to allow the lubricating fluid to carry away the thermal energy. In an exemplary embodiment, bearing supply water removes thermal energy from bearing 1516. In this embodiment, it is preferable that the volume of water flowing through the bearing is sufficient to maintain the bearing temperature within the operating limit. In addition, the diameter clearance may be varied to control the flow velocity of the bearing supply water, but it is preferable that these clearances are not so large as to generate a loss of hydrodynamic pressure.

[0122] Referring again to Figure 15H-K, the amount of bearing water supplied to the bearing 1516 is preferably sufficient to maintain hydrodynamic lubrication. Excessive bearing water may adversely affect the blower assembly 1500. For example, excess water may rapidly cool the high-pressure steam, unnecessarily reducing the thermal efficiency of the device. Another adverse effect of excess bearing water is that power loss may occur due to the shear of the water as it is discharged outward from the impeller assembly and pushed between the housing wall and the passing impeller blades.

[0123] Referring to Figure 15L, in an exemplary embodiment, a return channel 1526 for bearing supply water is provided within the blower to prevent excess bearing supply water from entering the impeller bucket.

[0124] Referring again to Figure 15H-K, in the exemplary embodiment, the bearing water supply pump maintains a pressure of 2-5 psi for input to the pressurized water supply bearing 1516. The flow velocity of the bearing water supply may be maintained by having a constant bearing water supply pressure. In the exemplary embodiment, the bearing water supply pressure may be controlled to ensure the flow velocity of the bearing water supply to the bearing 1516.

[0125] Referring again to Figure 15H-K, in the exemplary embodiment, the impeller assembly may be driven by a motor using a magnetic drive coupling rather than a mechanical seal. The absence of a mechanical seal does not result in frictional losses associated with the moving parts in contact with each other. In this embodiment, the magnetic drive coupling may include an inner rotor magnet 1518, a housing outer structure 1520, an outer magnet 1522, and a drive motor 1508.

[0126] Referring again to Figure 15H-K, the internal magnet rotor 1518 may be embedded in the cup. In exemplary embodiments, the magnets are arranged axially. In other embodiments, the axial arrangement may be radial. The cup may be made of plastic or metal material. In some embodiments, the material of the cup may be, but is not limited to, RYTON®, ULTEM®, or polysulfone. Similarly, the magnets may be made of materials including, but not limited to, ferrite, aluminum-nickel-cobalt, samarium-cobalt, and neodymium iron-boron. In exemplary embodiments, the cup is attached to the impeller assembly 1500. In exemplary embodiments, the cup is press-fitted onto the shaft 1514. Other methods for attaching the cup may include, but are not limited to, splines and set screws.

[0127] Referring again to Figure 15H-K, the magnetic coupling enclosure structure 1520 is positioned between the inner rotor magnet 1518 and the outer rotor magnet 1522. The magnetic coupling enclosure structure 1520 is a containment enclosure structure for the pressure vessel or blower assembly 1500. This enclosure structure seals the steam being compressed within the blower assembly 1500, preventing the steam from leaking into the surrounding environment.

[0128] Referring again to Figure 15H-K, since the outer casing structure 1520 is located between the inner rotor magnet 1518 and the outer rotor magnet 1522, eddy current losses may occur. If the outer casing structure 1520 is conductive, the rotating magnetic field may cause current to flow through the outer casing structure, resulting in power loss. Conversely, to reduce the amount of eddy current loss, an outer casing structure 1520 made of a highly electrical-resistive material is preferable. In exemplary embodiments, titanium may be used to manufacture the magnetically coupled outer casing structure 1520. This material provides a combination of high electrical resistance and corrosion resistance. Corrosion resistance is preferable because there is a possibility of contact between the bearing supply water and the outer casing structure 1520. In other embodiments, the outer casing structure 1520 may be made of a plastic material having higher electrical resistance and corrosion resistance. In these alternative embodiments, the outer casing structure 1520 may be made of materials including, but not limited to, RYTON®, ULTEM®, polysulfone, and PEEK.

[0129] Referring again to Figure 15H-K, the outer rotor magnet 1522 may be connected to the drive motor 1508. This motor rotates the outer rotor magnet 1522, which in turn rotates the inner rotor magnet, enabling the impeller assembly 1506 to compress low-pressure steam within the cavity defined by the upper housing 1502 and the lower housing 1504. In exemplary embodiments, the drive motor may be an electric motor. In alternative embodiments, the drive unit may be, but is not limited to, an internal combustion or Stirling engine.

[0130] Referring again to Figure 15H-K, the blower assembly 1500 may be configured as two single-stage blowers or two-stage blowers. In the operation of two single-stage blowers, the incoming low-pressure steam from the evaporator side of the evaporator / condenser is supplied simultaneously to both inlet ports of two separate stages of the blower. The first stage may be located at the bottom between the lower housing 1504 and the impeller assembly 1506, and the second stage may be located at the top between the upper housing 1502 and the impeller assembly 1506. As the impeller assembly 1506 rotates, the incoming low-pressure steam from the inlet ports 1510 of both stages is compressed simultaneously, and the high-pressure steam exits through the outlet port 1512 of the upper housing 1502 and the outlet port 1512 of the lower housing 1504.

[0131] Referring again to Figure 15H-K, in contrast, the two-stage blower has two different compression cycles. During the first compression cycle, low-pressure steam from the evaporator of the evaporator / condenser is supplied to the inlet 1514 of the lower housing. Compressed steam from the first stage exits through the outlet port 1516 of the lower housing and is supplied to the inlet port 1510 of the upper housing 1502. Compressed in the first stage, this steam is compressed again during the second stage. After the second compression cycle, the steam can exit the blower assembly 1500 through the outlet port 1512 of the upper housing 1502 at increased pressure.

[0132] For a given blower design, both two single-stage and two-stage blower configurations have distinct pressure-flow curves. These curves show that two single-stage blowers produce a higher steam velocity compared to a two-stage blower, which produces a higher pressure difference. Based on the system operating differential pressure, the blower velocity and efficiency depend on the blower's flow characteristics. Depending on the differential pressure across the blower assembly 1500, one configuration may be preferred over the other. In an exemplary embodiment, the blower assembly 1500 has a two-single-stage blower configuration.

[0133] Referring here to Figure 16-16A, an impeller assembly 1600 (also identified as 1506 in Figure 15) is located within an internal cavity defined by the upper housing 1502 and the lower housing 1504. The impeller assembly 1600 includes a plurality of impeller blades on each side of the impeller 1602 and a spindle 1604. In exemplary embodiments, the impeller 1602 may be manufactured from Radel®, and the impeller spindle 1604 may be manufactured from aluminum. In alternative embodiments, these components may be manufactured from materials including, but not limited to, titanium, PPS, and ULTEM®. Other materials may be used to manufacture these components due to the preference for their high temperature resistance and non-water absorption. In addition, the impeller spindle 1604 may have passages for returning bearing supply water to a reservoir. These passages prevent bearing supply water from entering the impeller bucket.

[0134] Referring again to Figure 16-16A, the blades are designed on each side of the impeller 1602 to generate a series of helical flows when the impeller is rotating. This flow causes the steam to repeatedly pass through the blades due to additional energy as the steam flows through the open annular channel. The number of blades and the volume of the buckets may be designed to optimize the desired flow velocity and pressure difference. The number of blades and the volume of the buckets are inversely proportional to each other, and therefore increasing the number of blades produces a higher pressure difference but a lower flow velocity. Labyrinth grooves on the outer circumference of the impeller 1602 prevent steam leakage over the stages of the blower assembly 1500, thereby increasing blower efficiency.

[0135] Referring again to Figure 15H-K, the shaft 1514 is mounted and stationary to the upper housing 1502 and the lower housing 1504. In exemplary embodiments, the shaft 1514 may be made of titanium. In other embodiments, the shaft 1514 may be made of materials including, but not limited to, aluminum oxide, silicon oxide, or titanium, as well as stainless steel with a coating to increase wear resistance and corrosion resistance. In addition, the shaft 1514 may have passages that carry bearing supply water to the shaft 1516.

[0136] Referring again to Figure 15H-K, the blower assembly 1500 in a two-stage blower configuration may generate a downward axial thrust force. This force is generated because the second stage at the top of the impeller assembly 1506 is under higher pressure compared to the first stage at the bottom of the impeller assembly 1506. In an alternative embodiment, this thrust force may be balanced by equal, opposite magnetic forces generated by offsetting the inner rotor magnet 1518 and the outer rotor magnet 1522. This configuration prevents excessive wear on the thrust surface of the lower pressurized water supply bearing 1516.

[0137] Referring here to Figure 17-17E, an alternative regenerating blower embodiment 1700 is shown. This embodiment may include an impeller housing assembly 1702, a mounting plate 1704, and a mounting flange 1706. For a cross-sectional view of the regenerating blower assembly 1700, see Figures 17B-D. For an exploded view of the regenerating blower assembly 1700, see also Figure 17E.

[0138] Referring here to Figure 17-17E, the mounting plate 1704 connects the mounting flange 1706 to the impeller housing assembly 1702. The mounting plate also provides a port that provides a fluid passage into the lower housing 1708 of the impeller housing assembly 1702, as shown in Figure 17E. In addition, the mounting plate provides a passage for bearing supply water to exit the blower assembly 1700.

[0139] Referring to Figure 17F-I, the impeller housing assembly 1702 may include the lower housing 1708, the impeller assembly 1710, and the upper housing 1712. Also, please refer to Figure 17H-I for a cross-sectional view of the impeller housing assembly 1702.

[0140] Referring here to Figure 17F-I, the lower housing 1708 and the upper housing 1712 define an internal cavity containing the impeller assembly 1710. This cavity provides volume for the impeller to compress the incoming low-pressure steam. The steam may enter the impeller housing assembly through inlet ports located within the lower housing 1708 and the upper housing 1712. After the low-pressure steam has been compressed by the impeller assembly 1710, the high-pressure steam may exit through outlet ports located within the lower housing 1708 and the upper housing 1712. For a detailed view of the lower housing 1708, see Figure 17J-K. In addition, the lower housing 1708 and the upper housing 1712 may be made of, but are not limited to, aluminum, titanium, PPS, and ULTEM®.

[0141] Referring again to Figure 17F-I, the upper enclosure 1712 may include an access cover 1714 attached to the top surface of the enclosure. For a top view of the upper enclosure 1712 with the access cover 1714 installed, see Figure 17L. This cover allows access to ports located inside the upper enclosure cover. For a top view of the upper enclosure 1712 without the access cover 1714 installed, see Figure 17M. This figure illustrates the inlet and outlet ports located inside the upper enclosure 1712.

[0142] Referring here to Figure 17N, the lower housing 1708 and the upper housing 1712 may include a pressure reducing conduit 1716 and a strip plate 1718 on the inner surface of the housing. These features perform functions similar to those described in the exemplary embodiment of the blower assembly 1500.

[0143] Referring here to Figure 18-18A, the internal cavity defined by the lower housing 1708 and the upper housing 1712 contains an impeller assembly 1800 (also identified as 1710 in Figure 17). This assembly may include a spindle 1802 and an impeller 1804 having blades, as shown in Figure 18-18A. When low-pressure steam enters the internal cavity of the impeller housing 1702, the impeller assembly 1800 compresses the steam as the assembly rotates.

[0144] Referring again to Figure 18-18A, the drive motor provides rotational energy to rotate the impeller 1804 and blades. A bearing 1716 may be located between the inner surface of the spindle and the shaft. These bearings support the shaft and allow the impeller 1804 to rotate freely. The bearing 1716 may be located near the end of the spindle 1802.

[0145] In alternative embodiments of the apparatus, the low-pressure vapor may be compressed using a liquid-sealed pump, such as the one described in U.S. Patent Application Publication No. 2005 / 0016828A1, published on January 27, 2005, entitled “Pressurized Vapor Cycle Liquid Distillation,” the contents of which are incorporated herein by reference. (Level sensor assembly) Referring now to Figure 19, an exemplary embodiment of the steam distillation apparatus 100 may also include a level sensor assembly 1900 (also identified as 108 in Figure 1). This assembly measures the amount of product water and / or discharge water produced by the apparatus 100.

[0146] Referring here to Figure 19-19A, an exemplary embodiment of the level sensor assembly 1900 may include a sedimentation tank 1902 and a level sensor housing 1904. The sedimentation tank 1902 collects any transported particulate matter in the discharge water before the water enters the discharge level sensor tank 1912. The tank removes particulate matter from the discharge water by reducing the velocity of the water as it flows through the tank. The sedimentation tank 1902 defines an internal volume. The volume may be divided approximately in half by using a fin 1905 that is close to the drain port 1908 and extends from the side wall opposite the drain port 1908. This fin 1905 may extend from the bottom to the top of the volume. The discharge enters through the inlet port 1906 and must flow around the fin 1905 before the water may enter through the level sensing port 1910. As the discharge enters the body of the container, the velocity decreases due to the increasing area. Any particles released may settle from the suspension due to a decrease in velocity. The sedimentation tank 1902 may be manufactured from any material having corrosion resistance and heat resistance. In exemplary embodiments, the housing is manufactured from RADEL®. In alternative embodiments, the sedimentation tank 1902 may be manufactured from other materials, including but not limited to titanium, copper-nickel, and stainless steel.

[0147] Referring again to Figures 19-19A, the sedimentation tank 1902 may have three ports: an inlet 1906, a drain 1908, and a level sensor support 1910. The inlet port 1906 may be located in the upper surface of the sedimentation tank 1902, as shown in Figures 19A-B, adjacent to the separation fins 1905 and opposite the drain port 1908. This port allows discharge water to enter the tank. The drain port 1908 may be located at the bottom of the sedimentation tank 1902, as shown in Figures 19A-B. The drain port 1908 provides access to the storage section to facilitate the removal of particulate matter from the tank. In exemplary embodiments, the bottom of the tank may be sloped toward the drain section, as shown in Figure 19B. The level sensor support 1910 may be located in the upper surface of the tank, as shown in Figure 19A, and adjacent to the separation fins 1905, but opposite the inlet port 1906. This port provides a fluid path to the discharge level sensor storage unit 1912. A fourth port is not shown in Figure 19A. This port allows discharge water to exit the level sensor assembly 1900 and enter the heat exchanger. This port is located inside one of the upper half side walls of the sedimentation tank 1902 and away from the inlet port 1906.

[0148] Referring again to Figure 19-19A, in the exemplary embodiment, the strainer may be installed in the flow path after the discharge water has exited the discharge level sensor storage unit 1912 and the sedimentation tank 1902. The strainer may collect larger particles while allowing the discharge water to flow to other device components. The strainer may be made of a corrosion-resistant material. In exemplary embodiments, the strainer is made of stainless steel. In addition, the filter element may be removable to facilitate cleaning of the element. The strainer removes particulate matter from the discharge water, limiting the amount of particulate matter that enters the heat exchanger. Excess particulate matter in the discharge water can clog the inner tubes of the heat exchanger with flakes and deposits, reducing the efficiency of the heat exchanger. In addition, particulate matter can cause blockages that obstruct the flow of discharge water through the heat exchanger.

[0149] Referring again to Figure 19-19A, the sedimentation tank 1902 is fluidly connected to the level sensor housing 1904. This housing may have three internal storage sections, including but not limited to the discharge level sensor storage section 1912, the product level sensor storage section 1914, and the bearing supply water storage section 1916. The discharge level sensor storage section 1912 is isolated from the other storage sections to prevent contaminants from mixing the product water with the discharge water. The level sensor housing 1904 may be manufactured from any material having corrosion resistance and heat resistance. In exemplary embodiments, the housing is manufactured from RADEL®. In other embodiments, the housing may be manufactured from other materials, including but not limited to titanium, copper-nickel, and stainless steel. In other embodiments, the ball float may have a range of motion of 45 degrees, and the housing may be shaped in various ways depending on the preference for a constant change in the volume of the fluid level during this movement.

[0150] Referring again to Figure 19-19A, the level sensor housing 1904 contains a discharge level sensor storage unit 1912. This storage unit is fluidly connected to the sedimentation tank 1902 via a measuring port 1910 located in the upper surface of the tank 1902. The storage unit provides a place where the velocity of the discharge water produced by the device may be measured using a level sensor 1918. As the discharge water fills the sedimentation tank, some of the water flows through the measuring port 1910 into the discharge level sensor storage unit 1912. In addition, a vent port 1923 may be located in the uppermost part of the storage unit. This port allows air to leak out of the storage unit, allowing the discharge water to fill the cavity. The volume of the storage unit must be sufficient to maintain the water level. A housing with insufficient volume may fill and discharge quickly, adversely affecting the function of the level sensor. In contrast, a storage unit with a large volume may have a slower level sensor response time due to slight changes in the height of the fluid level in response to a given increase or decrease in volume. A larger volume may also mitigate water level fluctuations generated by the operation of the device. Referring here to Figure 73, the discharge drain 7300 fluid path may be included in the level sensor assembly and fluidly connected to the level sensor assembly. In some embodiments, the discharge drain 7300 fluid path can be used to facilitate cleaning or flushing of the device 100. In some embodiments, the discharge drain 7300 fluid path may be sealed from the ambient environment by, for example, a manual ball valve, but the seal is not limited to a manual ball valve. In some embodiments, the valve may not be a manual valve, but may be, for example, a differential valve controlled by a control system, and in some embodiments, cleaning and flushing may be automated at least partially.

[0151] Referring again to Figure 19-19A, the product level sensor storage unit 1914 may be located next to the discharge level sensor storage unit 1912. The product level storage unit 1914 has an inlet port 1920 and an outlet port 1922. Product water enters the storage unit through the inlet port 1920 and exits the storage unit through the outlet port 1922. The outlet port 1922 may be located below the lower end measuring point of the level sensor to improve the outflow of water from the storage unit. Similarly, the inlet port 1920 may be located below the lower end measuring point of the level sensor to minimize the disturbance caused by the inflowing water. In an exemplary embodiment, the inlet port 1920 and the outlet port 1922 may be located on the side of the level sensor housing 1904, as shown in Figure 19A. This storage unit provides space for measuring the rate of the product being produced by the device. Furthermore, a vent port 1923 may be located in the upper part of the storage unit. This port allows air to escape from the storage section, enabling the production water to fill the cavity.

[0152] Referring again to Figure 19-19A, the product level sensor storage unit 1914 is fluidly connected to the bearing supply water storage unit 1916. The external port 1924, as shown in Figure 19C, provides a fluid path for product water to flow between the product level sensor storage unit 1914 and the bearing supply water storage unit 1916. The product water enters the bearing supply water storage unit 1916 through the external port 1924. In addition, the bearing supply water storage unit 1916 has a supply port 1926 and a return port 1928, as shown in Figure 19C. The supply port 1926 provides a fluid path for lubricating the bearings in the regenerative blower assembly. Similarly, the return port 1928 provides a fluid path for the product water to return from lubricating the bearings of the regenerative blower assembly. The supply and return ports may be located on the side of the level sensor housing 1904, as shown in Figure 19C.

[0153] Referring again to Figure 19-19A, an optical level sensor may be installed to monitor the amount of production water in the bearing supply water reservoir 1916. In an exemplary embodiment, the optical level sensor may be located at approximately two-thirds of the height within the bearing supply water reservoir 1916. The sensor senses the presence of water in the reservoir and indicates that there is enough water to lubricate the bearings. The sensor may also be installed by screwing it into a level sensor housing 1904. The sensor may include an O-ring to provide a watertight seal. In other embodiments, the sensor may be, but is not limited to, a conductivity sensor, a float switch, a capacitance sensor, or an ultrasonic sensor.

[0154] Referring here to Figure 19D-F, an alternative level sensor housing 1930 is shown, having two storage compartments. Within the level sensor housing 1930 is a discharge level sensor storage compartment 1932. This storage compartment is similar to and performs the same function as the aforementioned discharge storage compartment 1912 in the level sensor housing 1904. In contrast, here the product level sensor storage compartment 1934 contains product water to be supplied to the bearings of the regenerative blower. The bearing supply water storage compartment 1916 of the level sensor housing 1904 is eliminated from this configuration. Instead, product water is drawn from the product level sensor storage compartment to supply water for the regenerative blower.

[0155] Referring again to Figures 19D-19F, the product level sensor storage unit 1934 may have an inlet port 1935, an outlet port 1936, a return port 1938, and a supply port 1940. The inlet port 1935 allows product water to enter the storage unit. Similarly, the outlet port 1936 provides a fluid path for product water to exit the housing. Furthermore, the supply port 1940 allows product water to exit the storage unit and lubricate the bearings of the regenerating blower. After passing through the bearings of the regenerating blower, the product water may re-enter the product level sensor housing through the return port 1938. These ports may be located anywhere within the housing, but placing the supply port 1940 and the return port 1938 near the bottom of the housing may minimize adverse effects on the function of the level sensor.

[0156] Referring here to Figure 19G-H, the sensor 1942 may be positioned outside the level sensor housing 1904 to receive input from the level sensor assembly 1918. Upon receiving input from the level sensor assembly 1918, the sensor 1942 signals that the water level in the tank is within a specific range or at a specific level. In exemplary embodiments, the sensor may be a continuous analog sensor. This type of sensor provides continuous feedback about the position of the level sensor assembly 1918. As the magnet in the level sensor changes position, a change in voltage occurs, which is measured and used to determine the location of the sensor. Other embodiments may include, but are not limited to, a Hall sensor or a reed switch. Figure 19H illustrates one possible alternative embodiment of the level sensor assembly, which includes a set of floating magnets 1944 and a position magnet 1946. The position magnet 1946 is mounted on the side of the level sensor housing 1904.

[0157] Referring here to Figure 20-20A, level sensors 2000 (also identified as 1918 in Figures 19A and 19E) are located within the discharge level sensor storage unit 1912 and the product level sensor storage unit 1914. These sensors may include a base 2002, an arm 2004, and a floating ball 2006.

[0158] Referring again to Figure 20-20A, an exemplary embodiment of the level sensor 2000 may include a base 2002 that supports an arm 2004 and a floating ball 2006. The assembly also includes two magnets (not shown). The base is connected to the arm and floating ball assembly, which pivots on a small diameter axis (not shown). In addition, the base 2002 carries two magnets. These magnets are located 180 degrees apart from each other, on the surface of the base 2002, and parallel to the pivot point. In addition, these magnets may be arranged coaxially with the pivot point within the base 2002. In the exemplary embodiment, the magnets may be cylindrical magnets having an axial magnetization direction.

[0159] Referring again to Figure 20-20A, the level sensor 2000 measures the rotation of the arm and ball assembly relative to the pivot. In an exemplary embodiment, the maximum displacement angle is 45 degrees. In this embodiment, the level sensor is positioned to prevent the floating ball 2006 from being positioned directly below the pivot. In other embodiments, the maximum displacement angle may be as large as 80 degrees. The sensor may monitor the magnet through the walls of the housing. This configuration allows the sensor to be protected from corrosive discharge water and to seal the level sensor housing. The base may be manufactured from any material that is corrosion-resistant, heat-resistant, and non-magnetic. In an exemplary embodiment, the base 2002 is manufactured from G10 plastic. In alternative embodiments, the base 2002 may be manufactured from other materials, including but not limited to RADEL®, titanium, copper-nickel, and fiberglass laminates.

[0160] Referring again to Figure 20-20A, an arm 2004 is attached to the base 2002. The arm 2004 connects the base 2002 to the floating ball 2006. In the exemplary embodiment, the arm 2004 is made of G10 plastic material. Other materials may be used to manufacture the arm 2004 due to the preference for materials with sufficient high temperature resistance. Other materials may include, but are not limited to, stainless steel, plastic, RADEL®, titanium, and copper-nickel. The length of the arm is determined by the size of the level sensor housing. In addition, the exemplary embodiment has multiple openings located along and perpendicular to the longitudinal axis of the arm. These openings reduce the weight of the arm and allow the arm to be more sensitive to level changes.

[0161] Referring again to Figure 20-20A, a floating ball 2006 is attached to the other end of the arm 2004. The floating ball 2006 provides a surface area for contact with the water flow. The force applied to the floating ball 2006 by the water causes the level sensor assembly 2000 to pivot around a small diameter axis. The change in the position of this arm indicates the amount of water in the device. The floating ball may be made of any material having corrosion resistance and heat resistance. In addition, the material preferably has a low water absorption rate. In the exemplary embodiment, the floating ball is made of hollow stainless steel. For applications where the source water is highly concentrated, such as seawater, the floating ball 2006 may be made of any highly corrosion-resistant material, including but not limited to plastic, titanium, and copper-nickel. Furthermore, the floating ball 2006 is preferably sized appropriately to be placed within the level sensor housing 1904 so that the floating ball is free to move. In addition, the size of the floating ball 2006 is determined by the size of the level sensor storage unit.

[0162] Referring here to Figure 21-21A, a bearing water supply pump 2100 (also identified as 110 in Figure 1-1A) may be connected to the supply port 1926 of the bearing water supply reservoir 1916. The pump 2100 allows production water to flow from the bearing water supply reservoir 1916 to the regenerative blower. In exemplary embodiments, the flow rate is 60 ml / min and the pressure ranges from 2 psi to 2-1 / 4 psi. Any type of pump may be used, provided that the pump can provide a sufficient amount to maintain adequate lubrication flow to the bearings in the regenerative blower. In addition, the pump 2100 is preferably heat-resistant to withstand the high temperatures of the surrounding environment and the high temperatures of the production water passing through the pump. In exemplary embodiments, the bearing water supply pump 110 is a GOTEC linear positive displacement pump, model number ETX-50-VIC. In alternative embodiments, other types of pumps, such as centrifugal pumps, may be used, provided that the pump is capable of operating at high temperatures. (Control equipment) The apparatus may also include a manifold with multiple control valves for different water flow paths. Typically, this manifold may include control valves in the inlet piping for the source water to control the amount of water entering the apparatus. Since excessive pressure may prevent the control valves from opening, or once opened, from closing, a regulator may be included in the inlet piping to regulate the pressure of the source water.

[0163] Similarly, the manifold may also include a control valve within the outlet piping that carries the discharged water out of the device. This valve allows the operator to control the amount of discharged water that exits the device.

[0164] The control manifold may also include a control valve within the outlet piping for the produced water. This valve allows the operator to control the amount of produced water that exits the apparatus. In exemplary embodiments, there is one control valve for each section of the outlet piping. Similarly, the apparatus includes a vent valve to release gaseous compounds from the evaporator / condenser. The vent valve maintains the operating conditions of the apparatus by releasing small amounts of steam. Releasing steam prevents the apparatus from overheating. Similarly, releasing vapor prevents the accumulation of compounds in the condenser space, which can interfere with the device's function.

[0165] Typically, control valves may be of the same type. In an exemplary embodiment, the control device is a solenoid valve series 4BKR, model number 9-4BKR-55723-1-002, manufactured by SPARTAN SCIENTIFIC (Boardman, Ohio 44513). In alternative embodiments, the control device may be, but is not limited to, a proportional valve. The control valve is operated electronically using an electrical input of 0 to 5 volts.

[0166] The apparatus may also include a back pressure regulator, such as the one described in U.S. Patent Application Publication No. 2005 / 0194048A1, published on September 8, 2005, entitled “Backpressure Regulator,” the contents of which are incorporated herein by reference.

[0167] A steam distillation apparatus may include a voltage regulator. Typically, the apparatus may receive single-phase power from a conventional wall outlet. However, voltages may differ in other countries. To address this voltage difference, a voltage regulator may be included in the apparatus to ensure that the correct type of voltage is supplied to the electrical components of the apparatus.

[0168] In addition, a battery may be included in the system to provide electrical energy to the device. When electrical energy is supplied from the battery, the device preferably includes an electric inverter that converts the incoming electricity from direct current to alternating current. In other embodiments, the device may receive electrical energy from a Stirling and an internal combustion engine. These embodiments may also require an electric inverter. In other embodiments, the device may include a boost loop to increase the amount of voltage supplied to the device to power its electrical components. (Method of distilling water) This specification also discloses a method of steam distillation comprising the steps of filtering source water, heating source water using a heat exchanger, converting source water into low-pressure steam, removing water from raw material steam to produce dry low-pressure steam, compressing the dry low-pressure steam into high-pressure steam, and condensing the high-pressure steam into product water.

[0169] Referring here to Figure 22-22A, the source water is contaminated water that is converted into steam and later condensed into clean, pure water called production water. Figure 22 illustrates the fluid path of the source water in a previously disclosed apparatus. The source water enters the apparatus through an inlet pipe connected to a heat exchanger, as shown in Figure 22A. Typically, a pump may be installed to move the source water through the inlet pipe into the heat exchanger. A strainer 2202 may be installed in the inlet pipe between where the raw material enters the pipe and the connection to the heat exchanger (see Figure 22A). In other embodiments, a regulator 2204 may be located in the inlet pipe to regulate the flow of source water into the apparatus. Similarly, in one embodiment, a valve 2206 may be located in the inlet pipe to isolate the apparatus from the water source.

[0170] Referring again to Figure 22-22A, during operation, the source water passes through the strainer 2202 to remove large particles. These large particles can adversely affect the operation of the device by clogging the inlet and outlet valves or the inner tubes of the heat exchanger. Also, the particles can accumulate on the evaporator / condenser tubes, reducing the efficiency of the device. In the exemplary embodiment, the strainer 2202 is located before the control valve. In other embodiments, the strainer may be located before the inlet pump (not shown). In the exemplary embodiment, the strainer 2202 has a 50 μm user cleaner unit. In alternative embodiments, the device may not include the strainer 2202. After the source water has passed through the strainer 2202, the water enters the heat exchanger 2208.

[0171] Referring here to Figure 22B, the source water may fill the outer tube of the heat exchanger 2208 as it enters it. In an exemplary embodiment, the heat exchanger is a reverse-flow tube-in-tube heat exchanger. The source water enters the heat exchanger at approximately ambient temperature. Conversely, the production water and discharge water enter the heat exchanger at a higher temperature than the ambient temperature. The source water enters the heat exchanger at one end, and the production water and discharge water enter at the opposite end. As the source water flows through the heat exchanger, the high thermal energy of the production water and discharge water is conducted outward from the inner tube of the heat exchanger to the source water. This rise in the temperature of the source water allows the water to be converted to steam more efficiently in the evaporator / condenser.

[0172] Referring to Figures 22C-D, once the source water passes through the backflow tube-in-tube heat exchanger, the water exits the heat exchanger and enters the regenerative blower motor cooling loop. During operation, the regenerative blower motor 2210 generates thermal energy. This thermal energy must be removed from the blower motor 2210 for the blower to operate properly. As the source water passes through the blower motor cooling loop, the thermal energy generated by the blower motor is transferred to the source water. This heat transfer allows the blower motor to maintain a lower operating temperature and increases the temperature of the source water. A higher source water temperature increases the efficiency of the device because less energy is required to cause the phase change of the source water to steam. The source water exits the regenerative blower motor cooling loop and enters the evaporator / condenser through the reservoir 2212 shown in Figure 22E.

[0173] Figure 23-23A illustrates that the apparatus also contains a high-concentration source water called discharge water. This water removes particulate matter from the apparatus, preventing it from scaling down onto the evaporator / condenser tubes. This fluid may contain non-volatile contaminants that were present in the source water. These contaminants may include, but are not limited to, flakes from contaminants, heavy metals, or organic compounds. Specifically, these contaminants may include, but are not limited to, calcium carbonate and magnesium carbonate. In addition, the discharge water transfers thermal energy to the source water as it passes through the heat exchanger. Figure 23 shows the fluid path of discharge water in the previously disclosed apparatus. The discharge water is collected in the steam chamber 2302, as shown in Figure 23A. As low-pressure steam passes through the steam chamber 2302, water droplets are separated from the steam. These water droplets accumulate at the bottom of the steam chamber 2302 and are added to the existing discharge water. As the discharge water level increases, the water exits the steam chamber 2302 through ports. Through this port, the discharged water exits the steam chamber 2302 and enters the level sensor housing 2304 shown in Figure 23A.

[0174] Referring here to Figure 23B-C, the discharge water enters the level sensor housing 2304 and fills the sedimentation tank 2306. As the discharge water passes through the sedimentation tank 2306, particulate matter in the water settles at the bottom of the tank, thus separating the water from the particulate matter. Separating the particulate matter from the water prevents it from entering the heat exchanger. The heat exchanger may be adversely affected by the presence of particulate matter in the water. Particulate matter may accumulate in the inner tubes of the heat exchanger, making the heat exchanger less efficient. Particulate matter may reduce the discharge flow through the inner tubes, reducing the amount of thermal energy that can be transferred to the source water. In some cases, a group of particulate matter may cause blockages in the inner tubes, obstructing the flow of discharge water through the heat exchanger. As the discharge water fills the sedimentation tank 2306, the water may also fill the discharge level sensor storage unit 2308 shown in Figure 23C.

[0175] Referring here to Figure 23D-G, the discharge water may pass through the strainer 2310 before entering the heat exchanger 2312 shown in Figure 23E as it exits the level sensor housing 2304. The strainer 2310 removes any particulate matter remaining in the discharge water after it has flowed through the sedimentation tank 2306 of the level sensor housing 2304. Removing particulate matter from the discharge water reduces the accumulation of particulate matter in the heat exchanger and valves in the system. The discharge water enters the heat exchanger 2312 as shown in Figure 23E and fills one of the inner tubes. The water fills the heat exchanger 2312 as shown in Figure 23F. As the discharge water passes through the heat exchanger, thermal energy is transferred through the tubes containing the discharge water from the higher temperature discharge water to the lower temperature source water. The discharge water exits the heat exchanger as shown in Figure 23G. After exiting the heat exchanger, the discharge fluid passes through the mixing tank 2314 to prevent the steam being discharged from the apparatus from potentially harming individuals or nearby objects. Steam may be periodically discharged from the condenser space to maintain the apparatus's energy balance. Similarly, gaseous vapors (e.g., volatile organic compounds, air) must be cleared from the condenser space to maintain proper operation of the apparatus. Both steam and gaseous vapors are discharged into the mixing tank 2314, which contains low-temperature discharge water. Condensing the steam by mixing it with the discharge water allows for its safe discharge. In other embodiments, valves may be located in the tubing connecting the heat exchanger 2312 and the mixing tank 2314 to separate the mixing tank from the apparatus or to regulate the flow rate of the discharge water exiting the apparatus.

[0176] Referring here to Figure 24-24A, when high-pressure steam condenses upon contact with the outer surface of the tubes in the evaporator / condenser, product water is formed. Figure 24 shows the fluid path of product water in the previously disclosed apparatus. Product water is generated in the evaporator / condenser 2402, as shown in Figure 24A. As high-pressure steam condenses against the outer surface of the tubes in the evaporator / condenser, it forms water droplets. These water droplets accumulate at the bottom of the evaporator / condenser 2402, generating product water. As the product water level increases, the water exits the evaporator / condenser 2402 through a port and enters the level sensor housing 2404 shown in Figure 24A.

[0177] Referring here to Figures 24B-24E, the production water may enter the level sensor housing 2404 through a port connected to the product level sensor storage unit 2406 shown in Figure 24B. This storage unit collects the incoming production water and measures the amount of water produced by the apparatus. The water exits the product level sensor storage unit 2406 and enters the heat exchanger 2408 shown in Figure 24C. As the high-temperature production water passes through the heat exchanger 2408, it transfers thermal energy to the low-temperature source water through the inner tubes of the heat exchanger 2408. Figure 24D illustrates the production water passing through the heat exchanger 2408. After passing through the heat exchanger 2408, the production water exits the apparatus as shown in Figure 24E. In exemplary embodiments, the apparatus may include a product bypass valve 2410 and a product valve 2412. The product valve 2412 allows an operator to adjust the flow of production water exiting the apparatus. Typically, once the storage unit is 50 percent full, the product valve 2412 is circulated so that the amount of water entering the storage unit is equal to the amount leaving the storage unit. During the initial startup of the system, for the first few minutes of production, the product water being produced is rejected as waste by opening the product bypass valve 2410. Once the product is determined to be of sufficient quality, the product bypass valve 2410 closes and the product valve 2412 begins to operate.

[0178] Referring here to Figures 24F-24H, as the production water fills the production level sensor storage unit 2406, the water may also enter the bearing supply water storage unit 2410. The bearing supply water storage unit 2410 collects the incoming production water to lubricate the bearings in the regeneration blower 2412. The production water exits the bearing supply water tank 2410 and may enter the pump 2414 as shown in Figure 24G. The pump 2414 moves the production water to the regeneration blower. After exiting the pump 2414, the production water enters the regeneration blower 2412 as shown in Figure 24H.

[0179] Referring here to Figures 24H-24I, as the produced water enters the blower 2412, it provides lubrication between the bearing and the blower shaft. After exiting the regenerated blower 2412, the produced water may re-enter the level sensor housing 2404 through the bearing supply water storage unit 2410 (see Figure 24I).

[0180] Referring here to Figures 25-25C, vents may be provided to assist the flow of water throughout the apparatus. These paths assist the flow of water through the apparatus by removing air or steam from the apparatus. The vents are shown in Figure 25. Figure 25A illustrates a vent from the discharge level sensor storage unit 2502 to the steam chamber 2504 of the evaporator / condenser 2508. This path allows air in the storage unit to exit, enabling more discharge water to enter the storage unit. Similarly, Figure 25B illustrates a vent from the product level sensor storage unit 2506 to the evaporator / condenser 2508. This path allows air in the storage unit to exit, enabling product water to enter the storage unit. Finally, Figure 25C shows a vent from the condenser area of ​​the evaporator / condenser 2508, allowing air in the apparatus to exit the apparatus through the mixing tank 1510 into the ambient air. In addition, this vent helps maintain the balance of the device by releasing a small amount of steam from it.

[0181] Referring here to Figure 26, during operation, source water enters the reservoir 2602 of the evaporator / condenser 2608 in the manner described in Figure 22-22E. Once the source water first enters the reservoir 2602, a heating element may be used to transfer additional thermal energy to the water. Typically, the heating element may be used during the initial startup of the steam distillation apparatus. Otherwise, the heater is typically not used. As the amount of source water in the reservoir increases, the water flows out of the reservoir and into the evaporator / condenser tube 2604 through a port inside the plate 2606, which is positioned between the reservoir 2602 and the evaporator / condenser 2608, as shown in Figure 26. During the initial startup of the apparatus, the evaporator portion of the evaporator / condenser 2608 is filled with source water until a sufficient amount of water is present in the discharge level sensor reservoir. After the initial startup, the tube 2604 remains filled with source water.

[0182] Referring here to Figures 26A-26E, once the source water enters tube 2604, it is heated by the conduction of thermal energy through the tube wall from the high-pressure steam present outside tube 2604. Figure 26A illustrates the wet low-pressure steam flowing through tube 2604 of the evaporator / condenser 2608. The wet low-pressure steam travels through tube 2604 of the evaporator / condenser 2608 and enters the steam chamber 2610 illustrated in Figure 26B. As the steam flows through the steam chamber 2610, water droplets in the steam are separated from the steam. These water droplets collect at the base of the steam chamber 2610 and are added to the effluent already present at the base (see Figures 26C-D). The effluent flows out of the apparatus in the manner described in Figures 23-23G. The dry low-pressure steam exits the steam chamber 2610 and enters the regenerative blower 2612 as illustrated in Figures 26E-F.

[0183] Referring to Figure 26F-H, once the dry low-pressure steam enters the regenerative blower 2612, it is compressed to generate dry high-pressure steam. After the dry steam is compressed, the high-pressure steam exits the regenerative blower 2612 and enters the steam pipe 2614 of the steam chamber 2610. Refer to Figure 26G-H, which illustrates the steam exiting the blower 2612 and entering the steam pipe 2614 of the steam chamber 2610.

[0184] Referring here to Figure 26H-J, steam tube 2614 is fluidly connected to the internal cavity of the evaporator / condenser 2608. Steam tube 2614 provides an independent path for steam to enter the condenser side of the evaporator / condenser 2608 from the blower 2612. High-pressure steam is separated to maintain the steam pressure and to ensure that the steam is free of contaminants. Dry high-pressure steam exits steam tube 2614 in the steam chamber 2610 and enters the internal cavity of the evaporator / condenser 2608. Refer to Figure 26I, which shows the internal cavity of the evaporator / condenser 2608 containing high-pressure steam. As the high-pressure steam comes into contact with the outer surface of tube 2604 of the evaporator / condenser 2608, the steam transfers thermal energy to tube 2604. This energy is conducted through the tube wall to the source water located inside tube 2604. Once energy is transferred from the steam to the tube wall, the steam condenses from steam to fluid. This fluid is known as the product water. As droplets form on the outside of the tube wall, these droplets flow down to the base of the evaporator / condenser 2608. See Figure 26J, which shows the formation of product water in the internal cavity of the evaporator / condenser 2608. When the amount of product water in the cavity is sufficient, the product water may flow out of the evaporator / condenser, as shown in Figure 24-24I.

[0185] Referring to Figure 27, there are several factors that can affect the performance of the device being described. One of these factors is the pressure difference across the regenerative blower. Figure 27 is a graph illustrating the relationship between the amount of energy required to produce one liter of product and the change in pressure across the regenerative blower. Ideally, it is desirable to operate the blower so that the maximum amount of product water is produced using the minimum amount of electricity. From this graph, operating the blower with a pressure difference between 1.5 psi and 2 psi produces one liter of product water using the minimum amount of energy. Operating the blower at pressures above or below this range increases the amount of energy required to produce one liter of water.

[0186] Referring to Figure 28, another factor that can affect the performance of the device is the number of heat transfer tubes installed within the internal cavity of the evaporator / condenser assembly. Figure 28 illustrates the relationship between the number of heat transfer tubes and the production flow rate of produced water for a given change in pressure across the regenerative blower. From this graph, it can be seen that the more heat transfer tubes there are, the greater the production of produced water. In this graph, the configuration that produces the maximum amount of produced water per hour is an assembly with 85 tubes. The configuration that produces the minimum amount of water is an assembly with only 43 tubes for pressures of 2 psi or less.

[0187] Referring to Figure 29, this figure illustrates the amount of water produced by different heat transfer tube configurations. In this graph, the configuration with 102 heat transfer tubes produced the highest amount of water. In contrast, the configuration with shorter tubes, specifically only 48 tubes, produced the lowest amount of water.

[0188] Referring to Figure 30, the 48-tube heat transfer configuration produces more water per unit surface area, despite having fewer tubes than other configurations. Figure 30 illustrates the relationship between the amount of product produced and the size of the heat transfer surface area. This graph shows that the 48-tube heat transfer configuration with 15-inch tube lengths is the most efficient design. The least efficient configuration is the 102-tube heat transfer configuration. Therefore, while having a large number of tubes in the evaporator / condenser can produce more water, designs with fewer tubes may offer the most efficient use of resources.

[0189] Referring to Figure 31, this graph shows the performance differences between two 48-tube heat transfer tube designs. In this graph, the design difference is the length of the tubes. Across various pressure changes across the regenerative blower, this graph compares the amount of energy used and the water production flow rate for the two configurations. The configuration with 20-inch tubes produces slightly more product while consuming slightly less energy across a uniform pressure difference across the regenerative blower. (Control method) The pressure difference across the compressor directly determines the amount of product water the system can produce. The pressure difference across the compressor can be adjusted to ensure a specific amount of product water output from the system. Increasing the compressor speed typically results in an increase in the pressure difference across both the evaporator and condenser. Increasing the pressure difference increases the rate at which source water is evaporated into clean product water.

[0190] One of the limiting factors in controlling the steam distillation apparatus 100 is the amount of wastewater required to operate the machine. If there is insufficient wastewater, particulate matter separated from the source water will remain in the apparatus. This accumulation of particulate matter will adversely affect the operation and efficiency of the apparatus.

[0191] To ensure that particulate matter is removed from the device, there must be a sufficient amount of discharge water to transport the particulate matter out of the device. To determine how much discharge water is needed to operate the device in a particular environment, the amount of water entering the device (source water) must be known. If the source water has a high concentration of particulate matter, more discharge water will be needed to absorb and remove the particulate matter from the device. Conversely, if the source water has a low concentration of particulate matter, less discharge water will be needed.

[0192] Several different control methods may be implemented to control and monitor the amount of production water and discharged water produced by the apparatus. These methods may include, but are not limited to, the steps of measuring the water levels of production water and discharged water in storage units located within the apparatus, measuring the flow velocity of production water and discharged water produced by the apparatus, measuring the amount of inflow source water, and measuring the output amount of production water.

[0193] In the exemplary embodiment, the level sensor assembly may measure both the water level and the water flow velocity. The water level may be measured by the movement of the level sensor assembly. As water fills the reservoir, the water causes a change in the position of the level sensor assembly.

[0194] The water flow velocity may be determined by knowing the change in the position of the level sensor assembly, the area of ​​the storage section, and the time associated with the change in water level. Using a floating sensor to determine the flow is advantageous because there is no pressure drop due to the use of a floating sensor. The flow velocity may indicate the performance of the apparatus and whether that performance is consistent with the normal operation of the apparatus. This information allows the operator to determine whether the apparatus is functioning properly. For example, if the operator determines that the flow velocity is below normal operating conditions, the operator may examine the strainer in the inlet piping for impurities or the evaporator / condenser tubing for scale. Similarly, the operator may use the flow velocity to make adjustments to the apparatus. These adjustments may include steps to change the amount of discharged and produced water generated. While the flow velocity can indicate the performance of the apparatus, this measurement is not necessary.

[0195] To control the operation of a steam distillation apparatus, the water quality of either the influent source water or the effluent production water may be used. This control method determines the operation of the machine based on the water quality. In one embodiment, the conductivity of the production water is monitored. If the conductivity exceeds a specified limit, a sensor transmits a signal to stop the apparatus. In some embodiments, the sensor may be, but is not limited to, a conductivity sensor. In alternative embodiments, the step of monitoring the conductivity of the discharge water may be included. If the conductivity of the discharge water exceeds a specified limit, the sensor transmits a signal to increase the amount of source water entering the apparatus. Increasing the source water reduces the conductivity of the discharge water. In another embodiment, the conductivity of the source water may be monitored. If the conductivity exceeds a specified limit, the sensor transmits a signal to adjust the flow rate of the source water. A higher conductivity of the source water may result in a higher flow rate of both the source water and the discharge water.

[0196] In an alternative embodiment, the apparatus may include a control scheme in which the apparatus has a steady-state mode. During this mode, the apparatus reduces the amount of power consumed. In another embodiment, during this mode, a heating element may maintain a specific temperature or temperature range of the source water in the reservoir. Maintaining the temperature of the source water in the reservoir reduces the amount of time it takes for the machine to begin producing more productive water. In addition, during this mode, the regenerative blower is not functioning and the inlet and outlet valves are closed.

[0197] Examples of tests that may be performed on a water sample to analyze the quality of the source water include, but are not limited to, bacteriological, mineralogy, and chemical tests. Bacteriological tests indicate the amount of bacteria that may be present in the sample. The most common type of bacteriological test is the total coliform count.

[0198] Mineral analysis results may indicate the amount of mineral impurities in the water. Large amounts of minerals and other impurities can pose health hazards and affect the appearance and usability of the water.

[0199] Another type of water testing that may be performed is chemical testing. Many artificial chemicals can contaminate drinking water and pose health hazards to water consumers. Unless a specific chemical or a particular type of contaminant is suspected to be present in the water, this type of testing does not need to be performed routinely because it is expensive for unspecified chemical contaminants. However, if a specific chemical is suspected to be present in the source water, testing may be performed. Some examples of specific water quality tests are described below.

[0200] pH measures the relative acidity of water. A pH level of 7.0 is considered neutral. Pure water has a pH of 7.0. Water with a pH level below 7.0 is considered acidic. The lower the pH, the more acidic the water. Water with a pH greater than 7.0 is considered basic or alkaline. The higher the pH, the greater the alkalinity. In the United States, the pH of natural water is typically between 6.5 and 8.5. Freshwater sources with a pH below 5 or above 9.5 may not be able to provide nutrients to plant or animal species. pH may be determined using any known method in the art for testing.

[0201] Since pH is affected by temperature changes, it is preferable to measure it immediately at the source water testing site. Preferably, when using lakes, streams, rivers, puddles, etc., water samples are collected below the water surface, away from the "banks".

[0202] Nitrates—nitrogen is an element required by all living plants and animals to build proteins. In aquatic ecosystems, nitrogen exists in many forms. It may combine with oxygen to form compounds called nitrates. Nitrates may originate from fertilizers, sewage, and industrial waste. They can cause eutrophication of lakes and ponds. Eutrophication occurs when nutrients (such as nitrates and phosphates) are added to the water body. These nutrients usually originate from farmland, sewage, detergents, animal waste, and runoff from leaking septic systems. The presence of nitrates may be determined using any known method in the art for testing.

[0203] Turbidity - Turbidity refers to how clear or cloudy water is. Clear water has low turbidity levels, while turbid or muddy water has high turbidity levels. High levels of turbidity can be caused by suspended particles such as soil, sediment, sewage, and plankton. Soil may enter the water from nearby land through erosion or runoff. Sediment may be agitated by excessive activity in the water, for example, by fish or humans. Sewage is a result of waste runoff, and high levels of plankton may be due to excess nutrients in the water.

[0204] When water is highly turbid, it contains many suspended particles. These soil particles block sunlight, preventing aquatic plants from obtaining the sunlight they need for photosynthesis. The plants produce less oxygen, which in turn reduces the DO level. The plants wither more easily and are decomposed by bacteria in the water, which further reduces the DO level. Turbidity may be determined using any known method in the art for testing.

[0205] E. coli – The presence of coliform bacteria in tap water is an indication that the water may be contaminated with sewage or other putrefactive waste. Typically, coliform bacteria are found in large quantities on the surface film of water or in the sediment at the bottom.

[0206] Fecal coliforms, found in the lower intestines of humans or other warm-blooded animals, are a type of coliform bacteria. The presence of fecal coliforms in tap water is a clear indication that the water has been contaminated by sewage. Testing may be performed specifically for fecal coliforms or for all coliform bacteria, including all coliform strains, and may indicate fecal contamination. The presence of coliforms may be determined using any known method in the art for testing.

[0207] During operation, the water machine may perform conductivity tests on source water and / or production water to determine the quality of water entering and leaving the system. This test may be performed using conductivity sensors installed in the system's inlet and outlet piping. Water with high conductivity indicates that the water contains a greater amount of impurities. Conversely, water with lower conductivity indicates that the water contains lower levels of impurities. This type of test is comprehensive and provides only a general indication of the purity / quality of the water being analyzed.

[0208] Other types of tests may be performed to analyze specific levels of impurities / characteristics in water, including but not limited to pH, hardness, chloride, color, turbidity, sulfates, nitrites, nitrates, and E. coli. Typically, to analyze water entering or leaving a machine, the operator may first take a sample of the water. After obtaining the desired sample, the water may be tested using a water testing kit available from Hach Company (Loveland, Colorado 80539-0389). Other methods for testing water purity may include the step of sending the water to a laboratory for analysis. (A system for distilling water) This specification discloses cases in which a previously disclosed apparatus for distilling water may be implemented in a distribution system, as described in U.S. Patent Application Publication No. 2007 / 0112530A1, issued on May 17, 2007, entitled “Systems and Methods for Distributed Utilities,” whose contents are incorporated herein by reference. Furthermore, a monitoring / communication system may also be included in the distribution system, as described in U.S. Patent Application Publication No. 2007 / 0112530A1, issued on May 17, 2007, entitled “Systems and Methods for Distributed Utilities,” whose contents are incorporated herein by reference. (Alternative embodiment) While exemplary embodiments of stills / steam distillation apparatuses have been described, alternative embodiments of stills are considered, including alternative embodiments of specific elements of the still (i.e., heat exchangers, evaporators / condensers, compressors, etc.). Therefore, in some alternative embodiments, one or more elements are replaced with elements of the alternative embodiments described herein. In some embodiments, the entire still is replaced by the alternative embodiment; for example, a system as described in one embodiment utilizes the exemplary embodiment as a still, while in other embodiments, the system utilizes the alternative embodiment.

[0209] Referring to Figures 32-32C, an alternative embodiment of a steam distillation apparatus having a liquid-sealed pump 3200 is disclosed. The ring pump may include a fully rotating housing, which provides the greatest reduction in friction losses while still maintaining the design simplicity and cost-effectiveness of production shown in Figures 32-32C. As shown in Figure 32, the stator 3202 is stationary relative to the rotor 3204 and comprises an inlet 3206 and an outlet 3208. Steam is drawn in at pressure P1 and enters the rotor chamber 3210. The rotor 3204 is offset from the central axis Z, on which the rotating housing and the center of the liquid-sealed pump are located. As the rotor 3204 revolves around the central axis 3212 together with the rotor bearing 3214, the effective volume of the chamber 3210 decreases. Thereafter, the steam is compressed to pressure P2 as it is transported along the rotating path into the outlet 3208 and sent to the evaporator / condenser 104 in Figure 1. Preferably, a rotating housing (not shown) rotates together with the liquid ring inside the liquid-sealed pump to reduce energy loss due to friction.

[0210] Referring to Figures 32A-B, the stator 3202 has a support structure 3216 in the input and output regions. Below the support structure 3216 in the top view of the stator 3202 shown in Figures 32A-B, the individual blades 3218 of the rotor 3204, as well as the concentric arrangement of the rotor 3204 around the central axis, can be seen. This particular embodiment of the fluid-sealed pump is supplied axially and discharged axially, and may have vertical, horizontal, or other orientations during operation. Figure 32C shows yet another illustration of this embodiment.

[0211] The liquid-sealed pump 3200 is generally designed to operate within a very narrow range of input and output pressures, so that the apparatus operates in the range of 5 to 15 psig. The pressure of the apparatus may be regulated using a check valve that releases vapor from the chamber 3210, as shown in Figure 32-32C. Improved apparatus performance is preferably achieved by positioning the exhaust port outlet 3208 at a specific rotation angle around the rotor shaft, where the specific angle corresponds to the desired pressure increase for the distillation operation. One embodiment of a specific port opening angle for regulating the pressure of the apparatus is shown in Figure 32A. The outlet 3208 is positioned at approximately 90 degrees of rotation around the rotor access, allowing vapor to be discharged from the chamber 3210. Positioning the outlet 3208 at a high rotation angle around the stator shaft increases the pressure of the apparatus and decreases the pump's output, while positioning the outlet 3208 at a lower angle around the stator shaft results in lower apparatus pressure and increased pump output. Improved pump efficiency may be achieved by selecting the arrangement of outlet 3208 to optimize the pressure in the apparatus. Furthermore, the arrangement of outlet 3208 for maintaining the pressure in the apparatus may minimize the complexity of the apparatus by eliminating a check valve at the exhaust port to chamber 3210, thereby providing a simpler and more cost-effective compressor.

[0212] Referring here to Figure 32D, it may be desirable to measure the depth of the liquid ring in the compressor in order to optimize performance during operation. In embodiments disclosed herein, the liquid-sealed pump housing 3232 rotates with the liquid ring in the pump, and the fluid temperature is typically about 110°C. Methods for measuring the depth of the ring include any one of the conventional methods, such as using ultrasonic, radar, float, fluid conductivity, and optical sensors. Due to the complexity of the rotating housing, the use of a capacitive sensor is a preferred embodiment for this measurement, as the capacitance of the capacitor changes as the depth of the fluid in the capacitor changes.

[0213] Referring again to Figure 32D, the disc-shaped capacitor sensor plate 3234 is mounted on the bottom of the rotating housing 3232, equidistant from the bottom surface 3232A of the rotating housing 3232 and the bottom surface 3204A of the rotor 3204. Thus, the capacitor is defined by the housing 3232, the rotor 3204, and the capacitor sensor 3234. A lead 3240 connects the capacitor from the capacitor sensor 3234 through a passage 3236A in the rotating housing shaft 3236 to the secondary section 3242 (not shown) of a ferrite core transformer, preferably. In one embodiment, the secondary section 3242 rotates at the same speed as the capacitor plate and is inductively connected to the primary section of the ferrite core transformer. The primary winding 3238 is stationary, and signals traveling back and forth across the level measuring capacitor are transmitted through the transformer, thus enabling the transmission of depth information from the rotating position to the stationary position. Capacitance is measured by determining the LC resonance of the capacitor (C) caused by the inductance (L) of the secondary section of the transformer. In an exemplary embodiment, an LC oscillator circuit is constructed, and the oscillation frequency is used as a measure of capacitance.

[0214] Referring to Figure 32E, this figure illustrates an alternative design for the pump 3200 to prevent contamination and transport of contaminating fluid droplets along with the vapor into the evaporator / condenser 104 in Figure 1. In such an embodiment, the liquid-sealed pump 3200 is located in the headspace of the evaporator / condenser 104, and as the rotating housing 3232 rotates, the spray is removed, and the rotation generates a cyclone effect, which, by centrifugal force, propels the spray and water droplets, forcing them to collide with the distiller housing and flow down into the water in the reservoir. There may also be fins 3244 extending from the outside of the rotating housing 3232 to enhance the circulation and rotation of vapor in the annular space between the rotating housing 3232 and the stationary housing 3228. The outlet 3242 is provided for the flow passage to the evaporator / condenser 104.

[0215] Referring here to Figure 32F-G, an alternative embodiment of the liquid-sealed pump 3200 may include a ring pump 3252, which has a single two-channel stator / body 3256 and an outer rotating housing 3254 surrounding a rotor 3258, where the sealing surface between the rotating housing 3254 and the stationary stator / body 3256 is a cylinder. The two-channel stator / body 3256 is kept stationary with respect to the chamber 3260 of the pump 3252, as well as the rotor 3258 and the rotating housing 3254, and has an inlet 3262 and an outlet 3264. Steam is drawn in at P1 and passes through the inlet 3266. As the rotor rotates around the stationary stator 3256, when the inlet 3266 coincides with the intake hole 3268 of the rotor 3258, the steam passes through the intake hole 3268 into the rotor chamber 3270. As the rotor 3258 rotates, it is offset from the central axis Z such that the effective volume of the rotor chamber 3270 decreases. In this way, the steam is compressed to pressure P2 as it is transported along the rotating path to the outlet hole 3272 of the rotor 3258. As the rotor 3258 rotates, the outlet hole 2 coincides with the outlet 3274 of the stationary outlet 3264, and the steam at pressure P2 passes through the outlet 3274 into the outlet 3264 which is sent to the evaporator / condenser. In such an embodiment, the rotating housing 3254 rotates with the water 3276 present in the chamber 3260, thereby reducing frictional energy loss due to windage. There may also be small holes 3278 present in the housing 3254 to allow the water 3276 to enter and exit the chamber 3260, thereby controlling the fluid level in the pump. In addition, the rotor 3258 has multiple blades 3280, which are easily visible when the rotor 3258 is viewed from above, as shown in Figure 32G. The individual rotor chambers 3270, as well as the individual intake holes 3268 and exit holes 3272 for each rotor chamber 3270, are also easily visible in this figure.

[0216] Referring to Figure 32H, an alternative embodiment of a liquid-sealed pump is present, in which the interface between the rotary housing 3254 and the stator 3256 is conical rather than cylindrical. In this embodiment, the rotor drive shaft 3282 has an end 3286 positioned on a bearing 3284, which allows the rotary rotor housing 3254 to rotate together with the rotor 3258. The inlet 3262 and outlet 3264, along with the corresponding inlet 3266 and outlet 3274, are kept stationary relative to the rotor 3258 and rotor housing 3254.

[0217] Referring here to Figures 32F, H, and I, further embodiments may include a conical or axial seal 3282 located between the stationary sections 3264 and 3262 and the rotor 3258. In the conical embodiment, most clearly seen in Figure 32I, the seal 3282 thereby separates the inlet 3266 from the outlet 3274 of the rotor 3258 to prevent leakage. In contrast to the embodiment of the fluid-sealed pump discussed with respect to Figures 32-32C (see above), which is supplied axially and discharged axially, the fluid-sealed pump shown in Figures 32E-I and 7 is supplied axially and discharged radially.

[0218] In alternative embodiments, the steam distillation apparatus may include a back pressure regulator. The back pressure regulator may help maintain safe and optimal operation of the process being carried out under pressurization. During operation, the steam distillation apparatus may include a back pressure regulator to purify brackish or seawater into drinking water, and excessive pressure in the apparatus generated from volatile components at startup or from a compressor operating outside specifications may be dangerous to the operator if such pressure is not safely relieved. Similarly, volatile components present in the feedstream at startup may present contaminants that interfere with the proper operation of the apparatus. The back pressure regulator may function to relieve the excess pressure and return the apparatus to the desired operating pressure.

[0219] The aforementioned embodiments of steam distillation apparatus generally operate above atmospheric pressure, typically around 10 psig. Such apparatus advantageously offer higher vapor density at higher pressures, thereby allowing more vapor to be pumped through the positive displacement pump than at lower pressures. The resulting higher yield provides improved overall system efficiency. Furthermore, the higher yield and higher system pressure reduce the power required for the compressor and eliminate the need for two additional pumps: one for pumping the concentrated product and another for pumping the discharge flow. The overall structure is simplified as many shapes tolerate internal pressure better than external pressure. Importantly, operating at ultra-atmospheric pressure reduces the impact of minor leaks on overall efficiency and performance. Non-condensable gases such as air inhibit the condensation process and expand below atmospheric pressure, in which case minor leaks act as air intake, which does not occur in systems operating at ultra-atmospheric pressure.

[0220] Referring here to Figures 33 and 33A, these figures show a back pressure regulator that may be incorporated into the steam distillation apparatus 100 when the apparatus is operated at atmospheric pressure or above. The back pressure regulator 3300 has a vessel 3302 containing an opening 3304. One side of the opening is connected to a pressurized conduit of the apparatus (e.g., the outlet of a compressor in a steam compression distillation apparatus), which may be exposed to constantly fluctuating high pressures. The other side of the opening terminates in a port 3306. The port 3306 is covered by a spherical movable stop 3308. The stop 3308 is held in an arm 3310 using a retainer 3312 at a fixed distance from a pivot pin 3314. The arm 3310 is attached to a point fixed in relation to the opening port 3306 by a hinge via the pivot pin 3314. The arm 3310 includes a counter mass 3316 suspended from the arm, which is movable along axis 3318 so that the distance between the counter mass 3316 and the pivot pin 3314 may vary. In the embodiment shown in Figure 33, the axial direction of the opening 3304 is perpendicular to the direction of the gravity vector 3320. The back pressure regulator may also include a housing to prevent foreign matter from entering the regulator and interfering with the function of its internal components.

[0221] Referring again to Figures 33 and 33A, during operation, when the pressure in the pressurized conduit is below a given setpoint, the arm 3310 maintains a horizontal position with respect to the direction of gravity 3320. This arm position is known in this embodiment as the closed position and corresponds to the stop 3308 covering the port 3306. When the pressure in the conduit exceeds the setpoint, a force acts on the stop 3308, resulting in a torque acting around the pivot pin 3314. The torque acts to rotate the arm 3310 around the pivot pin 3314 in a counterclockwise direction, moving the arm away from its closed position and exposing the port 3306, allowing fluid to leak out of the opening 3304. When the pressure in the conduit is below the setpoint, the force of the gas is no longer sufficient to keep the arm 3310 away from its closed position, and therefore the arm 3310 returns to the closed position, and the stop 3308 covers the port 3306.

[0222] Referring again to Figures 33 and 33A, the arm 3310 acts as a lever in generating an adjustable moment, and the countermass 3316 multiplies the force applied to the port 3306 through the stop 3308. This force multiplication reduces the weight required to close the opening 3304, in contrast to designs where only the stop 3308 acts vertically on the top of the opening 3304, as in the case of a pressure cooker. Thus, a large port size may be covered by a relatively lightweight and large stop to promote rapid airflow from the pressurized conduit, and the countermass acts to adjust the desired setpoint, thus requiring less design effort in selecting a particular port size and stop properties. The addition of the shaft 3318 for adjusting the position of the countermass 3316 allows for a change in the multiplier ratio in this embodiment. As the countermass 3316 is moved closer to the pivot pin 3314, the multiplier ratio is reduced, generating a lower closing force. If the counter mass 3316 is moved further away from the pivot pin 3314, the multiplier ratio increases, and thus the closing force increases. Thus, the position of the counter mass 3316 effectively acts to adjust the setpoint of the back pressure regulator.

[0223] Adjusting the back pressure regulator setpoint may be useful when the back pressure regulator is used at higher altitudes. When atmospheric pressure is lower, the operating pressure of the apparatus is correspondingly lower. As a result, the temperature of the distillation apparatus decreases, which can adversely affect the performance of the apparatus. Similarly, such adjustments allow the end user to identify the desired back pressure regulator setpoint. The use of a counter mass to apply closing force may also reduce the cost of the back pressure regulator and reduce component fatigue. In certain embodiments, the adjustable counter mass is designed to allow a range of setpoints with a minimum setpoint of substantially 10 psig or less and a maximum setpoint of substantially 17 psig or more. Thus, various embodiments allow for precise pressure regulation of the apparatus, unlike devices that merely serve as safety relief valves.

[0224] Referring here to Figures 33B-C, these figures illustrate an alternative embodiment of the back pressure regulator 3300 having an opening 3326 configured such that port 3328 is oriented perpendicular to the direction of gravity 3320. Thus, other embodiments may be adapted to any opening orientation while maintaining the use of an adjustable countermass.

[0225] The back pressure regulator may be configured to allow a small leakage rate below the setpoint in order to clear the accumulation of volatile gases, which act to insulate heat exchange and suppress boiling in the system. However, the regulator is designed to allow the pressure to gradually increase in the pressurized conduit despite this small leakage. In one embodiment, below the setpoint of the back pressure regulator, the release of volatile components from the pressurized conduit may also be achieved through a specially designed leak vent while the back pressure regulator arm is in the closed position. The leak vent is configured to allow a certain leakage rate from the port or opening while the pressure in the conduit is below the setpoint. Such a leak vent may be designed by various means known to those skilled in the art. Non-limiting examples include the steps of: specifically positioning a stop and port to allow a small opening while the arm is in a closed position; designing the port such that a small opening that cannot be covered by the stop is always exposed; specifying a non-elastic seal configuration of a certain rigidity between the stop and the port when the arm is in a closed position; and configuring an opening leading to the port such that it has a small opening to allow fluid leakage.

[0226] Referring here to Figures 33D-G, these figures illustrate alternative embodiments of the back pressure regulator 3300 that allow volatile leakage below a set point. In one alternative embodiment, port 3332 has a notch 3334 as shown in Figure 33D, and an enlarged view of area C in Figure 33D is shown in Figure 33E. Thus, when the stop is in contact with port 3332, the arm of the back pressure regulator is in the closed position, and the leak vent is located at the notch 3334, which allows fluid leakage. In another alternative embodiment of the back pressure regulator 3300, opening 3336 has a small opening 3338 as shown in Figure 33F, and an enlarged view of area E in Figure 33F is shown in Figure 33G. Opening 3338 is configured such that when the stop covers port 3336, a leak vent is created, as fluid may leak through opening 3338.

[0227] Various features of the back pressure regulator may be modified or altered. For example, the stop used with the back pressure regulator may have any shape, size, or mass that matches the desired operating conditions, and such stop does not have to be spherical, as shown in some embodiments discussed herein. Similarly, to modify the setpoint of the regulator, stop parts of similar size but different weights may be used with the retainer. Likewise, counter masses of different sizes, shapes, and masses may be used with various embodiments, depending on the preference that they are adapted by the shaft and arm configuration (compare 3316 in Figures 33 and 33A with 3330 in Figures 33B and 33C). Such counter masses may be attached to and oriented with respect to the arm by any of the various techniques that are obvious to those skilled in the art. The arrangement of the pivot pins does not have to be as shown in Figures 33-33C, but may be placed wherever advantageous it is to provide the mechanical advantages required to achieve a particular pressure setpoint.

[0228] Referring again to Figure 33, other embodiments of the back pressure regulator 3300 may optionally utilize the aforementioned drain port features. Alternatively, embodiments of the back pressure regulator 3300 may not utilize the countermass force adjustment features and may rely on specific properties of the stop section to provide the set point for the back pressure regulator.

[0229] Other embodiments of the steam distillation apparatus do not utilize a vessel but rely on an opening that is essentially part of the system. In such cases, the back pressure regulator arm may be directly mounted to a part of the system so that the arm, stop, and counter mass are properly oriented for the operation of the regulator.

[0230] Referring here to Figure 34, the container 3302 includes a drain port 3322. Since the back pressure regulator 3300 may operate within the bounded region 3402 of the large-scale system 3400, the drain port 3322 serves as a pathway to discharge fluid that is swept from the pressurized conduit 3404 through the opening 3304 into the bounded region 3402. The drain port 3322 may connect the bounded region 3402 to another region of the large-scale system or to the external environment 3406. In addition, the accumulation of gas in the bounded region 3402 may result in the condensation of such gas. The gas swept through the opening 3304 may also be mixed with droplets of fluid that may accumulate in the bounded region 3402. Therefore, the drain port 3322 may also be used to clear the accumulation of condensates that accumulate in the bounded region 3402. The condensates may also be discharged from the bounded region using a separate opening 3408.

[0231] Referring now to Figure 35, in an alternative embodiment, the apparatus may maintain a constant discharge water flow to prevent debris and other accumulation in the apparatus, as follows: The water level 3502 in the head chamber 3504 is regulated through a feedback control loop using a level sensor L1, a valve V1, and a raw material pump 3506 to maintain an appropriate water flow through the discharge flow 3508. A three-way raw material pump filling valve 3510 is set to pump water into the reservoir 3512, which raises the water level 3502 in the head chamber 3504. As the fluid level 3502 in the head chamber 3504 rises, the fluid overflows the dam-like barrier 3514 into the discharge control chamber 3516 containing the discharge level sensor L1. If necessary, the discharge valve V1 is controlled so that the water flow from the discharge control chamber 3516 through the heat exchanger 3518 extracts heat, cools the discharge flow 3508, and flows out through the volatilizer mixer 3520 and valve V1, thereby allowing the high-temperature gas and steam 3522 from the evaporator section 3524 to cool, and then the discharge flow to the waste 3526.

[0232] Referring again to Figure 35, the apparatus may also maintain proper production logistics as follows: The product level 3528 increases in the condenser chamber 3530 and enters the product control chamber 3532, which houses the product level sensor L2. Using a feedback control loop together with the level sensor L2 and valve V2, the production logistics 3534 is controlled to flow from the product control chamber 3532 through the heat exchanger 3518, extract heat to cool the production logistics 3534, and then exit through valve V2 to complete the production logistics as a production water outlet 3536.

[0233] The system may preferably be configured to maintain the proper water level of the liquid-sealed pump 3538 by using a fluid recovery system to replenish fluid losses. There are several ways in which fluid may be depleted from the ring pump during system operation, including leakage into the lower storage section 3540, discharge through the exhaust port 3542, and evaporation. Leakage and removal losses can be highly dependent on operating parameters such as rotational speed and the flow rate of the liquid-sealed pump 3538. These leakage and removal losses may require a complete replacement of the fluid in the pump several times per hour. Evaporation losses are typically minimal.

[0234] Referring to Figure 35, the fluid level in the ring pump 3538 may be maintained by adding additional source water or production water, or, preferably, by recirculating the liquid water lost from the liquid-sealed pump for improved system efficiency. In one embodiment, the fluid level in the ring pump 3538 is maintained primarily by recirculating the fluid accumulated in the lower storage unit 3540. Fluid may accumulate in the lower storage unit 3540 by leakage from the liquid-sealed pump 3538 and by fluid discharged into the exhaust pipe 3542, captured by the mist remover 3544, and fed into the lower storage unit 3540. Alternatively, the fluid discharged into the exhaust pipe 3542 and captured by the mist remover 3544 may be returned through the exhaust port of the liquid-sealed pump. The fluid accumulated in the lower storage unit may be recirculated by one of several pumping mechanisms. One exemplary method is to use a siphon pump.

[0235] Referring again to Figure 35, the minimum water depth is preferably maintained in the lower storage section for the siphon pump to function properly. In one embodiment, a fluid-seal pump control chamber 3546 housing a fluid-seal pump level sensor L3 may be used to control the fluid-seal pump level and the water level in the lower storage section 3540. The fluid-seal pump control chamber 3546 is fluidically connected to the fluid-seal pump 3538 and the lower storage section 3540. The fluid-seal pump 3538 is connected to a three-way raw material filling valve 3510, which is set to open when the fluid-seal pump 3538 needs more water, and is also connected to a fluid-seal pump drain valve V3, which opens when it is necessary to discharge water from the fluid-seal pump 3538 into the discharge flow 3508.

[0236] Referring again to Figure 35, if recirculated water from the lower storage unit 3540 is not primarily used to maintain the fluid level in the liquid-sealed pump 3538, either chilled source water or production water may be used. If source water is used, introducing chilled water (which may be about 85°C lower than the system temperature) into the liquid-sealed pump 3538 reduces system efficiency, or, alternatively, using a preheater for such chilled source water increases the system's energy balance. Alternatively, using production water does not adversely affect the system temperature but reduces the production level and therefore can lead to system inefficiency. At startup, the initial fluid level of the liquid-sealed pump is preferably supplied from source water.

[0237] Referring here to Figure 35A, in one embodiment, the start-up time may be shortened by using an external connecting valve 3550 between the feed 3548 and discharge 3508 fluid lines, located adjacent to the low-temperature heat exchanger 3518. To determine the fluid level in the evaporator head 3504 during initial filling, the connecting valve 3550 is opened, the discharge valve BV is closed, and fluid is fed into the system through the feed line 3548. Connecting the discharge 3508 and feed 3548 lines results in equal fluid heights in the discharge level sensor housing 3516 and the evaporator head 3504, thereby enabling the determination of the fluid level in the evaporator head 3504 and allowing the evaporator to be filled to the minimum required level at startup. Using the minimum required level shortens the preheating time and prevents overflow from the evaporator head 3504 through the liquid-sealed pump 3538 to the condenser 3552 when the liquid-sealed pump 3538 is started, as shown in Figure 35.

[0238] Referring again to Figure 35A, the concentration of solids in the discharge stream 3508 may be monitored and controlled to prevent precipitation of substances from the solution, and thus clogging of the system. Also, during startup, the circulation pump 3554 may circulate water through the heat exchanger 3518 to preheat the heat exchanger to the appropriate temperature for normal operation. Conductivity sensors (not shown) may be used to determine the total dissolved solids (TDS) by measuring the electrical conductivity of the fluid. In certain embodiments, the sensor is an inductive sensor, so that no conductive material is in contact with the fluid flow. For example, during seawater distillation, if the TDS content in the discharge stream 3508 rises above a predetermined level, the supply rate of the fluid source is increased. Since the production of distilled water changes only slightly as a function of the fluid supply rate, increasing the supply rate of the fluid source increases the velocity of the discharge stream 3508, and the increased discharge stream velocity results in a reduced concentration of TDS, thereby maintaining the overall nationality and productivity of the system.

[0239] Alternative embodiments also include a fluid control system that uses a level sensor and a variable flow valve in a feedback configuration. Optimal operation of the distiller requires that the total fluid inflow closely matches the total fluid outflow. Maintaining a nearly constant fluid level in the distiller fulfills this requirement. In certain embodiments, the sensor is a volumetric level sensor, which is a particularly robust sensor for measuring the fluid level. Volumetric level sensors have no moving parts, are less sensitive to contamination, and are simple and inexpensive to manufacture. The opening of the variable flow valve is controlled by the fluid level measured by the volumetric level sensor, thereby adjusting the fluid level at the location of the level sensor. A rising fluid level causes the valve to open further, increasing the outflow from the sensor volume. Conversely, a falling fluid level causes the valve to close further, decreasing the outflow from the sensor volume.

[0240] The flow velocity from the input pump, passing through the variable flow control valve, may be determined using in-situ calibration techniques. Level sensors and associated level sensor volumes may be used to determine the filling or discharging rate of the sensor volume. By appropriately configuring the control valves, the flow velocity calibration of each valve, and also the flow velocity calibration of the raw material pump, may also be determined.

[0241] In one embodiment, a valve block (not shown) may be used to integrate all control valves of the system into a single component, which may be integrated with the fluid flow manifold. A control system may also be incorporated, comprising a sensor for total dissolved solids and a discharge flow, as well as other devices for controlling the height / level of the fluid in the floating valve or head.

[0242] Referring again to Figure 35, there are also a steam flow line 3554 from head 3504 to compressor 3538, a steam outlet 3542 for diverting steam to the evaporator / condenser, a high-temperature product line 3534 that also allows for the collection of high-temperature purified condensate products 3528 from the evaporator / condenser through exchanger 3518, and a line (not shown) for diverting the high-temperature product to compressor 3538 to maintain a constant water level. There may also be a drain line (not shown) for when the system is shut down.

[0243] Referring here to Figure 36-36C, an alternative embodiment may also include a fluid distribution manifold 3600. Figure 36 shows one pump-side view of one particular embodiment of the fluid distribution manifold 3600. An input in the form of raw material feed flows through port 3602, and an output flow (output) flows through port 3604. An additional output in the form of production logistics flows through port 3606, while port / chamber 3608 provides a vent for volatile matter (output), and port 3610 provides a drain (output) for a liquid-sealed pump. Figure 36A shows the other pump-side view of the same particular embodiment of the fluid distribution manifold 3600. Port / chamber 3608 for volatile matter output is clearly visible, as is the drain 3610 for the liquid-sealed pump. In this figure of this particular embodiment, a condenser vapor mist remover chamber 3612 can be seen, as well as a mist collector and drain area 3614.

[0244] Specifically referring to Figure 36B, this figure illustrates one side of the evaporator / condenser side of the fluid distribution manifold 3600 in the same particular embodiment. The raw material supply port 3602, as well as the discharge port 3604 and the product port 3606, are readily visible in this figure. In addition, the evaporator vapor port 3616 and the condenser vapor port 3618 can be seen.

[0245] Specifically referring to Figure 36B, this figure illustrates the other side of the evaporator / condenser side of the fluid distribution manifold 3600 in the same particular embodiment. Again, the discharge through port 3604 can be seen, as well as the liquid-sealed pump drain port 3606, the second condenser vapor mist remover 3612, the evaporator vapor mist remover 3620, and the mist collector and drain area 3614. The reservoir level control chamber can also be seen in this figure, along with the product level control chamber 3622 and the liquid-sealed pump supply unit 3624.

[0246] Referring again to Figure 36-36C, the fluid distribution manifold 3600 can eliminate most of the piping systems in a fluid purification system, advantageously incorporating various functions, including flow regulation, mist removal, and pressure regulation, into a single unit, thereby simplifying manufacturing and reducing the overall number of components. The core plate and manifold may be made of, for example, plastic, metal, or ceramic plates, or any other non-corrosive material capable of withstanding high temperatures and pressures. The method of manufacturing the core plate and manifold includes brazing and outer coating.

[0247] Referring here to Figures 37-37A, these figures illustrate a fitting assembly in a particular embodiment that allows fluid to be in contact throughout the system. For example, there may be floating fluid between the exchanger 3518 (shown in Figure 35) and the intake / exhaust ports 3220 and 3208 (shown in Figure 32). Figure 37A illustrates a connector 3702 which may be welded to a heat exchanger port (not shown), the connector 3702 connecting to a fluid interface 3704, the fluid interface then communicating with a fluid distribution manifold. Figure 37A shows a cross-sectional view across line AA (see Figure 37). The connector 3702 has the ability to float to compensate for alignment transitions that may be caused by temperature or manufacturing variations. Sealing is completed by an O-ring 3706. As can be seen from the diagram in Figure 37, when the O-ring seal 3706 rotates 90 degrees around the central axis along line AA, the connector 3702 and the fluid interface 3704 are locked together, forming a fluid interface connection.

[0248] Referring here to Figures 38-38A, these figures illustrate another embodiment of the evaporator / condenser 3800. As seen in Figure 38, the evaporator / condenser 3800 is a flat evaporator / condenser containing several parallel core layers 3802 and 3804, typically made of a copper-nickel alloy or other heat-conducting material, with rib sections 3806 creating channels 3810 and 3812 for directing the steam and condensed fluid flow. The steam intake 3814 and product outlet 3816 manifolds (as well as, contaminant intake and volatile outlet manifolds, not shown) may be connected to a liquid-sealed pump / compressor via a fluid interface. Bolt 3818 secures the core evaporator / condenser 3800 to the bracket of the external housing of the liquid-sealed pump / compressor. During operation, all alternating horizontal rows 3802 and 3804 (as shown in Figures 38 and 38A) are equipped with evaporator channels 3810 and condenser channels 3812, such that the two functions never overlap on any given layer. Figure 38A, a detail of Figure 38, more clearly shows how the combined evaporator / condenser manifold operates. As shown, column 3802 does not interact with column 3804 and is closed to each other, thereby separating the functions of evaporation and condensation in the horizontal core layer.

[0249] Referring now to Figure 39, this figure illustrates an alternative embodiment of a heat exchanger used in a steam distillation apparatus, such a heat exchanger making full use of available system and heat sources. In one particular embodiment, heat from at least one of multiple sources passes through a multi-line heat exchanger 3902, such as the one shown in Figure 39, and a series of two-channel heat exchangers such as 3904, 3906, 3908, and 3910 are piped to produce a multi-line effect. Note that in the particular embodiment of the multi-line heat exchanger shown in Figure 39, the low-temperature intake flow 3912 passes through all the heat exchanger units 3904, 3906, 3908, and 3910, one heat source, e.g., high-temperature product 3914, flows through heat exchanger units 3904 and 3908, and another heat source, e.g., high-temperature discharge flow 3916, flows through heat exchanger units 3906 and 3910. Thus, multiple heat sources may be used to replace the low-temperature intake flow 3912.

[0250] Referring now to Figure 39A, this figure illustrates an alternative embodiment of the heat exchanger. In this embodiment, the heat exchanger may be a single multi-channel heat exchanger 3918. In this particular embodiment, heat sources such as a low-temperature intake 3912 and a high-temperature product 3914, and a high-temperature discharge flow 3916, flow through the exchanger 3918 simultaneously but in opposite directions, thereby enabling heat exchange between the low-temperature intake 3912 and both heat sources 3914 and 3916 within a single heat exchanger 3912.

[0251] Referring here to Figure 40, one alternative embodiment may include the step of measuring evaporator and condenser pressures to evaluate overall system performance and / or to provide data to a control system. To avoid the use of expensive sensors required to withstand the high temperatures of the evaporator / condenser 4002, pressure sensors PE and Pc are mounted on the fluid line between the low-temperature side of the heat exchanger 4004 and the corresponding control valves VE and VC. To avoid measuring a pressure below the actual system pressure, which occurs when fluid is flowing to the pressure sensors located at this position, the control valves are momentarily closed to stop the flow. During the “no-flow” period, the pressure remains constant as it returns from the control valves to the evaporator or condenser, allowing for accurate measurement of the system pressure. These short “no-flow” periods do not result in any adverse effects on the distiller's performance.

[0252] Referring here to Figure 41-41B, this figure illustrates another embodiment of the present disclosure, which includes a filtration mechanism in the intake for increasing the purity of the final production fluid. A multi-unit flip filter 4100, having a pivot joint 4102 joining at least two filter units 4104 and 4106, is housed in a filter housing 4108 that directs the fluid through the filter units 4104 and 4106 and facilitates the rotation of the filter units 4104 and 4106 around the central pivot joint 4102. As shown, the discharge flow 4109 passes through the flip filter unit 4104, while the intake fluid flow 4110 simultaneously flows from the intake through the flip filter unit 4106 during purification. After a certain interval, a flip filter switch (not shown) rotates the flip filter 4100 in the flip filter pivot joint 4102 around a central axis indicated by a dotted line, so that the filter unit 4106, which is contaminated with contaminants filtered from the contaminated intake fluid, is backwashed by the discharge flow 4109, and the filter unit 4104 becomes a filter unit that filters the intake fluid flow 4110. In such embodiments, O-ring gaskets 4112 and 4114 may be used as seals between the filter units 4104 and 4106 and the fluid passages of the discharge flow 4109 and the intake fluid flow 4110, respectively.

[0253] Referring here to Figure 41C-D, the multi-unit flip filter may also be a multi-section annular filter 4112. The multi-unit flip filter 4112, which has a pivot point 4114 around which multiple flip filter units such as 4116 and 4118 pivot, may also be housed in a filter housing 4120 that directs the fluid flow through the individual filter units 4116 and 4118 and facilitates the rotation of the filter 4112 around the pivot point 4114. As shown, the discharge flow 4109 passes through one flip filter unit 4116, while the intake fluid flow 4110 simultaneously flows from the intake through the flip filter unit 4118 during purification. As shown in Figure 41, a flip filter switch (not shown) rotates the flip filter 4112 around a central axis indicated by a dotted line at the flip filter pivot point 4114. As a result, filter unit 4118, which is contaminated with contaminants filtered from the contaminated intake fluid, is backwashed by the discharge flow 4109, and filter unit 4116 becomes a filter unit that filters the intake fluid flow 4110. A series of seals, as indicated by 4122 and 4124, are used between the individual filter units 4116 and 4118 to separate the discharge flow 4109 flowing through one filter section from the intake fluid flow 4110 flowing through the other filter section.

[0254] Referring here to Figures 41E-41F, other embodiments may include a manual valve 4122 to change the reporting of the water flow. Such a valve would, for example, allow the use of a discharge flow 4109 to continuously clean one unit of each flip filter, effectively switching in a single operation which unit is being filtered and which unit is being backwashed, thereby backwashing filter unit 4104 or 4106 without actually having to replace the filter 4100 itself. In one particular embodiment, when the valve 4122 is in position A, filter unit 4104 is filtering the intake fluid 4110 and filter unit 4106 is backwashing with discharge flow 4109. When the valve 4100 is switched to position B, filter unit 4104 is backwashed with discharge flow 4108 and filter unit 4106 is filtering the input fluid 4110. (Stirling cycle engine) In some embodiments, the various embodiments of the steam distillation apparatus described above may be powered by a Stirling cycle machine (which may also be called a Stirling engine). In exemplary embodiments, the Stirling cycle machine is a Stirling engine described in the pending U.S. Patent Application No. 12 / 105,854, filed April 18, 2008, attorney reference number 170, which is incorporated herein by whole reference. However, in other embodiments, the Stirling cycle machine may be any of the Stirling cycle machines described in U.S. Patents 6,381,958, 6,247,310, 6,536,207, 6,705,081, 7,111,460, and 6,694,731, all of which are incorporated herein by reference in their entirety.

[0255] Stirling cycle machines, including engines and refrigerators, have a long technical tradition, as described in detail in Walker, Stirling Engines, Oxford University Press (1980), which is incorporated herein by reference. The fundamental principle of a Stirling cycle engine is the mechanical realization of the Stirling thermodynamic cycle, which involves isochoric heating of a gas in a cylinder, isothermal expansion of the gas (during which the action is carried out by driving a piston), isochoric cooling, and isothermal compression. Additional background information regarding the Stirling cycle engine and its improvements is discussed in Hargreaves, *The Phillips Stirling Engine* (Elsevier, Amsterdam, 1991), which is incorporated herein by reference.

[0256] The operating principle of a Stirling cycle machine is readily explained with respect to Figures 45A–45E, where identical digits are used to identify the same or similar parts. Many mechanical layouts of Stirling cycle machines are known in the art, and specific Stirling cycle machines, generally designated by the digit 5110, are shown for illustrative purposes only. In Figures 45A–45D, the piston 5112 and the displacement 5114 move in a stepwise reciprocating motion within a cylinder 5116, which may be a single cylinder in some embodiments of the Stirling cycle machine, but may be more than one cylinder in other embodiments. The working fluid contained within the cylinder 5116 is constrained by seals to leak out around the piston 5112 and the displacement 5114. The working fluid is selected for its thermodynamic properties, as will be discussed in the following description, and is typically helium at several atmospheres of pressure, but any gas, including any inert gas, may be used, including but not limited to hydrogen, argon, neon, nitrogen, air, and any mixture thereof. The position of the displacementr 5114 controls whether the working fluid is in contact with the high-temperature interface 5118 or the low-temperature interface 5120, which correspond to the interface where heat is supplied to the working fluid and the interface where heat is extracted from the working fluid, respectively. The supply and extraction of heat will be discussed in more detail below. The volume of the working fluid controlled by the position of the piston 5112 is called the compression space 5122.

[0257] During the first phase of the Stirling cycle, as shown in Figure 45A, the piston 5112 compresses the fluid in the compression space 5122. Compression occurs at a substantially constant temperature as heat is extracted from the fluid into the surrounding environment. The state of the Stirling cycle machine 5110 after compression is shown in Figure 45B. During the second phase of the cycle, the displacementr 5114 moves toward the low-temperature interface 5120, displacing the working fluid from the region of the low-temperature interface 5120 to the region of the high-temperature interface 5118. This stage may also be called the transfer phase. At the end of the transfer phase, the working fluid is heated by a constant volume, so the fluid becomes more pressure. The increased pressure is symbolically shown in Figure 45C by the measurement of the pressure gauge 5124.

[0258] During the third phase (expansion phase) of the Stirling cycle machine, the volume of the compression space 5122 increases as heat is received from outside the Stirling cycle machine 5110, thereby converting heat into work. In practice, heat is supplied to the fluid using a heater head (not shown), which will be discussed in more detail in the following description. At the end of the expansion phase, the compression space 5122 is filled with the cold fluid, as shown in Figure 45D. During the fourth phase of the Stirling cycle machine 5110, the fluid is transferred from the region of the hot interface 5118 to the region of the cold interface 5120 by the motion of the displacer 5114 in the opposite direction. At the end of this second transfer phase, the fluid fills the compression space 5122 and the cold interface 5120, as shown in Figure 45A, and is ready for the iteration of the compression phase. The Stirling cycle is represented by a PV (pressure-volume) diagram, as shown in Figure 45E.

[0259] Furthermore, in some embodiments, when the fluid passes from the high-temperature interface 5118 region to the low-temperature interface 5120 region, it may pass through a regenerator (shown as 5408 in Figure 48). The regenerator is a matrix-like material with a large surface area-to-volume ratio that absorbs heat from the fluid when it enters from the high-temperature interface 5118 region and heats the fluid when it passes through from the low-temperature interface 5120 region.

[0260] Stirling cycle machines are generally not used in practical applications due to several difficult challenges in their development. These involve practical considerations such as efficiency and lifespan. Therefore, there is a greater need for Stirling cycle machines with minimal lateral load on the piston, increased efficiency, and lifespan. (Rocking beam drive) Referring here to Figures 46-48, an embodiment of a Stirling cycle machine according to one embodiment is shown in cross-section. The engine embodiment is generally designated by the number 5300. While the Stirling cycle machine is generally described in relation to the embodiment of the Stirling engine 5300 shown in Figures 46-48, it should be understood that many types of machines and engines, including but not limited to refrigerators and compressors, may also benefit from the various embodiments and improvements described herein, including but not limited to external combustion engines and internal combustion engines.

[0261] Figure 46 shows a cross-section of an embodiment of a rocking beam drive mechanism 5200 for an engine such as a Stirling engine (the term "rocking beam drive unit" is used synonymously with "rocking beam drive mechanism"), which has linearly reciprocating pistons 5202 and 5204 housed in cylinders 5206 and 5208, respectively. The cylinders include linear bearings 5220. The rocking beam drive unit 5200 converts the linear motion of pistons 5202 and 5204 into rotational motion of a rank shaft 5214. The rocking beam drive unit 5200 comprises a rocking beam 5216, a rocker pivot 5218, a first coupling assembly 5210, and a second coupling assembly 5212. Pistons 5202 and 5204 are coupled to the rocking beam drive unit 5200 via the first coupling assembly 5210 and the second coupling assembly 5212, respectively. The rocking beam drive unit is connected to the crankshaft 5214 via a connecting rod 5222.

[0262] In some embodiments, the locking beam and the first part of the coupling assembly may be located inside the crankcase, while the cylinder, piston, and the second part of the coupling assembly are located in the working space.

[0263] In the crankcase 5400 of Figure 48, the majority of the locking beam drive unit 5200 is located below the cylinder housing 5402. The crankcase 5400 is the space that enables the operation of the locking beam drive unit 5200, which has a crankshaft 5214, a locking beam 5216, a linear bearing 5220, a connecting rod 5222, and coupling assemblies 5210 and 5212. The crankcase 5400 intersects the cylinders 5206 and 5208 perpendicular to the plane of the axes of the pistons 5202 and 5204. The pistons 5202 and 5204 reciprocate within their respective cylinders 5206 and 5208, as also shown in Figure 46. The cylinders 5206 and 5208 extend above the crankshaft housing 5400. The crankshaft 5214 is mounted within the crankcase 5400 below the cylinders 5206 and 5208.

[0264] Figure 46 shows one embodiment of the rocking beam drive unit 5200. Connecting assemblies 5210 and 5212 extend from pistons 5202 and 5204, respectively, connecting pistons 5202 and 5204 to the rocking beam 5216. In some embodiments, the connecting assembly 5212 for piston 5204 may include a piston rod 5224 and a link rod 5226. In some embodiments, the connecting assembly 5210 for piston 5202 may include a piston rod 5228 and a link rod 5230. Piston 5204 operates vertically within cylinder 5208 and is connected by connecting assembly 5212 to end pivot 5232 of the rocking beam 5216. Cylinder 5208 provides guidance for the longitudinal motion of piston 5204. The piston rod 5224 of the coupling assembly 5212, attached to the lower portion of the piston 5204, is longitudinally driven by its link rod 5226 in a substantially linear reciprocating motion path along the axis of the cylinder 5208. The distal end of the piston rod 5224 and the proximal end of the link rod 5226 are jointly hinged together via a coupling means 5234 in some embodiments. The coupling means 5234 may be any coupling means known in the art, including but not limited to flexible joints, roller bearing elements, hinges, journal bearing joints (shown as 5600 in Figure 50), and bends (shown as 5700 in Figures 51A and 51B). The distal end of the link rod 5226 may be coupled to one end pivot 5232 of the rocking beam 5216, which is positioned vertically and upright below the proximal end of the link rod 5226. A stationary linear bearing 5220 may be positioned along the connecting assembly 5212 to further ensure substantially linear longitudinal motion of the piston rod 5224, and thus substantially linear longitudinal motion of the piston 5204. In the exemplary embodiment, the link rod 5226 does not pass through the linear bearing 5220. This ensures, among other things, that the piston rod 5224 maintains substantially linear longitudinal motion.

[0265] In exemplary embodiments, the link rods may be made of aluminum, and the piston rods and connecting rods may be made of D2 tool steel. Alternatively, the link rods, piston rods, connecting rods, and rocking beam may be made of 4340 steel. Other materials, including but not limited to titanium, aluminum, steel, or cast iron, may be used for the components of the rocking beam drive unit. In some embodiments, the fatigue strength of the materials used is greater than the actual loads experienced by the components during operation.

[0266] Referring again to Figures 46-48, the piston 5202 operates vertically within the cylinder 5206 and is connected by a coupling assembly 5210 to an end pivot 5236 of the rocking beam 5216. The cylinder 5206, among other things, serves to provide guidance for the longitudinal motion of the piston 5202. The piston rod 5228 of the coupling assembly 5210 is attached to the lower portion of the piston 5202 and is driven axially by its link rod 5230 in a substantially linear reciprocating motion path along the axis of the cylinder 5206. The distal end of the piston rod 5228 and the proximal end of the link rod 5230 are, in some embodiments, jointly hinged together via coupling means 5238. The coupling means 5238 may, in various embodiments, include, but are not limited to, a bend (shown as 5700 in Figures 51A and 51B), a roller bearing element, a hinge, a journal bearing coupling (shown as 5600 in Figure 50), or coupling means known in the art. In some embodiments, the distal end of the link rod 5230 may be connected to one end pivot 5236 of the rocking beam 5216, which is positioned vertically and upright below the proximal end of the link rod 5230. A stationary linear bearing 5220 may be positioned along the linking assembly 5210 to further ensure substantially linear longitudinal motion of the piston rod 5228 and thus ensure linear longitudinal motion of the piston 5202. In exemplary embodiments, the link rod 5230 does not pass through the linear bearing 5220 to ensure that the piston rod 5228 maintains substantially linear longitudinal motion.

[0267] The connecting assemblies 5210 and 5212 convert the alternating longitudinal motion of the respective pistons 5202 and 5204 into the oscillating motion of the rocking beam 5216. The delivered oscillating motion is converted into the rotational motion of the crankshaft 5214 by the connecting rod 5222, with one end of the connecting rod 5222 rotatably connected to a connecting pivot 5240 located in the rocking beam 5216 between the end pivot 5232 and the rocker pivot 5218, and the other end of the connecting rod 5222 rotatably connected to the crankpin 5246. The rocker pivot 5218 may be substantially located midway between the end pivots 5232 and 5236, oscillatingly supporting the rocking beam 5216 as a fulcrum, and thus guiding the respective piston rods 5224 and 5228 to perform sufficient linear motion. In the exemplary embodiment, the crankshaft 5214 is located above the rocking beam 5216, but in other embodiments, the crankshaft 5214 may be located below the rocking beam 5216 (as shown in Figures 49B and 49D), or in some embodiments, the crankshaft 5214 is located alongside the rocking beam 5216 so as to still have an axis parallel to the rocking beam 5216.

[0268] Referring again to Figures 46-48, the rocking beam oscillates around the rocker pivot 5218, and the end pivots 5232 and 5236 follow an arc-shaped path. Since the distal ends of the link rods 5226 and 5230 are connected to the rocking beam 5216 at pivots 5232 and 5236, the distal ends of the link rods 5226 and 5230 also follow this arc-shaped path, resulting in angular deviations 5242 and 5244 from the longitudinal axis of the motion of the respective pistons 5202 and 5204. The connecting means 5234 and 5238 are configured such that any angular deviations 5242 and 5244 experienced by the piston rods 5224 and 5228 from the link rods 5226 and 5230 are minimized. Essentially, angular deviations 5244 and 5242 are absorbed by coupling means 5234 and 5238 so as to reduce lateral loads on pistons 5204 and 5202, while piston rods 5224 and 5228 maintain substantially linear longitudinal motion. To further absorb any angular deviations 5244 or 5242 and thus keep the piston push rod 5224 or 5228 and piston 5204 or 5202 in linear motion along the longitudinal axis of piston 5204 or 5202, a stationary linear bearing 5220 may also be positioned inside cylinder 5208 or 5206 or along coupling assembly 5212 or 5210.

[0269] Therefore, considering the reciprocating motion of pistons 5202 and 5204, deviations 5242 and 5244 of the reciprocating motion of pistons 5202 and 5204 from the longitudinal axis cause noise, reduced efficiency, increased friction against the cylinder walls, increased lateral loads, and lower durability of the parts, so it is necessary to keep the motion of pistons 5202 and 5204 as close to linear as possible. Thus, the alignment of cylinders 5206 and 5208, as well as the arrangement of the crankshaft 5214, piston rods 5224 and 5228, link rods 5226 and 5230, and connecting rod 5222, can affect, among other things, the efficiency and / or volume of the device. To increase the linearity of the piston motion as described above, the pistons (shown as 5202 and 5204 in Figures 46-48) are preferably as close as possible to the sides of their respective cylinders 5206 and 5208.

[0270] In another embodiment for reducing the angular deviation of the link rods, the link rods 5226 and 5230 reciprocate substantially linearly along the longitudinal axes of their respective pistons 5204 and 5202 to reduce the angular deviation and thus reduce the lateral load applied to each piston 5204 and 5202. The angular deviation defines the deviation of the link rod 5226 or 5230 from the longitudinal axis of the piston 5204 or 5202. The digits 5244 and 5242 refer to the angular deviations of the link rods 5226 and 5230 as shown in Figure 46. Thus, the position of the link assembly 5212 affects the angular displacement of the link rod 5226, based on the length of the distance between the end pivot 5232 and the rocker pivot 5218 of the rocking beam 5216. Thus, the position of the link assembly may be such that the angular displacement of the link rod 5226 is reduced. For link rod 5230, the length of the connecting assembly 5210 may also be determined and positioned to reduce the angular displacement of link rod 5230, based on the length of the distance between the end pivot 5236 and the rocker pivot 5218 of the rocking beam 5216. Thus, the lengths of link rods 5226 and 5230, the lengths of the connecting assemblies 5212 and 5210, and the length of the rocking beam 5216 are important parameters that greatly influence and / or determine the angular deviation of link rods 5226 and 5230 as shown in Figure 46.

[0271] An exemplary embodiment has a linear rocking beam 5216 having endpoints 5232 and 5236, a rocker pivot 5218, and a connecting pivot 5240 along the same axis. However, in other embodiments, the rocking beam 5216 may be curved so that the pistons are positioned at an angle to each other, as shown in Figures 49C and 49D.

[0272] Referring here to Figures 46-48 and 51A-51B, in some embodiments of the linking assembly, the linking assemblies 5212 and 5210 may include flexible link rods that are axially rigid but flexible in the plane of the rocking beam 5216 for motion between the link rods 5226 and 5230 and the pistons 5204 and 5202, respectively. In this embodiment, a bent portion (shown as 5700 in Figures 51A and 51B), which is at least a portion of the link rods 5226 and 5230, is elastic. The bent portion 5700 serves as a linking means between the piston rod and the link rod. The bent portion 5700 may more effectively absorb the crank-induced lateral load of the piston and thus allow each piston to maintain linear axial motion inside the piston cylinder. This bent portion 5700 allows for small rotations in the plane of the rocking beam 5216 between the link rods 5226 and 5230 and the pistons 5204 or 5202, respectively. In this embodiment, the bend 5700 is shown to be flat to increase the elasticity of the link rods 5226 and 5230, but in some embodiments, the bend 5700 is not flat. The bend 5700 may also be constructed near the lower portion of the piston or near the distal ends of the link rods 5226 and 5230. In one embodiment, the bend 5700 may be made of #D2 tool steel strengthened to 58-62RC. In some embodiments, two or more bends (not shown) may be present on the link rods 5226 or 5230 to increase the elasticity of the link rods.

[0273] In alternative embodiments, the piston axes in each cylinder housing may extend in different directions, as shown in Figures 49C and 49D. In exemplary embodiments, the piston axes in each cylinder housing are substantially parallel, and preferably substantially perpendicular, as shown in Figures 46-48 and 55A and 55B. Figures 49A-49D include various embodiments of the rocking beam drive mechanism, including similar numbers as shown and described with respect to Figures 2-4. It will be understood by those skilled in the art that changing the relative position of the connecting pivot 5240 along the rocking beam 5216 changes the stroke of the piston.

[0274] Therefore, changes in the relative position of the connecting pivot 5240 in the rocking beam 5216, as well as the parameters of piston rods 5224 and 5228, link rods 5230 and 5226, the length of the rocking beam 5216, and the length of the rocker pivot 5218, cause various changes in the angular deviation of link rods 5226 and 5230, the phase of pistons 5204 and 5202, and the size of device 5300. Thus, in various embodiments, a wide range of piston phase angles and variable engine size may be selected based on modifications to one or more of these parameters. In practice, in the exemplary embodiment, link rods 5224 and 5228 have substantially lateral motion within -0.5 to +0.5 degrees from the longitudinal axis of pistons 5204 and 5202. In various other embodiments, depending on the length of the link rods, the angle may vary between about 0 and 0.75 degrees. However, in other embodiments, the angle may be higher, including between about 0 and about 20 degrees. However, as the length of the linkage rod increases, the crankcase / overall engine height, as well as the engine's weight, also increases.

[0275] One feature of the exemplary embodiment is that each piston has a link rod that substantially extends to an accompanying piston rod so as to form a connecting assembly. In one embodiment, the connecting assembly 5212 for piston 5204 includes a piston rod 5224, a link rod 5226, and a connecting means 5234, as shown in Figure 46. More specifically, one proximal end of piston rod 5224 is attached to the lower portion of piston 5204, and the distal end of piston rod 5224 is connected to the proximal end of link rod 5226 by the connecting means 5234. The distal end of link rod 5226 extends perpendicularly to the end pivot 5232 of the locking beam 5216. As described above, the connecting means 5234 may be, but is not limited to, a joint, hinge, coupling, or bend, or other means known in the art. In this embodiment, the ratio of the piston rod 5224 to the link rod 5226 may determine the angular deviation of the link rod 5226 as described above.

[0276] In one embodiment of the machine, an engine such as a Stirling engine employs two or more rocking beam drive units on the crankshaft. Referring here to Figure 52, an uncovered "four-cylinder" rocking beam drive mechanism 5800 is shown. In this embodiment, the rocking beam drive mechanism has four pistons 5802, 5804, 5806, and 5808 connected to two rocking beam drive units 5810 and 5812. In an exemplary embodiment, the rocking beam drive mechanism 5800 is used in a Stirling engine having at least four pistons 5802, 5804, 5806, and 5808 arranged in a quadrilateral arrangement connected to a pair of rocking beam drive units 5810 and 5812, with each rocking beam drive unit connected to the crankshaft 5814. However, in other embodiments, the Stirling cycle engine includes between one and four pistons, and in yet another embodiment, the Stirling cycle engine includes five or more pistons. In some embodiments, the rocking beam drive units 5810 and 5812 are substantially similar to the rocking beam drive units described above with respect to Figures 46-48 (shown as 5210 and 5212 in Figures 46-48). In this embodiment, the piston is shown outside the cylinder, but in practice, the piston is inside the cylinder.

[0277] Referring again to Figure 52, in some embodiments, the rocking beam drive mechanism 5800 has a single crankshaft 5814 having a pair of longitudinally spaced, radially and opposingly oriented crankpins 5816 and 5818 adapted for journaling within a housing, and a pair of rocking beam drive units 5810 and 5812. Each rocking beam 5820 and 5822 is pivotably connected to rocker pivots 5824 and 5826 and to crankpins 5816 and 5818, respectively. In an exemplary embodiment, the rocking beams 5820 and 5822 are connected to a rocking beam shaft 5828.

[0278] In some embodiments, the motor / generator may be connected to the crankshaft in an acting relationship. In one embodiment, the motor may be located between the rocking beam drive units. In another embodiment, the motor may be located externally. The term "motor / generator" is used to mean either the motor or the generator, or either one.

[0279] Figure 53 shows one embodiment of the crankshaft 5814. A motor / generator 5900, such as a permanent magnet ("PM") generator, is positioned on the crankshaft. The motor / generator 5900 may be positioned between or inside the rocking beam drive units (not shown, shown as 5810 and 5812 in Figure 53), or it may be positioned outside or outside the rocking beam drive units 5810 and 5812 at the end of the crankshaft 5814, as indicated by the number 51000 in Figure 54A.

[0280] When the motor / generator 5900 is positioned between the rocking beam drive units (not shown, indicated as 5810 and 5812 in Figure 52), the length of the motor / generator 5900 is limited by the distance between the rocking beam drive units. The square of the diameter of the motor / generator 5900 is limited by the distance between the crankshaft 5814 and the rocking beam shaft 5828. Since the capacity of the motor / generator 5900 is proportional to the square of its diameter and length, these dimensional limitations result in a "pancake" motor / generator 5900 with a limited capacity, having a relatively short length and a relatively large square of diameter. While the use of a "pancake" motor / generator 5900 may reduce the overall dimensions of the engine, the dimensional limitations imposed by the internal configuration result in a motor / generator with a limited capacity.

[0281] By positioning the motor / generator 5900 between the rocking beam drive units, the motor / generator 5900 is exposed to the heat generated by the mechanical friction of the rocking beam drive units. Due to the internal position of the motor / generator 5900, cooling the motor / generator 5900 becomes even more difficult, thereby increasing the effect of the heat produced by the motor / generator 5900, as well as the heat absorbed by the motor / generator 5900 from the rocking beam drive units. This can lead to overheating of the motor / generator 5900, and ultimately to failure.

[0282] Referring to both Figures 52 and 53, the internal arrangement of the motor / generator 5900 also leads to an asymmetrical configuration of pistons 5802, 5804, 5806, and 5808, as pistons 5802, 5804, 5806, and 5808 are connected to the rocking beam drive units 5810 and 5812, respectively. The increase in distance also results in an increase in the distance between pistons 5802 and 5804 and pistons 5806 and 5808. Asymmetrical piston arrangements can lead to inefficient thermodynamic operation of the combustor and heater head, which in turn can result in a decrease in overall engine efficiency. Additionally, asymmetrical piston arrangements can lead to larger heater head and combustion chamber dimensions.

[0283] An exemplary embodiment of the motor / generator configuration is shown in Figure 54A. As shown in Figure 54A, the motor / generator 51000 is located externally from the rocking beam drive units 51010 and 51012 (shown as 5810 and 5812 in Figure 52) and at the end of the crankshaft 51006. The external position allows for a motor / generator 51000 having a larger length and diameter square than the "pancake" motor / generator described above (shown as 5900 in Figure 53). As previously mentioned, the capacity of the motor / generator 51000 is proportional to the square of its length and diameter, and since the external motor / generator 51000 may have a larger length and diameter square, the configuration of the external motor / generator 51000 shown in Figure 54A, in conjunction with the engine, may allow for the use of a motor / generator with a higher capacity.

[0284] As shown in the embodiment of Figure 54A, by positioning the motor / generator 51000 outside the drive units 51010 and 51012, the motor / generator 51000 is not exposed to the heat generated by the mechanical friction between the drive units 51010 and 51012. Furthermore, the external position of the motor / generator 1000 makes it easier to cool the motor / generator, thereby enabling more mechanical engine cycles for a given amount of time, which in turn enables higher overall engine performance.

[0285] Furthermore, because the motor / generator 51000 is located on the outside and not between the drive units 51010 and 51012, the rocking beam drive units 51010 and 51012 may be located closer together, thereby allowing the pistons connected to the drive units 51010 and 51012 to be arranged in an equilateral configuration. In some embodiments, depending on the type of combustor used, particularly in the case of a single combustor embodiment, the equilateral arrangement of the pistons allows for higher efficiency of the thermodynamic operation of the combustor and heater head, which in turn allows for higher overall engine performance. The equilateral arrangement of the pistons also advantageously allows for smaller heater head and combustion chamber dimensions.

[0286] Referring again to Figures 52 and 53, the crankshaft 5814 may have concentric ends 5902 and 5904, which in one embodiment are crank journals and, in various other embodiments, may be bearings, but are not limited to these. Each concentric end 5902, 5904 has crankpins 5816, 5818, respectively, which may be offset from the central axis of the crankshaft. To balance any instability that the crankshaft 581 may experience, at least one counterweight 5906 may be installed at either end of the crankshaft 5814 (shown as 51006 in Figure 54A). This crankshaft configuration, combined with the rocking beam drive unit described above, allows the pistons (shown as 5802, 5804, 5806, and 5808 in Figure 52) to work in conjunction with one revolution of the crankshaft 5814. This characteristic will be further described below. In other embodiments, a flywheel (not shown) may be positioned on the crankshaft 5814 (shown as 51006 in Figure 54A) to further reduce angular velocity fluctuations for a more constant speed.

[0287] Referring again to Figures 52 and 53, in some embodiments, a cooler (not shown) may also be positioned along the crankshaft 5814 (shown as 51006 in Figure 54A) and the rocking beam drive units 5810 and 5812 (shown as 51010 and 51012 in Figure 54A) to cool the crankshaft 5814 and the rocking beam drive units 5810 and 5812. In some embodiments, the cooler may be used to cool the working gas in the cryogenic chamber of the cylinder, and may also be configured to cool the rocking beam drive units. Various embodiments of the cooler will be discussed in detail below.

[0288] Figures 54A-54G show several embodiments of various components of the machine. As shown in this embodiment, the crankshaft 51006 is connected to the motor / generator 51000 via a motor / generator coupling assembly. Since the motor / generator 51000 is mounted on the crankcase 51008, pressurization of the crankcase by the input fluid may result in deformation of the crankcase, which in turn may lead to misalignment between the motor / generator 51000 and the crankshaft 51006, causing the crankshaft 51006 to deflect. Since the rocking beam drive units 51010 and 51012 are connected to the crankshaft 51006, the deflection of the crankshaft 51006 may lead to failure of the rocking beam drive units 51010 and 51012. Therefore, in one embodiment of the machine, a motor / generator coupling assembly is used to connect the motor / generator 51000 to the crankshaft 51006. The motor / generator coupling assembly accommodates differences in the alignment between the motor / generator 51000 and the crankshaft 51006, which may contribute to the failure of the rocking beam drive units 51010 and 51012 during operation.

[0289] Referring again to Figures 54A-54G, in one embodiment, the motor / generator coupling assembly is a spline assembly including a spline shaft 51004, a sleeve rotor 51002 of the motor / generator 51000, and a crankshaft 51006. The spline shaft 51004 connects one end of the crankshaft 51006 to the sleeve rotor 51002. The sleeve rotor 51002 is attached to the motor / generator 51000 by mechanical means such as press-fitting, welding, screwing, or equivalent. In one embodiment, the spline shaft 51004 includes multiple splines on both ends of the shaft. In other embodiments, the spline shaft 51004 includes an intermediate splineless portion 51014 having a diameter smaller than the outer or inner diameter of the splined portions 51016 and 51018. In yet another embodiment, one end portion of the spline shaft 51016 has a spline that extends over a longer distance along the shaft than the second end portion 51018, which similarly includes a spline thereon.

[0290] In some embodiments, the sleeve rotor 51002 includes an opening 51020 extending along the longitudinal axis of the sleeve rotor 51002. The opening 51020 is capable of receiving a spline shaft 51004. In some embodiments, the opening 51020 includes a plurality of inner splines 51022 capable of engaging with a spline on one end of the spline shaft 51004. The outer diameter 51028 of the inner splines 51022 may be larger than the outer diameter 51030 of the splines on the spline shaft 51004 so that the fitting between the inner splines 51022 and the splines on the spline shaft 51004 is loose (as shown in Figure 54E). The loose fit between the inner spline 51022 and the spline on the spline shaft 51004 contributes to maintaining the spline engagement between the spline shaft 51004 and the rotor sleeve 51002 during deflection of the spline shaft 51004, which may be caused by pressure from the crankcase. In other embodiments, a longer splined portion 51016 of the spline shaft 51004 may engage with the inner spline 51022 of the rotor 51002.

[0291] Referring again to Figures 54A-54G, in some embodiments, the crankshaft 51006 has an opening 51024 above its end, capable of receiving one end of the spline shaft 51004. The opening 51024 preferably includes a plurality of inner splines 51026 that engage with the splines on the spline shaft 51004. The outer diameter 51032 of the inner splines 51026 may be larger than the outer diameter 51034 of the splines on the spline shaft 51004 so that the fit between the inner splines 51026 and the splines on the spline shaft 51004 is loose (as shown in Figure 54F). As previously mentioned, the loose fit between the inner spline 51026 and the spline on the spline shaft 51004 contributes to maintaining the spline engagement between the spline shaft 51004 and the crankshaft 51006 during the deflection of the spline shaft 51004, which may be caused by the pressure of the crankcase. The loose fit between the inner splines 51026 and 51022 on the crankshaft 51006 and the sleeve rotor 51002 and the spline on the spline shaft 51004 may contribute to maintaining the deflection of the spline shaft 51004. This may allow for misalignment between the crankshaft 51006 and the sleeve rotor 51002. In some embodiments, a shorter splined portion 51018 of the spline shaft 51004 may engage with the opening 51024 of the crankshaft 51006, thus preventing these potential misalignments.

[0292] In some embodiments, the opening 51020 of the sleeve rotor 51002 includes a plurality of internal splines extending along the length of the opening 51020. This arrangement helps ensure that the spline shaft 51004 is properly inserted into the opening 51020 during assembly. This helps maintain proper alignment between the splines on the spline shaft 51004 and the internal splines on the sleeve rotor 51002.

[0293] Referring here to Figure 48, one embodiment of the engine is shown, where pistons 5202 and 5204 of engine 5300 operate between a high-temperature chamber 5404 and a low-temperature chamber 5406 of cylinders 5206 and 5208, respectively. Between the two chambers, there may be a regenerator 5408. The regenerator 5408 may have a variable density and a variable area, and in some embodiments, it is made of wire. The variable density and area of ​​the regenerator may be adjusted so that the working gas has a substantially uniform flow across the regenerator 5408. Various embodiments of the regenerator 5408 are discussed below and in detail in U.S. Patent No. 6,591,609 issued to Kamen et al. on 17 July 2003 and U.S. Patent No. 6,862,883 issued to Kamen et al. on 8 March 2005, which are incorporated herein by reference in their entirety. As the working gas passes through the high-temperature chamber 5404, the heater head 5410 may heat the gas to expand it and push pistons 5202 and 5204 toward the low-temperature chamber 5406, where the gas is compressed. As the gas is compressed in the low-temperature chamber 5406, pistons 5202 and 5204 may be pulled back toward the high-temperature chamber to undergo the Stirling cycle again. The heater head 5410 may be a pinhead, finhead, folded finhead, heater tube as shown in Figure 48, or any other known embodiment of a heater head, including but not limited to those described below. Various embodiments of the heater head 5410 are discussed in detail below and incorporated herein by reference in their entirety in U.S. Patent No. 6,381,958 issued to Kamen et al. on 7 May 2002, U.S. Patent No. 6,543,215 issued to Langenfeld et al. on 8 April 2003, U.S. Patent No. 6,966,182 issued to Kamen et al. on 22 November 2005, and U.S. Patent No. 7,308,787 issued to LaRocque et al. on 18 December 2007.

[0294] In some embodiments, the cooler 5412 may be positioned alongside the cylinders 5206 and 5208 to further cool the gas passing through the cryogenic chamber 5406. Various embodiments of the cooler 5412 are discussed in detail in the following sections and in U.S. Patent No. 7,325,399 issued to Strimling et al. on February 5, 2008, which is incorporated herein by reference in its entirety.

[0295] In some embodiments, at least one piston seal 5414 may be positioned on pistons 5202 and 5204 to seal the high-temperature section 5404 from the low-temperature section 5406. In addition, at least one piston guide ring 5416 may be positioned on pistons 5202 and 5204 to help guide the piston motion within each cylinder. Various embodiments of the piston seal 5414 and guide ring 5416 are described in detail below and in U.S. Patent Application No. 10 / 175,502, filed July 19, 2002, issued February 6, 2003 (now abandoned), which is incorporated herein by reference in its entirety.

[0296] In some embodiments, at least one piston rod seal 5418 may be positioned relative to piston rods 5224 and 5228 to prevent the working gas from leaking into the crankcase 5400 or, alternatively, into the airlock space 5420. The piston rod seal 5418 may be an elastomer seal or a spring-loaded seal. Various embodiments of the piston rod seal 5418 will be discussed in detail below.

[0297] In some embodiments, for example, in the rolling diaphragm and / or bellows embodiments described in more detail below, the airlock space may be eliminated. In such cases, the piston rod seals 5224 and 5228 seal the working space away from the crankcase.

[0298] In some embodiments, at least one rolling diaphragm / bellows 5422 may be positioned along the piston rods 5224 and 5228 to prevent airlock gas from leaking into the crankcase 5400. Various embodiments of the rolling diaphragm 5422 will be discussed in detail below.

[0299] Figure 48 shows a cross-section of engine 5300, which has only two pistons and one locking beam drive unit. However, it should be understood that the operating principle described herein may generally apply to a four-cylinder double-locking beam drive engine, such as the one shown by the number 5800 in Figure 58. (Piston action) Referring now to Figures 52 and 55, the movement of pistons 5802, 5804, 5806, and 5808 during one full rotation of the crankshaft 5814 is shown. After a quarter rotation of the crankshaft 5814, piston 5802 is at the top of the cylinder, also known as top dead center; piston 5806 is in the upper intermediate stroke; piston 5804 is at the bottom of the cylinder, also known as bottom dead center; and piston 5808 is in the lower intermediate stroke. After a half rotation of the crankshaft 5814, piston 5802 is in the lower intermediate stroke; piston 5806 is at top dead center; piston 5804 is in the upper intermediate stroke; and piston 5808 is at bottom dead center. As the crankshaft 5814 completes a 3 / 4 rotation, piston 5802 is at bottom dead center, piston 5806 is in the downward intermediate stroke, piston 5804 is at top dead center, and piston 5808 is in the upward intermediate stroke. Finally, as the crankshaft 5814 completes a full rotation, piston 5802 is in the upward stroke, piston 5806 is at bottom dead center, piston 5804 is in the downward intermediate stroke, and piston 5808 is at top dead center. During each 1 / 4 rotation, there is a 90-degree phase difference between pistons 5802 and 5806, a 180-degree phase difference between pistons 5802 and 5804, and a 270-degree phase difference between pistons 5802 and 5808. Figure 56A illustrates the relationship between the pistons, which are approximately 90 degrees out of phase with the preceding and succeeding pistons. In addition, Figure 55 shows the means of a machine in an exemplary embodiment of the transmission action. Therefore, the action is transmitted from piston 5802 to piston 5806, piston 5804, and piston 5808, so that all pistons exert their action by moving from the top to the bottom of their respective cylinders as the crankshaft 5814 rotates completely.

[0300] Referring here to Figure 55 along with Figures 56A-56C, a 90-degree phase difference between pistons in an exemplary embodiment is illustrated. Referring here to Figure 56A, the cylinders are shown in a linear path, but this is for illustrative purposes only. In an exemplary embodiment of a four-cylinder Stirling cycle machine, the flow path of the working gas contained within the cylinder working space follows a figure-eight pattern. Thus, the working spaces of cylinders 51200, 51202, 51204, and 51206 are connected in a figure-eight pattern, for example, from cylinder 51200 to cylinder 51202, to cylinder 51204, and to cylinder 51208, so that the fluid flow pattern follows a figure-eight pattern. Referring again to Figure 56A, an uncovered view of cylinders 51200, 51202, 51204, and 51206 obtained along line BB (shown in Figure 56C) is illustrated. The 90-degree phase difference between the pistons as described above allows the working gas in the warm section 51212 of cylinder 51204 to be delivered to the cold section 51222 of cylinder 51206. When pistons 5802 and 5808 are out of phase by 90 degrees, the working gas in the warm section 51214 of cylinder 51206 is delivered to the cold section 51216 of cylinder 51200. When pistons 5802 and 5806 are also out of phase by 90 degrees, the working gas in the warm section 51208 of cylinder 51200 is delivered to the cold section 51218 of cylinder 51202. When pistons 5804 and 5806 are also out of phase by 90 degrees, the working gas in the warm section 51210 of cylinder 51202 is delivered to the cold section 51220 of cylinder 51204. Once the working gas in the warm section of the first cylinder enters the cold section of the second cylinder, the working gas begins to compress. Subsequently, the piston in the second cylinder, located in the lower section, pushes the compressed working gas back through the regenerator 51224 and the heater head 51226 (shown in Figure 56B), pushing it back into the warm section of the first cylinder. Once inside the warm section of the first cylinder, the gas expands, driving the piston in that cylinder and thus driving the working gas in the cold section of the first cylinder into the cylinder through the previous regenerator and heater head.As shown in Figure 56A, pistons 5802, 5804, 5806, and 5808 are connected to a common crankshaft 5814 (shown in Figure 55) via drive units 5810 and 5812 in such a manner that the circulating motion of each piston precedes the motion of the preceding piston by approximately 90 degrees, thus enabling the periodic movement characteristics of the working gas between these cylinders 51200, 51202, 51204, and 51206. (Rolling diaphragms, metal bellows, airlocks, and pressure regulators) In some embodiments of Stirling cycle machines, a lubricating fluid is used. Seals are used to prevent the lubricating fluid from leaking out of the crankcase.

[0301] Referring here to Figures 57A-59, some embodiments of a Stirling cycle machine include a fluid-lubricated locking beam drive unit and an engine entry area that may be damaged by the lubricating fluid, utilizing a rolling diaphragm 51300 positioned along the piston rod 51302 to prevent the lubricating fluid from leaking out of the crankcase (not shown, but components housed in the crankcase are represented as 51304). It is beneficial to contain the lubricating fluid because if the lubricating fluid enters the working space (not shown, but components housed in the working space are represented as 51306), it may contaminate the working fluid, come into contact with the regenerator 51308, and clog the regenerator 51308. The rolling diaphragm 51300 may be made of an elastomer material such as rubber, or rubber reinforced with woven or nonwoven fabric to provide rigidity. Alternatively, the rolling diaphragm 51300 may be made of other materials such as fluorosilicone or nitrile with woven or nonwoven fabric. The rolling diaphragm 51300 may also be made of a finely cut fabric, which is a nonwoven fabric containing carbon nanotubes or polyester or KEVLAR® fibers dispersed in, for example, an elastomer. In some embodiments, the rolling diaphragm 51300 is supported by an upper sealing piston 51328 and a bottom sealing piston 51310. In other embodiments, the rolling diaphragm 51300, as shown in Figure 57A, is supported through a notch in the upper sealing piston 51328.

[0302] In some embodiments, a pressure difference is placed across the rolling diaphragm 51300 such that the pressure above the seal 51300 is different from the pressure inside the crankcase 51304. This pressure difference expands the seal 51300, allowing the seal 51300 to act as a dynamic seal, ensuring that the rolling diaphragm maintains its shape throughout its operation. Figures 57A and 57C-57H illustrate how the pressure difference affects the rolling diaphragm. As the rolling diaphragm 51300 moves with the piston rod 51302, it conforms to the shape of the bottom-sealed piston 51310, preventing the seal 51300 from separating from the surface of the piston 51310 during operation. Such separation can cause seal failure. As the rolling diaphragm 51300 moves with the piston rod 51302, it maintains constant contact with the bottom-sealed piston 51310. This occurs because one side of the seal 51300 always has pressure applied to it, thereby causing the seal 51300 to expand to conform to the surface of the bottom sealing piston 51310. In some embodiments, the upper sealing piston 51328 "rolls above" the corner of the rolling diaphragm 51300 that is in contact with the bottom sealing piston 51310, in order to further maintain the seal 51300 in contact with the bottom sealing piston 51310. In exemplary embodiments, the pressure difference is in the range of 10 to 15 PSI. A smaller pressure in the pressure difference is preferably in the crankcase 51304 so that the rolling diaphragm 51300 may expand into the crankcase 51304. However, in other embodiments, the pressure difference may have a larger or smaller range of values.

[0303] The pressure difference may be generated by a variety of methods, including, but not limited to, the use of a pressurized lubrication system, a pneumatic pump, a sensor, an electric pump, a method by vibrating a rocking beam to generate a pressure rise in the crankcase 51304, a method by generating static electricity on the rolling diaphragm 51300, or other similar methods. In some embodiments, the pressure difference is generated by pressurizing the crankcase 51304 to a pressure that is below the average pressure of the working space 51306. In some embodiments, the crankcase 51304 is pressurized to a pressure in the range of 10 to 15 PSI below the average pressure of the working space 51306, but in various other embodiments, the pressure difference may be smaller or larger. Further details regarding the rolling diaphragm are included below.

[0304] However, referring here to Figures 57C, 57G, and 57H, another embodiment of the Stirling machine is shown, in which the airlock space 51312 is located between the working space 51306 and the crankcase 51304. The airlock space 51312 maintains a constant volume and pressure necessary to generate the pressure difference required for the function of the rolling diaphragm 51300 as described above. In one embodiment, the airlock 51312 is completely sealed from the working space 51306, so the pressure in the airlock 51312 is equal to the average pressure in the working space 51306. Thus, in some embodiments, the lack of an effective seal between the working space and the crankcase is one of the reasons for the need for an airlock space. Thus, in some embodiments, the airlock space may be eliminated by a more efficient and effective seal.

[0305] During operation, the average pressure in the working space 51306 may fluctuate, causing the average pressure in the airlock 51312 to fluctuate as well. One reason for pressure fluctuations is that during operation, the working space may become hotter, which in turn may increase the pressure in the working space, and consequently in the airlock, because the airlock and the working space are in fluid communication. In such cases, the pressure difference between the airlock 51312 and the crankcase 51304 also fluctuates, causing unnecessary stress in the rolling diaphragm 51300, which may lead to seal failure. Therefore, in some embodiments of the machine, the average pressure within the airlock 51312 is regulated to maintain a constant desired pressure difference between the airlock 51312 and the crankcase 51304, ensuring that the rolling diaphragm 51300 remains inflated and maintains its shape. In some embodiments, a pressure transducer is used to monitor and manage the pressure difference between the airlock and the crankcase and, accordingly, to regulate the pressure to maintain a constant pressure difference between the airlock and the crankcase. Various embodiments of pressure regulators that may be used are described in further detail below and incorporated herein by reference in their entirety in U.S. Patent No. 7,310,945 issued to Gurski et al. on 25 December 2007.

[0306] A constant pressure difference between the airlock 51312 and the crankcase 51304 may be achieved by adding or removing working fluid from the airlock 51312 via a pump or a release valve. Alternatively, a constant pressure difference between the airlock 51312 and the crankcase 51304 may be achieved by adding or removing working fluid from the crankcase 51304 via a pump or a release valve. The pump and release valve may be controlled by a pressure regulator. The working fluid may be added to the airlock 51312 (or crankcase 51304) from a separate source such as a working fluid container, or it may be transmitted from the crankcase 51304. If the working fluid is transmitted from the crankcase 51304 to the airlock 51312, it may cause engine failure. Therefore, it may be desirable to filter the working fluid before it passes into the airlock 51312 to prevent the lubricant from passing from the crankcase 51304 into the airlock 51312 and ultimately into the working space 51306.

[0307] In some embodiments of the machine, the crankcase 51304 may be filled with a fluid having different thermal properties from the working fluid. For example, if the working gas is helium or hydrogen, the crankcase may be filled with argon. Thus, the crankcase is pressurized, and in some embodiments helium is used, but in other embodiments any inert gas as described herein may be used. Thus, the crankcase is a wet pressurized crankcase in exemplary embodiments. In other embodiments where no lubricating fluid is used, the crankcase is not wet.

[0308] In exemplary embodiments, the rolling diaphragms 51300 do not allow gas or liquid to pass through them, which allows the working space 51306 to remain dry and the crankcase 51304 to retain lubricating fluid and become moist. Allowing a moist water-retaining crankcase 51304 reduces friction in the rocking beam drive unit 51316, thereby increasing engine efficiency and lifespan. In some embodiments, the use of roller bearings or ball bearings in the drive unit 51316 may also be eliminated by the use of lubricating fluid and rolling diaphragms 51300. This may further reduce engine noise and increase engine lifespan and efficiency.

[0309] Figures 58A–58E show cross-sections of various embodiments of rolling diaphragms (indicated as 51400, 51410, 51412, 51422, and 51424) configured to be mounted between the upper and lower sealed pistons (indicated as 51328 and 51310 in Figures 57A and 57H) and between the upper and lower mounting surfaces (indicated as 51320 and 51318 i...

Claims

1. A steam distillation apparatus, The raw material fluid inlet, Evaporator and condenser apparatus, A substantially cylindrical casing, A plurality of tubes in the housing, wherein the raw material fluid inlet is fluidly connected to an evaporator / condenser via the plurality of tubes, and the evaporator / condenser converts the raw material fluid into steam and the compressed steam into a product fluid, An evaporator / condenser apparatus equipped with A heat exchanger fluidly connected to the raw material fluid inlet and the product fluid outlet, wherein the heat exchanger is Outer tube and, At least one inner tube, A heat exchanger equipped with, A regenerative blower fluidly connected to the evaporator and condenser, wherein the regenerative blower compresses steam, the compressed steam flows to the evaporator and condenser, and the compressed steam is converted into a product fluid by the evaporator and condenser. A steam distillation apparatus equipped with, A control system for controlling the steam distillation apparatus, A Stirling engine electrically connected to the steam distillation apparatus, the Stirling engine supplying power to the steam distillation apparatus in part, It is equipped with, The control system for controlling the steam distillation apparatus is: At least one controller, The idle state in which at least one of the controllers is not operating, The raw material valve is open and the raw material fluid is injected into the water reservoir of the steam distillation apparatus, A heating state in which the heater in the water reservoir is set to maximum output until the water in the reservoir reaches a predetermined temperature, The heat exchanger reaches its maximum load state when the raw material valve is opened to create a predetermined load cycle, The bearing feed pump is driven at a predetermined speed, and the discharge motor is activated in a start pump state. The steam distillation apparatus is in an operating state that produces product water, A steam distillation system further equipped with the following features.

2. The control system for controlling the steam distillation apparatus A discharge controller that controls the discharge valve, A raw material flow controller configured to maintain a raw material flow rate level by controlling a raw material flow valve, A discharge level sensor connected to the discharge controller and the raw material flow rate controller, wherein the discharge level sensor sends a signal relating to the discharge level to the discharge controller and the raw material flow rate controller which displays the discharge level, Furthermore, it is equipped with, The raw material flow controller drives the raw material flow valve based at least on the signal from the discharge level sensor. The discharge controller drives the discharge valve based at least on the signal from the discharge level sensor. The discharge level and the raw material flow rate level are maintained by using the signal from the discharge level sensor as input. A steam distillation system according to claim 1, characterized in that...

3. The aforementioned Stirling engine is At least one locking drive mechanism, A rocking beam having a rocker pivot, At least one cylinder, At least one piston, each piston housed within a cylinder, is capable of substantially linearly reciprocating within each cylinder, A coupling assembly having a proximal end and a distal end, wherein the proximal end is connected to the piston and the distal end is connected to the locking beam by an end pivot, and the linear motion of the piston is converted into rotational motion of the locking beam, A locking drive mechanism equipped with, A crankcase that houses the locking beam and the first part of the connecting assembly, A crankshaft connected to the locking beam by a connecting rod, wherein the rotational motion of the locking beam is transmitted to the crankshaft, An operating space housing the at least one cylinder, the at least one piston, and the second part of the connecting assembly, A seal for sealing the working space from the crankcase, The steam distillation system according to claim 1, characterized by comprising the following:

4. The steam distillation system according to claim 3, characterized in that the seal is a rolling diaphragm.

5. The aforementioned connecting assembly is Piston rod and, Link stick and, Furthermore, it is equipped with, The steam distillation system according to claim 3 or 4, characterized in that the piston rod and the link rod are connected by a connecting means.

6. The steam distillation system according to any one of claims 3 to 5, further comprising a lubrication fluid pump within the crankcase.

7. The steam distillation system according to any one of claims 1 to 6, characterized in that the heat exchanger is arranged around the housing of the evaporator and condenser.

8. The steam distillation system according to any one of claims 1 to 7, characterized in that the outer tube of the heat exchanger is a raw material fluid passage, and the at least one inner tube is a product fluid passage.

9. The steam distillation system according to any one of claims 1 to 8, wherein the heat exchanger further comprises at least three inner tubes.

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