Water vapor distillation apparatus, methods, and systems

Abstract

To provide a fluid vapor distillation system for producing clean water by clarifying water.SOLUTION: In a fluid vapor distillation system: a control system controlling a fluid vapor distillation apparatus including a raw material flow rate controller controlling an emission valve and a raw material flow rate valve and an emission level sensor connected to an emission controller and the raw material flow rate controller, is included; the emission level sensor sends a signal on an emission level to the emission controller and the raw material flow rate controller displaying the emission level; the raw material flow rate controller drives the raw material flow rate valve based on at least an emission level sensor signal; the emission controller drives the emission valve based on at least the emission level sensor signal; and the emission level and the raw material flow rate level are held by using the emission level sensor signal as input.SELECTED DRAWING: Figure 75

Description

[Technical Field]

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

[0002] Reliable sources of clean water are difficult to obtain for most of humanity. The Department for International Development reports that approximately 1.2 billion people lack access to safe drinking water. The report said millions of deaths each year, mostly children, are attributable to water-related diseases. Many water purification techniques, including carbon filters, chlorination, pasteurization, and reverse osmosis, Many of these techniques are significantly affected by variations in water quality and are not suitable for use in the developing world. Bacteria, viruses, organic matter, arsenic, lead, mercury, etc., which may be found in water supplies. These systems do not address a wide variety of common contaminants, such as chlorine dioxide and pesticides. Some of these require the use of consumables such as filters or chemicals. Some of the technologies require significant infrastructure and highly trained operators. It is only suitable for large centralized water systems that require both consumable and permanent Reliable on a smaller, distributed scale, regardless of water source, with no need for constant maintenance The ability to produce clean water with sufficient yield is highly desirable, especially in the developing world. Summary of the Invention [Problem to be solved by the invention]

[0003] The use of vapor compression distillation to purify water is well known and addresses many of these concerns. However, in some cases, due to scarce financial resources, limited technological assets, and in the developing world, Low population densities that make it unfeasible to build large-scale centralized water systems in most parts of the world Also, the availability of sufficient low-cost, reliable electricity to operate the vapor compression distillation system. restrict the ability to properly maintain such systems. In some situations, it may be necessary to reduce the power required to operate the system while increasing efficiency and production capacity. Improved vapor compression distillation that reduces costs and the amount of system maintenance required The system and associated components can provide a solution. [Means for solving the problem]

[0004] In accordance with one aspect of the present invention, a fluid vapor distillation system is disclosed. The system includes: a discharge controller for controlling the discharge valve, a raw material flow controller for controlling the raw material flow valve, and a discharge level sensor connected to the discharge controller and the raw material flow controller; a control system for controlling the steam distillation apparatus, the emission level sensor detecting the emission level; sending a signal to the discharge controller and the material flow controller indicating the discharge level; The feed flow controller drives the feed flow valve based on at least the discharge level sensor signal. The discharge controller drives the discharge valve based on at least the discharge level sensor signal, and Level and feed flow levels are maintained using the discharge level sensor signal as an input. can be.

[0005] In some embodiments of this aspect of the invention, the control system includes at least one controller At least one controller is idle and not in operation. The valve opens and the raw fluid enters the water reservoir of the fluid vapor distillation apparatus. The fluid in the water reservoir reaches a predetermined temperature. The heating state is such that the heater in the water reservoir is at maximum output until the specified load is reached. When the heat exchanger is in the peak condition, the bearing feed pump is driven at a specified speed and discharged. Start pump state to start the motor and operating state to produce product water for the fluid vapor distillation unit. The system also includes one or more of the following: a raw material fluid inlet; a substantially cylindrical enclosure; and a plurality of tubes in the housing, the raw material fluid inlet being The evaporator-condenser is fluidly connected to the feed fluid, which is converted into vapor and compressed. The heat exchanger is in fluid communication with the feed fluid inlet and the product fluid outlet. The heat exchanger includes an outer tube and at least one inner tube, and the regenerative blower is connected to the evaporator. The regenerative blower is fluidly connected to a condenser and compresses the vapor, which is then evaporated and condensed. The heat exchanger is mounted around the evaporator-condenser housing and converts the compressed steam into product fluid. The outer tube included in the heat exchanger is a raw material fluid flow path, and at least one inner tube is a product fluid flow path. The heat exchanger further includes at least three inner tubes. All three inner tubes are twisted together to form a substantially spiral shape. The connectors are attached to two ends and are used to connect the evaporator and condenser. The evaporator-condenser tubes further contain packing inside the tubes. The packing is rods. The evaporator-condenser further includes a vapor chamber fluidly connected to the plurality of tubes. The control system further includes an impeller assembly driven by a magnetic drive linkage. At least two processors: a motor control engine processor and an ARM The fluid vapor distillation apparatus includes a conductivity measuring device for measuring the conductivity of the production fluid. The device further includes a conductivity meter and a conductivity cell.

[0006] In another aspect of the present invention, a fluid vapor distillation apparatus is disclosed. The apparatus includes a feed fluid inlet, An evaporator-condenser apparatus having a substantially cylindrical housing, and a plurality of tubes in the housing, The fluid inlet is fluidly connected to an evaporator-condenser, which converts the source fluid into vapor. The heat exchanger converts the compressed vapor into a product fluid, and the heat exchanger has a feed fluid inlet and a product fluid outlet. The heat exchanger is fluidly connected to the regenerative block, the heat exchanger including an outer tube and at least one inner tube. The regenerative blower is fluidly connected to the evaporator-condenser, and the regenerative blower compresses the vapor and the compressed vapor The vapor flows to the evaporative condenser, and the compressed vapor is converted into product fluid, which controls the fluid vapor distillation apparatus. The control system includes a discharge controller that controls the discharge valve, a raw material flow controller that controls the raw material flow valve, and a a controller, and an emission level sensor in communication with the emission controller and the feed flow controller. the emission level sensor outputs a signal related to the emission level to indicate the emission level; The raw material flow controller is configured to at least The raw material flow valve is driven based on the signal from the discharge level sensor, and the discharge controller controls at least the discharge The discharge valve is driven based on the signal from the level sensor, thereby controlling the discharge level and the raw material flow rate level. The rule is maintained using the emission level sensor signal as an input.

[0007] In some embodiments of this aspect of the invention, at least one controller, At least one controller is idle, the raw material valve is open and raw material fluid flows. The fluid in the water reservoir of the steam distillation apparatus is poured into the water reservoir until it reaches a predetermined temperature. Heat exchanger with maximum output of heater and opening raw material valve to a predetermined duty cycle. At peak condition, the bearing feed pump is driven at a predetermined speed and the discharge motor is started. and one or more of the operating conditions in which the fluid vapor distillation apparatus produces product water. The heat exchanger is placed around the evaporator-condenser housing. The tubes are feed fluid flow paths and at least one inner tube is a product fluid flow path. The at least three inner tubes are further comprised of a substantially twisted inner tube. The heat exchanger has a spiral shape. The heat exchanger includes two ends, each with a connector. The connectors are attached to form the joints with the evaporator and condenser. The evaporator-condenser further includes a packing inside the tube. The packing is rods. The regenerative blower further includes a steam chamber connected to the impeller. The control system further includes a processor assembly. The fluid vapor distillation apparatus includes a controller engine processor and an ARM® processor. further includes a conductivity meter and a conductivity cell for measuring the conductivity of the product fluid.

[0008] In accordance with one aspect of the present invention, a fluid vapor distillation apparatus is disclosed. an evaporator-condenser apparatus having an inlet, a substantially cylindrical housing, and a plurality of tubes in the housing; The raw fluid inlet is fluidly connected to an evaporator-condenser, which evaporates the raw fluid. The heat exchanger converts the raw fluid into gas and the compressed steam into product fluid. The heat exchanger is fluidly connected to the body outlet, the heat exchanger including an outer tube and at least one inner tube, The regenerative blower is fluidly connected to the evaporator-condenser, and the regenerative blower compresses the vapor and The compressed steam flows to an evaporative condenser, where the compressed steam is converted into product fluid, and the 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 controls the discharge controller, which controls the discharge valve, the raw material flow valve, and the raw material flow controller. a feed flow controller, and a discharge level controller in communication with the feed flow controller; a bell sensor, and an emission level sensor outputs a signal related to the emission level to indicate the emission level; The raw material flow controller sends the raw material to a discharge controller and a raw material flow controller. At the same time, the raw material flow valve is driven based on the signal from the discharge level sensor, and the discharge controller In addition, the discharge valve is driven based on the signal from the discharge level sensor, thereby controlling the discharge level and the raw material. The flow level is maintained using the discharge level sensor signal as an input. The system includes at least one controller, and the at least one controller In the idle state, the raw material valve opens and the raw material enters the sump of the fluid vapor distillation unit. In the ON state, the heater in the water reservoir is set to maximum output until the fluid in the water reservoir reaches the specified temperature. State, open the raw material valve to the specified duty cycle, heat exchanger peak state, bearing feed a start pump state that drives the pump at a predetermined speed and starts the discharge motor, and a fluid vapor When the distillation unit includes an operating state in which product water is produced, the heat exchanger is When the outer tube included in the heat exchanger is the raw material fluid flow path, If the heat exchanger has at least three inner tubes, one of which is in the product fluid flow path. The at least three inner tubes are twisted together to form a substantially helical structure. The heat exchanger further includes two ends, each of which has a connector. When the connector is installed, it forms a joint with the evaporator and condenser. If the tube contains additional packing inside the tube. If the packing is rods. The regenerative blower may further include a steam chamber fluidly connected to the plurality of pipes. The control system further includes an impeller assembly driven by the air drive coupling. The system has at least two processors: a motor control engine processor and an ARM ( If the product contains a refrigerant processor, the fluid vapor distillation device measures the electrical conductivity of the product fluid. The device further includes a conductivity meter and a conductivity cell for measuring the conductivity.

[0010] In accordance with one aspect of the present invention, a steam distillation system is disclosed. a water vapor distillation apparatus including a feed 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 fluidly connected to the evaporator-condenser, The generator-condenser converts the raw fluid into steam and the compressed steam into the product fluid. The system includes a heat exchanger fluidly connected to the feed fluid inlet and the product fluid outlet, The exchanger includes an outer tube and at least one inner tube, and the system is an evaporator-condenser. a regenerative blower fluidly connected to the regenerative blower, the regenerative blower compressing the vapor and generating a compressed vapor; The air flows to the evaporative condenser, where the compressed steam is converted into product fluid, and the system a control system for controlling the steam distillation apparatus, and a starboard electrically connected to the steam distillation apparatus; The Stirling engine comprises a steam distillation system at least in part. Supply power.

[0011] Some embodiments of this aspect of the invention include one or more of the following: That is, the control system controls the discharge controller, which controls the discharge valve, the raw material flow valve, and the raw material flow controller. a feed flow controller, and a discharge level controller in communication with the feed flow controller; a bell sensor, and an emission level sensor outputs a signal related to the emission level to indicate the emission level; The raw material flow controller sends the raw material to a discharge controller and a raw material flow controller. At the same time, the raw material flow valve is driven based on the signal from the discharge level sensor, and the discharge controller In addition, the discharge valve is driven based on the signal from the discharge level sensor, thereby controlling the discharge level and the raw material. The flow level is maintained using the discharge level sensor signal as an input. The system for controlling the device further includes at least one controller, The system is idle with at least one controller not operating, The valve opens and the raw fluid enters the water reservoir of the fluid vapor distillation device. The heating state is that the heater in the water reservoir is at maximum output until the specified load size is reached. When the heat exchanger is in the peak condition, the bearing feed pump is driven at a predetermined speed and the discharge motor the start pump state that starts the motor, and the operating state that the fluid vapor distillation unit produces product water. The Stirling engine includes a rocking beam having a rocker pivot. At least one locking drive mechanism including at least one cylinder, at least one The cylinder includes two pistons, each of which is housed in a cylinder and the pistons are operatively moved within the cylinder. It is possible to achieve a qualitatively linear reciprocating motion, and the Stirling engine is and a distal end, the proximal end of which is connected to the piston. and a distal end connected to the rocking beam by an end pivot for linear motion of the piston. The motion of the rocking beam is converted into rotational motion, and the Stirling engine a crankcase housing the first part of the linkage assembly; a connecting rod; The crankshaft is connected to the rocking beam by a rotational movement of the rocking beam. The Stirling engine is connected to a crankshaft and has at least one cylinder, a small number of an operating space for housing at least one piston and a second portion of the coupling assembly; and , if it includes a seal to seal the working space from the crankcase.

[0012] In some embodiments of this implementation of the system, one or more of the following may occur: Included, i.e., when the seal is a rolling diaphragm. The piston rod and the link rod are connected together by a connecting means. If the system also includes a lubricating fluid pump in the crankcase, is.

[0013] Various embodiments of the system include one or more of the following: When the heat exchanger is placed around the evaporator / condenser housing, the outer tube of the heat exchanger is in contact with the raw material flow. The heat exchanger is a heat exchanger with at least one inner tube serving as a product fluid flow path. When the vessel 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 release valve. a discharge controller for controlling the raw material flow rate valve, a raw material flow rate controller for controlling the raw material flow rate valve, and a discharge controller a discharge level sensor in communication with the feed flow controller; The discharge controller and the raw material flow controller send signals related to the discharge level to display the discharge level. The raw material flow controller is based on at least the signal of the discharge level sensor. The feed flow valve is driven, and the discharge controller controls the discharge level based on at least a signal from the discharge level sensor. The discharge valve is driven, and the discharge level and the material flow level are controlled by the signal of the discharge level sensor. The number is used as input and maintained.

[0015] Some embodiments of this aspect of the invention include one or more of the following: That is, the device further includes at least one controller, and However, at least one controller is idle and not operating, and the raw material valve is open. Injection state of the feed fluid into the water reservoir of the fluid steam distillation apparatus, the fluid in the water reservoir reaches a predetermined temperature The heater in the water reservoir is set to maximum output until the heating state, and the raw material valve is opened to a predetermined duty cycle. When the heat exchanger is at its peak, 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 an evaporator-condenser apparatus including a raw material fluid inlet and a substantially cylindrical housing. and a plurality of tubes in the housing, the raw material fluid inlet being fluidly connected to the evaporator-condenser. The evaporator-condenser converts the raw fluid into steam and the compressed steam into the product fluid. The apparatus includes a heat exchanger fluidly connected to the feed fluid inlet and the product fluid outlet, The exchanger includes an outer tube and at least one inner tube, and the device is an evaporator-condenser and a flow a regenerative blower electrically connected to the regenerative blower, the regenerative blower compressing the steam, the compressed steam The evaporator-condenser heat exchanger converts the compressed steam into a product fluid. When the outer tube included in the heat exchanger is a raw material fluid flow path, At least one inner tube is a product fluid flow path. If the heat exchanger has at least three inner tubes, The at least three inner tubes are twisted together to form a substantially spiral shape. The heat exchanger includes two ends, each with a connector attached. When the evaporator and condenser tubes are connected, the filling inside the tubes is If the packing is rods. If the evaporator and condenser are fluidly connected to multiple tubes. The regenerative blower further comprises a steam chamber having an impeller driven by a magnetic drive coupling. and a control system further comprising at least two processors, i.e., Including a motor control engine processor and an ARM® processor. Fluid vapor The distillation apparatus further includes a conductivity meter and a conductivity cell for measuring the conductivity of the product fluid. In this case,

[0016] According to one aspect of the present invention, a steam distillation apparatus is disclosed. The control system includes at least one controller, At least one controller is in an idle state, and the raw material valve is open and the raw material fluid flows. The state of injection into the water reservoir of the steam distillation apparatus, the fluid in the water reservoir until it reaches the specified temperature Heating condition with heater at maximum output, raw material valve open to set the specified duty cycle, heat exchanger maximum In the full state, 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.

[0017] 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 the discharge valve, a feed flow valve that controls the feed valve, and a feed valve that controls the feed valve. a feed flow controller and a discharge controller in communication with the feed flow controller; The emission level sensor further includes a level sensor, the emission level sensor detecting a signal related to the emission level. The raw material flow controller sends the signal to a discharge controller and a raw material flow controller. and a discharge controller that drives the raw material flow valve based on at least a signal from the discharge level sensor. , and actuating the discharge valve based on at least a signal from the discharge level sensor, thereby and if the feed flow level is maintained using the signal of the discharge level sensor as an input. The apparatus includes a raw material fluid inlet, an evaporator-condenser apparatus including a substantially cylindrical housing, and The housing includes a plurality of tubes, the raw material fluid inlet of which is fluidly connected to the evaporator-condenser, and the evaporator-condenser The condenser converts the raw fluid into steam and the compressed steam into a product fluid. a heat exchanger fluidly connected to the feed fluid inlet and the product fluid outlet, the heat exchanger being external a tube and at least one inner tube, and the device is fluidly connected to an evaporator-condenser; The regenerative blower compresses steam, and the compressed steam is passed through an evaporative condenser. The compressed steam flows to the product fluid. When the outer tube included in the heat exchanger is the raw material fluid passage, at least If one inner tube is in the product fluid flow path, the heat exchanger must have at least three inner tubes. The at least three inner tubes are twisted together to form a substantially helical When the heat exchanger further includes two ends, each end is provided with a connector. If the connector is attached, it forms a joint with the evaporator and condenser. When the tubes contain additional fillers. When the fillers are rods. Evaporators and condensers wherein the regenerative blower further includes a steam chamber fluidly connected to the plurality of pipes. and wherein the control system further includes an impeller assembly driven by the dynamic linkage. At least two processors: a motor control engine processor and an ARM (registered If the product contains a refrigerant processor, the fluid vapor distillation device measures the electrical conductivity of the product fluid. When the device further includes a conductivity meter and a conductivity cell for measuring the conductivity of the sample,

[0018] In accordance with one aspect of the present invention, a fluid vapor distillation apparatus is disclosed. The evaporator-condenser device includes a substantially cylindrical housing and a nozzle. The raw material fluid inlet is fluidly connected to the evaporator-condenser, and the evaporator-condenser includes a plurality of tubes in the body. The condenser converts the feed fluid into vapor and the compressed vapor into a product fluid. The system also includes a heat exchanger fluidly connected to the feed fluid inlet and the product fluid outlet. The heat exchanger includes an outer tube and at least one inner tube. Also included is a regenerative blower fluidly connected to the condenser / evaporator. The compressed vapor flows to an evaporative condenser where the compressed vapor is converted into a product fluid. The solid vapor distillation apparatus also includes a control system.

[0019] In some embodiments of this aspect of the invention, the heat exchanger is mounted around the evaporator-condenser housing. When arranged in a casing, the outer tube is a fluid flow path and at least one inner tube is a product fluid flow path. When the system further includes a heat exchanger, the heat exchanger further includes at least three inner tubes. , when at least three inner tubes are wound to form a substantially helical shape; The heat exchanger further has two ends, each end having a connector attached thereto, the connectors being connected to a steam When forming connections to the evaporator-condenser, the evaporator-condenser tubes are further In the case where the packing is a rod, the evaporator-condenser may further be in fluid contact with the plurality of tubes. In the case of a steam chamber connected to the regenerative blower, the regenerative blower is further driven by a magnetic drive coupling. If an impeller assembly is provided, it may include one or more of:

[0020] According to another aspect of the present invention, a steam distillation system is disclosed. , a raw material fluid input portion, and an evaporator-condenser device. The evaporator-condenser device comprises substantially The apparatus includes a cylindrical housing and a plurality of tubes in the housing. The raw material fluid input section flows into the evaporator-condenser. Physically connected to the evaporator-condenser, the evaporator-condenser converts the raw fluid into steam and delivers the compressed steam to the product stream. The fluid vapor distillation apparatus also includes a raw fluid input section and a product fluid output section. 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 steam, which is then converted into a product fluid. , which flows to the evaporative condenser.

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

[0022] Some embodiments of this aspect of the invention are directed to a Stirling engine having at least one a locking drive mechanism, the locking drive mechanism having a rocker pivot; beam, at least one cylinder, and at least one piston. A piston is housed within each cylinder. The pistons are substantially linear within each cylinder. The drive mechanism has a proximal end and a distal end. At least one coupling assembly, the proximal end of which is connected to the piston and the distal end of which is connected to the end The piston is connected to the rocking beam by a pivot. The first part of the linkage assembly is connected to the rocking beam. It also includes a crankcase that houses the parts. It is connected to the rocking beam by a connecting rod. The rotational motion of the rocking beam is transmitted to the crankshaft. The machine also includes at least one cylinder, at least one piston, and a connecting assembly. It also includes a working space that houses the second part of the assembly. A seal is included to prevent this.

[0023] Additionally, some embodiments of this aspect of the invention are characterized in that the seal is a rolling diaphragm. When the connecting assembly further includes a piston rod and a link rod, When the link rods and the link rods are connected together by a connecting means, the heat exchanger is When arranged around the condenser housing, the outer tube is the fluid flow path and at least one inner tube is the If the product fluid flow path further includes a heat exchanger, the heat exchanger further includes at least three When the inner tube is provided, the evaporator-condenser further includes a steam chamber fluidly connected to the plurality of tubes. In this case, the regenerative blower further comprises an impeller assembly driven by a magnetic drive linkage. When the device is equipped with the above, it includes one or more of the following.

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

[0025] These and other features and advantages of the present invention will become more apparent from the following detailed description of the invention when taken in conjunction with the accompanying drawings. This will be better understood by reading the form: [Figure 1] FIG. 1 is an isometric view of a steam distillation apparatus. [Figure 1A] FIG. 1A is an exploded view of an exemplary embodiment of the present disclosure. [Figure 1B] FIG. 1B is a cross-sectional view of an exemplary embodiment. [Figure 1C] FIG. 1C is a cross-sectional view of an exemplary embodiment. [Figure 1D] FIG. 1D is an assembled view of an exemplary embodiment. [Figure 1E] FIG. 1E is a detailed view of an exemplary embodiment of a frame. [Figure 1F] FIG. 1F is an assembly view of an alternative embodiment. [Figure 1G] FIG. 1G is an assembly view of an alternative embodiment. [Figure 1H] FIG. 1H is an assembly view of an alternative embodiment. [Figure 2] FIG. 2 is an assembled view of an exemplary embodiment of a tube-in-tube heat exchanger assembly. [Figure 2A] FIG. 2A is an exploded view of one embodiment of a tube-in-tube heat exchanger. [Figure 2B] FIG. 2B is a rear isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2C] FIG. 2C is a front isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2D] FIG. 2D is a cross-sectional view of one embodiment of a tube-in-tube heat exchanger. [Figure 2E] FIG. 2E is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger. [Figure 2F] FIG. 2F is a cutaway view of an embodiment of a tube-in-tube heat exchanger illustrating the helical arrangement of the inner tubes. [Figure 2G] FIG. 2G is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger. [Figure 2H] FIG. 2H is an isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2I] FIG. 2I is an isometric view of an exemplary embodiment of a tube-in-tube heat exchanger. [Figure 2J] FIG. 2J is an exploded view of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2K] FIG. 2K is an assembly drawing of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2L] FIG. 2L is an assembly drawing of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2M] FIG. 2M is a detailed view of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2N] FIG. 2N is a detailed view of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2O] FIG. 2O is a schematic diagram of an alternative embodiment of a tube-in-tube heat exchanger configuration. [Figure 2P] FIG. 2P is an assembly view of an alternative embodiment of the heat exchanger. [Figure 2Q] FIG. 2Q is an exploded view of an alternative embodiment of a heat exchanger. [Figure 2R] FIG. 2R is a cross-sectional view of an alternative embodiment of a heat exchanger. [Figure 3] FIG. 3 is an exploded view of a connector for a fitting assembly for a tube-in-tube heat exchanger. [Figure 3A] FIG. 3A is a cross-sectional view of a fitting assembly for a tube-in-tube heat exchanger. [Figure 3B] FIG. 3B is a cross-sectional view of a fitting assembly for a tube-in-tube heat exchanger. [Figure 3C] FIG. 3C is an isometric view of an exemplary embodiment of the first connector. [Figure 3D] FIG. 3D is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3E] FIG. 3E is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3F] FIG. 3F is a cross-sectional view of an exemplary embodiment of the first connector. [Figure 3G] FIG. 3G is an isometric view of an exemplary embodiment of the second connector. [Figure 3H] FIG. 3H is a cross-sectional view of a fitting assembly for a tube-in-tube heat exchanger. [Figure 3I] FIG. 3I is a cross-sectional view of an exemplary embodiment of the second connector. [Figure 3J] FIG. 3J is a cross-sectional view of an exemplary embodiment of the second connector. [Figure 4]FIG. 4 is an isometric view of an exemplary embodiment of an evaporator / condenser assembly. [Figure 4A] FIG. 4A is a cross-sectional view of an exemplary embodiment of an evaporator / condenser assembly. [Figure 4B] FIG. 4B is an isometric cross-sectional view of an exemplary embodiment of an evaporator / condenser. [Figure 4C] FIG. 4C is an isometric view of an alternative embodiment of the evaporator / condenser assembly. [Figure 5] FIG. 5 is an assembly view of an exemplary embodiment of a basin. [Figure 5A] FIG. 5A is an exploded view of an exemplary embodiment of a basin. [Figure 6] FIG. 6 is an isometric detail view of a flange for a sump assembly. [Figure 7] FIG. 7 is an exploded view of an exemplary embodiment of an evaporator / condenser. [Figure 7A] FIG. 7A is a top view of an exemplary embodiment of an evaporator / condenser assembly. [Figure 7B] FIG. 7B shows the percentage of distillate output of the evaporator as a function of pressure for several liquid boiling modes. [Figure 8] FIG. 8 is an isometric view of an exemplary embodiment of a tube for an evaporator / condenser. [Figure 9] FIG. 9 is an exploded view of the tube and rod configuration for the evaporator / condenser. [Figure 9A] FIG. 9A is an isometric view of an exemplary embodiment of an evaporator / condenser rod. [Figure 10] FIG. 10 is an isometric view of an exemplary embodiment of a sump tube plate. [Figure 10A] FIG. 10A is an isometric view of an exemplary embodiment of an upper tube sheet. [Figure 11] FIG. 11 is a detailed view of the top cap for the evaporator / condenser. [Figure 12] FIG. 12 is an isometric view of an exemplary embodiment of a steam chest. [Figure 12A] FIG. 12A is an isometric view of an exemplary embodiment of a steam chest. [Figure 12B]FIG. 12B is a cross-sectional view of an exemplary embodiment of a steam chest. [Figure 12C] FIG. 12C is an exploded view of an exemplary embodiment of a steam chest. [Figure 12D] FIG. 12D is an isometric view of an alternative embodiment. [Figure 12E] FIG. 12E is a cross-sectional view of an exemplary embodiment of a steam chest. [Figure 12F] FIG. 12F is a cross-sectional view of an exemplary embodiment of a steam chest. [Figure 13] FIG. 13 is an assembly drawing of an alternative embodiment of the evaporator / condenser. [Figure 13A] FIG. 13A is a cross-sectional view of an alternative embodiment of an evaporator / condenser. [Figure 13B] FIG. 13B is an assembly drawing of an alternative embodiment of the evaporator / condenser illustrating the arrangement of the tubes. [Figure 13C] FIG. 13C is a cross-sectional view of an alternative embodiment of an evaporator / condenser illustrating the arrangement of the tubes. [Figure 13D] FIG. 13D is an isometric view of an alternative embodiment of an evaporator / condenser without a sump. [Figure 13E] FIG. 13E is an exploded view of an alternative embodiment of the evaporator / condenser. [Figure 14] FIG. 14 is an isometric view of the mist eliminator assembly. [Figure 14A] FIG. 14A is an isometric view of the outside of the cap for the mist eliminator. [Figure 14B] FIG. 14B is an isometric view of the inside of the cap for the mist eliminator. [Figure 14C] FIG. 14C is a cross-sectional view of the mist eliminator assembly. [Figure 14D] FIG. 14D is a cross-sectional view of the mist eliminator assembly. [Figure 15] FIG. 15 is an assembly view of an exemplary embodiment of a regenerative blower. [Figure 15A] FIG. 15A is a bottom view of an exemplary embodiment of a regenerative blower assembly. [Figure 15B]FIG. 15B is a top view of an exemplary embodiment of a regenerative blower assembly. [Figure 15C] FIG. 15C is an exploded view of an exemplary embodiment of a regenerative blower. [Figure 15D] FIG. 15D is a detailed view of the exterior of the top of the housing for the exemplary embodiment of the regenerative blower. [Figure 15E] FIG. 15E is a detailed view of the interior surface of the top of the housing for the exemplary embodiment of the regenerative blower. [Figure 15F] FIG. 15F is a detailed view of the interior surface of the lower portion of the housing for the exemplary embodiment of the regenerative blower. [Figure 15G] FIG. 15G is a detailed view of the exterior of the lower portion of the housing for the exemplary embodiment of the regenerative blower. [Figure 15H] FIG. 15H is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15I] FIG. 15I is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15J] FIG. 15J is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 15K] FIG. 15K is a schematic diagram of an exemplary embodiment of a regenerative blower assembly. [Figure 15L] FIG. 15L is a cross-sectional view of an exemplary embodiment of a regenerative blower. [Figure 16] FIG. 16 is a detailed view of the impeller assembly of an exemplary embodiment of a regenerative blower. [Figure 16A] FIG. 16A is a cross-sectional view of the impeller assembly. [Figure 17] FIG. 17 is an assembly drawing of an alternative embodiment of a regenerative blower. [Figure 17A] FIG. 17A is an assembly drawing of an alternative embodiment of a regenerative blower. [Figure 17B] FIG. 17B is a cross-sectional view of an alternative embodiment of a regenerative blower assembly. [Figure 17C] FIG. 17C is a cross-sectional view of an alternative embodiment of a regenerative blower assembly. [Figure 17D] FIG. 17D is a cross-sectional view of an alternative embodiment of a regenerative blower assembly. [Figure 17E] FIG. 17E is an exploded view of an alternative embodiment of a regenerative blower. [Figure 17F] FIG. 17F is an assembly drawing of the impeller housing. [Figure 17G] FIG. 17G is an exploded view of the impeller housing. [Figure 17H] FIG. 17H is a cross-sectional view of an alternative embodiment of an impeller housing assembly. [Figure 17I] FIG. 17I is a cross-sectional view of an alternative embodiment of an impeller housing assembly. [Figure 17J] FIG. 17J is a bottom view of the lower portion of the impeller housing. [Figure 17K] FIG. 17K is a detailed view of the interior surface of the lower portion of the impeller housing. [Figure 17L] FIG. 17L is a top view of the upper portion of the impeller housing assembly. [Figure 17M] FIG. 17M is a top view of the upper portion of the housing for the impeller assembly without the cover installed. [Figure 17N] FIG. 17N is a detailed view of the interior of the top of the housing for the impeller assembly. [Figure 18] FIG. 18 is a detailed view of the impeller assembly for an alternative embodiment of the regenerative blower. [Figure 18A] FIG. 18A is a cross-sectional view of the impeller assembly. [Figure 19] FIG. 19 is an assembly drawing of the level sensor assembly. [Figure 19A] FIG. 19A is an exploded view of an exemplary embodiment of a level sensor assembly. [Figure 19B] FIG. 19B is a cross-sectional view of the settling tank within the level sensor housing. [Figure 19C] FIG. 19C is a cross-sectional view of the release sensor and product level sensor reservoir within the level sensor housing. [Figure 19D] FIG. 19D is an assembly view of an alternative embodiment of the level sensor assembly. [Figure 19E] FIG. 19E is an exploded view of an alternative embodiment of the level sensor assembly. [Figure 19F] FIG. 19F is a cross-sectional view of an alternative embodiment of a level sensor assembly. [Figure 19G] FIG. 19G is a schematic diagram of the operation of the level sensor assembly. [Figure 19H] FIG. 19H is an alternative embodiment of the level sensor assembly. [Figure 20] FIG. 20 is an isometric view of the level sensor assembly. [Figure 20A] FIG. 20A is a cross-sectional view of the level sensor assembly. [Figure 21] FIG. 21 is a front isometric view of the bearing feed pump. [Figure 21A] FIG. 21A is an isometric view of the rear side of the bearing feed pump. [Figure 22] FIG. 22 is a schematic diagram of the source water flow path for an exemplary embodiment of a water vapor distillation apparatus. [Figure 22A] FIG. 22A is a schematic diagram of source water entering a heat exchanger. [Figure 22B] FIG. 22B is a schematic diagram of source water passing through a heat exchanger. [Figure 22C] FIG. 22C is a schematic diagram of the source water exiting the heat exchanger. [Figure 22D] FIG. 22D is a schematic diagram of source water passing through a regenerative blower. [Figure 22E] FIG. 22E is a schematic diagram of source water exiting and entering the regenerative blower. [Figure 23] FIG. 23 is a schematic diagram of the blowdown water flow path for an exemplary embodiment of a water vapor distillation apparatus. [Figure 23A] FIG. 23A is a schematic diagram of blow-off water exiting the evaporator / condenser assembly and entering the level sensor housing. [Figure 23B] FIG. 23B is a schematic diagram of blowdown water filling the settling tank within the level sensor housing. [Figure 23C] FIG. 23C is a schematic diagram of blow-off water filling the blow-off level sensor reservoir within the level sensor housing. [Figure 23D]FIG. 23D is a schematic diagram of blowdown water exiting the level sensor housing and entering the strainer. [Figure 23E] FIG. 23E is a schematic diagram of blowdown water exiting the strainer and entering the heat exchanger. [Figure 23F] FIG. 23F is a schematic diagram of blowdown water passing through a heat exchanger. [Figure 23G] FIG. 23G is a schematic diagram of blowdown water exiting the heat exchanger. [Figure 24] FIG. 24 is a schematic diagram of the product water flow path for an exemplary embodiment of a water vapor distillation apparatus. [Figure 24A] FIG. 24A is a schematic diagram of product water exiting the evaporator / condenser assembly and entering the level sensor housing. [Figure 24B] FIG. 24B is a schematic diagram of product water entering the product level sensor reservoir within the level sensor housing. [Figure 24C] FIG. 24C is a schematic diagram of the product water exiting the product level sensor reservoir and entering the heat exchanger. [Figure 24D] FIG. 24D is a schematic diagram of product water passing through a heat exchanger. [Figure 24E] FIG. 24E is a schematic diagram of the product water exiting the heat exchanger. [Figure 24F] FIG. 24F is a schematic diagram of product water entering the bearing feedwater reservoir within the level sensor housing. [Figure 24G] FIG. 24G is a schematic diagram of the product water exiting the level sensor housing and entering the bearing feed pump. [Figure 24H] FIG. 24H is a schematic diagram of the product water exiting the bearing feed pump and entering the regenerative blower. [Figure 24I] FIG. 24I is a schematic diagram of the product water exiting the regenerative blower and entering the level sensor housing. [Figure 25] FIG. 25 is a schematic diagram of an air passage for an exemplary embodiment of a water vapor distillation apparatus. [Figure 25A]FIG. 25A is a schematic diagram of the vent path that allows air to exit the emission sensor reservoir and enter the evaporative condenser. [Figure 25B] FIG. 25B is a schematic diagram of the vent path that allows air to exit the product sensor reservoir and enter the evaporative condenser. [Figure 25C] FIG. 25C is a schematic diagram of the vent path that allows air to exit the evaporator / condenser assembly. [Figure 26] FIG. 26 is a schematic diagram of low pressure steam entering the tubes of the evaporator / condenser assembly from the sump. [Figure 26A] FIG. 26A is a schematic diagram of low pressure steam passing through the tubes of an evaporator / condenser assembly. [Figure 26B] FIG. 26B is a schematic diagram of wet low pressure steam exiting the tubes of the evaporator / condenser assembly and entering the steam chest. [Figure 26C] FIG. 26C is a schematic diagram of wet low-pressure steam flowing through the vapor chest of the evaporator / condenser assembly. [Figure 26D] FIG. 26D is a schematic diagram of the production of blowdown water as low pressure steam passing through the steam chest. [Figure 26E] FIG. 26E is a schematic diagram of dry low pressure steam exiting the steam chest and entering the regenerative blower. [Figure 26F] FIG. 26F is a schematic diagram of dry low-pressure steam passing through a regenerative blower. [Figure 26G] FIG. 26G is a schematic diagram of high pressure steam exiting the regenerative blower. [Figure 26H] FIG. 26H is a schematic diagram of high pressure steam entering a steam pipe. [Figure 26I] FIG. 26I is a schematic diagram of high pressure steam exiting the steam line and entering the evaporator / condenser chamber. [Figure 26J] FIG. 26J is a schematic diagram of the generation of product water from high pressure steam condensing in an evaporator / condenser chamber. [Figure 27]FIG. 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] FIG. 28 is a graph illustrating the relationship between product production rate and the number of heat transfer tubes in the evaporator / condenser assembly. [Figure 29] FIG. 29 is a graph illustrating the product water production rate of an evaporator / condenser assembly as a function of the amount of heat transfer surface area associated with the evaporator / condenser chamber. [Figure 30] FIG. 30 is a graph illustrating the heat transfer surface efficiency for varying amounts of heat transfer tubes in an evaporator / condenser assembly as it relates to changes in pressure across the regenerative blower. [Figure 31] FIG. 31 is a graph illustrating the amount of energy consumed by the evaporator / condenser assembly at different pressure differentials across production rates and regenerative blowers. [Figure 32] FIG. 32 is a cross-sectional top view of a rotor and stator according to a particular embodiment, showing the support structure for the input, the blades and chambers between the blades, and the rotating drive shaft. [Figure 32A] FIG. 32A is a side top view of the rotor and stator corresponding to the embodiment shown in FIG. 32, showing the support structures for the input and output, the blades, the eccentric arrangement within the housing unit, and the drive shaft. [Figure 32B] FIG. 32B is a top view of the rotor and stator corresponding to the embodiment shown in FIGS. 32 and 32A, showing the support structures for the input and output sections, the blades, the eccentric arrangement within the housing unit, and the drive shaft. [Figure 32C] FIG. 32C is a cross-sectional view of the rotor and stator corresponding to the embodiment shown in FIGS. 32, 32A, and 32B, showing the blades, drive shaft, and bearings. [Figure 32D] FIG. 32D is a cross-sectional view of a liquid ring pump according to one embodiment showing a capacitance sensor. [Figure 32E]FIG. 32E is a cross-sectional view of a liquid ring pump according to one embodiment showing the eccentric rotor, rotor blades, drive shaft with bearings, rotating housing unit for the liquid ring pump, stationary housing, and the cyclone effect from the steam and the resulting exclusion of mist and water droplets. [Figure 32F] FIG. 32F is a schematic diagram of an alternative embodiment of a liquid ring pump. [Figure 32G] FIG. 32G is a top view of an alternative embodiment of a rotor showing multiple vanes and chambers between the vanes, as well as the intake and exit holes for each individual chamber. [Figure 32H] FIG. 32H is further detail of the liquid ring pump showing the stationary intake port and rotating drive shaft, rotor, and housing unit. [Figure 32I] FIG. 32I is a diagram of a seal that may be present between the stationary and rotor portions of a liquid ring pump, separating the intake from the outlet. [Figure 33] FIG. 33 is a side view of a backpressure regulator according to one embodiment. [Figure 33A] FIG. 33A is a diagonal view of the backpressure regulator shown. [Figure 33B] FIG. 33B is a side view of an alternative embodiment of a backpressure regulator having vertically oriented ports. [Figure 33C] FIG. 33C is a diagonal view of the backpressure regulator shown. [Figure 33D] FIG. 33D is an enlarged view of portion C of FIG. 33D depicting the port cutouts of the backpressure regulator. [Figure 33E] FIG. 33E is a close-up view of section C of FIG. 33D, depicting the ports of the backpressure regulator. [Figure 33F] FIG. 33F is a cutaway side view of one embodiment of a backpressure regulator. [Figure 33G] FIG. 33G is an enlarged view of portion E of FIG. 33F depicting the small opening of the backpressure regulator port. [Figure 34] FIG. 34 is a schematic diagram of a backpressure regulator implemented within the device. [Figure 35] FIG. 35 is a schematic diagram of an alternative embodiment of a water vapor distillation apparatus. [Figure 35A] FIG. 35A is a detailed schematic diagram of an alternative embodiment of the level sensor housing depicting external connection valves between the source and discharge fluid lines. [Figure 36] FIG. 36 is a view of the pump side of the fluid distribution manifold. [Figure 36A] FIG. 36A is a view of the second face of the pump side of the fluid distribution manifold. [Figure 36B] FIG. 36B is a side view of the evaporator / condenser side of the fluid distribution manifold. [Figure 36C] FIG. 36C is a view of the second face of the evaporator / condenser side of the fluid distribution manifold. [Figure 37] FIG. 37 is a top view of a coupler of an alternative embodiment of a fitting assembly. [Figure 37A] 37A is a side view of an alternative embodiment of the fitting assembly of FIG. 37. FIG. [Figure 38] FIG. 38 is a cross-sectional view of an alternative embodiment of an evaporator / condenser having separate heating layers and ribs. [Figure 38A] FIG. 38A is a cross-sectional detail of an alternative embodiment of an evaporator / condenser showing how the ribs effectively separate the vapor / evaporation from the liquid / condensate layer. [Figure 39] FIG. 39 is a schematic diagram of an alternative embodiment of a heat exchanger. [Figure 39A] FIG. 39A is a schematic diagram of an alternative embodiment of a heat exchanger. [Figure 40] FIG. 40 is a schematic overview of an alternative embodiment of a water vapor distillation apparatus that includes system pressure measurement using a cold air sensor. [Figure 41] FIG. 41 shows a diagram of a flip filter with the intake and discharge streams flowing through the filter units, each of which rotates about a pivot joint about a central axis. [Figure 41A] FIG. 41A shows a flip filter housing. [Figure 41B] FIG. 41B is a detailed diagram of the flip filter of FIG. [Figure 41C]FIG. 41C is an alternative embodiment of a composite flip filter. [Figure 41D] FIG. 41D is a schematic diagram of an alternative embodiment of a flip filter. [Figure 41E] FIG. 41E is a schematic diagram of the flow path of one embodiment of a flip filter. [Figure 41F] FIG. 41F is a schematic diagram illustrating a manual switch for varying the water flow through the individual units of the flip filter of FIG. 41E. [Figure 42] FIG. 42 is a depiction of a surveillance system for a distributed public facility. [Figure 43] Figure 43 is a depiction of a distribution system for a public facility. [Figure 44] FIG. 44 is a conceptual flow diagram of a possible embodiment of a system incorporating an alternative embodiment of a water vapor distillation apparatus. [Figure 44A] FIG. 44A is a schematic block diagram of a power supply for use with the system shown in FIG. [Figure 45A] FIG. 45A illustrates the principle of operation of a Stirling cycle machine. [Figure 45B] FIG. 45B illustrates the principle of operation of a Stirling cycle machine. [Figure 45C] FIG. 45C illustrates the principle of operation of a Stirling cycle machine. [Figure 45D] FIG. 45D illustrates the principle of operation of a Stirling cycle machine. [Figure 45E] FIG. 45E illustrates the principle of operation of a Stirling cycle machine. [Figure 46] FIG. 46 shows a diagram of a rocking beam drive, according to one embodiment. [Figure 47] FIG. 47 shows a diagram of a rocking beam drive, according to one embodiment. [Figure 48] FIG. 48 shows a diagram of an engine, according to one embodiment. [Figure 49A] FIG. 49A depicts various views of a rocking beam drive, according to one embodiment. [Figure 49B]FIG. 49B depicts various views of a rocking beam drive, according to one embodiment. [Figure 49C] FIG. 49C depicts various views of a rocking beam drive, according to one embodiment. [Figure 49D] FIG. 49D depicts various views of a rocking beam drive, according to one embodiment. [Figure 50] FIG. 50 shows a bearing style rod connector, according to one embodiment. [Figure 51A] FIG. 51A shows a bend, according to one embodiment. [Figure 51B] FIG. 51B shows a bend, according to one embodiment. [Figure 52] FIG. 52 shows a four-cylinder dual rocking beam drive arrangement, according to one embodiment. [Figure 53] FIG. 53 shows a cross section of a crankshaft according to one embodiment. [Figure 54A] FIG. 54A shows a diagram of an engine, according to one embodiment. [Figure 54B] FIG. 54B shows a crankshaft connection according to one embodiment. [Figure 54C] FIG. 54C shows a diagram of a sleeve rotor, according to one embodiment. [Figure 54D] FIG. 54D shows a view of a crankshaft, according to one embodiment. [Figure 54E] FIG. 54E is a cross section of a sleeve rotor and splined shaft according to one embodiment. [Figure 54F] FIG. 54F is a cross section of a crankshaft and splined shaft according to one embodiment. [Figure 54G] FIG. 54G shows various views of a sleeve rotor, crankshaft, and splined shaft according to one embodiment. [Figure 55] FIG. 55 illustrates the operation of a piston in an engine, according to one embodiment. [Figure 56A] FIG. 56A shows an unpackaged schematic view of the workspace and cylinder, according to one embodiment. [Figure 56B]FIG. 56B shows a schematic diagram of the cylinder, heater head, and regenerator according to one embodiment. [Figure 56C] FIG. 56C shows a view of a cylinder head, according to one embodiment. [Figure 57A] FIG. 57A shows a view of a rolling diaphragm with supporting top and bottom seal pistons, according to one embodiment. [Figure 57B] FIG. 57B is an exploded view of a rocking beam drive engine, according to one embodiment. [Figure 57C] FIG. 57C shows a diagram of the cylinder, heater head, regenerator, and rolling diaphragm according to one embodiment. [Figure 57D] FIG. 57D shows various views of a rolling diaphragm in operation, according to one embodiment. [Figure 57E] FIG. 57E shows various views of a rolling diaphragm in operation, according to one embodiment. [Figure 57F] FIG. 57F shows an unpackaged schematic view of the workspace and cylinder, according to one embodiment. [Figure 57G] FIG. 57G shows a diagram of an external combustion engine, according to one embodiment. [Figure 58A] FIG. 58A shows diagrams of various embodiments of rolling diaphragms. [Figure 58B] FIG. 58B shows diagrams of various embodiments of rolling diaphragms. [Figure 58C] FIG. 58C shows diagrams of various embodiments of rolling diaphragms. [Figure 58D] FIG. 58D shows diagrams of various embodiments of rolling diaphragms. [Figure 58E] FIG. 58E shows diagrams of various embodiments of rolling diaphragms. [Figure 59A] FIG. 59A shows a diagram of a metal bellows and associated piston rod and piston, according to one embodiment. [Figure 59B] FIG. 59B shows a diagram of a metal bellows diaphragm, according to one embodiment. [Figure 59C]FIG. 59C shows a diagram of a metal bellows diaphragm, according to one embodiment. [Figure 59D] FIG. 59D shows a diagram of a metal bellows diaphragm, according to one embodiment. [Figure 59E] FIG. 59E shows a diagram of a metal bellows, according to various embodiments. [Figure 59F] FIG. 59F shows a diagram of a metal bellows, according to various embodiments. [Figure 59G] FIG. 59G shows a diagram of a metal bellows, according to various embodiments. [Figure 59H] FIG. 59H shows a schematic of a rolling diaphragm identifying the various load regions. [Figure 59I] FIG. 59I shows a schematic diagram of a rolling diaphragm identifying the convolution regions. [Figure 60] FIG. 60 shows a diagram of a piston and piston seal, according to one embodiment. [Figure 61] FIG. 61 shows a diagram of a piston rod and piston rod seal, according to one embodiment. [Figure 62A] FIG. 62A shows a diagram of a piston seal backing ring, according to one embodiment. [Figure 62B] FIG. 62B shows a pressure diagram for the backing ring, according to one embodiment. [Figure 62C] FIG. 62C shows a piston seal, according to one embodiment. [Figure 62D] FIG. 662D shows a piston seal, according to one embodiment. [Figure 62E] FIG. 62E shows a piston rod seal, according to one embodiment. [Figure 62F] FIG. 62F shows a piston rod seal, according to one embodiment. [Figure 63A] FIG. 63A shows a diagram of a piston seal backing ring, according to one embodiment. [Figure 63B] FIG. 63B shows a pressure diagram for a piston seal backing ring, according to one embodiment. [Figure 64A]FIG. 64A shows a diagram of a piston rod seal backing ring, according to one embodiment. [Figure 64B] FIG. 64B shows a pressure diagram for a piston rod seal backing ring, according to one embodiment. [Figure 65] FIG. 65 shows a view of a piston guide ring, according to one embodiment. [Figure 66] FIG. 66 shows an unpackaged schematic view of the workspace and cylinder, according to one embodiment. [Figure 67A] FIG. 67A shows a diagram of an engine, according to one embodiment. [Figure 67B] FIG. 67B shows a diagram of an engine, according to one embodiment. [Figure 68] FIG. 68 shows a diagram of a crankshaft, according to one embodiment. [Figure 69A] FIG. 69A shows various configurations of pump drives, according to various embodiments. [Figure 69B] FIG. 69B shows various configurations of pump drives, according to various embodiments. [Figure 69C] FIG. 69C shows various configurations of pump drives, according to various embodiments. [Figure 70A] FIG. 70A shows various views of an oil pump, according to one embodiment. [Figure 70B] FIG. 70B shows a diagram of an engine, according to one embodiment. [Figure 70C] FIG. 70C shows another view of the engine depicted in FIG. 70B. [Figure 71A] FIG. 71A shows a diagram of an engine, according to one embodiment. [Figure 71B] FIG. 71B shows a diagram of an engine, according to one embodiment. [Figure 71C] FIG. 71C shows a diagram of a coupling joint, according to one embodiment. [Figure 71D] FIG. 71D shows a diagram of the crankshaft and splined shaft of the engine, according to one embodiment. [Figure 72A] FIG. 72A shows an illustration of a generator connected to one embodiment of the device. [Figure 72B] FIG. 72B shows a schematic diagram of an auxiliary power unit for providing power and heat to the water vapor distillation apparatus. [Figure 72C] FIG. 72C shows a schematic diagram of the system, according to one embodiment. [Figure 73] FIG. 73 is a schematic diagram of the flow path according to one embodiment of a water vapor distillation apparatus. [Figure 74] FIG. 74 is an isometric view of an embodiment of a tube-in-tube heat exchanger with an embodiment of a connector attached. [Figure 74A] FIG. 74A is an isometric view of one embodiment of the connector shown in FIG. [Figure 74B] 74B is a cross-sectional view of one embodiment of the connector shown in FIG. [Figure 74C] 74C is an end view of one embodiment of the connector shown in FIG. [Figure 75] FIG. 75 is a flow diagram of the water operating states. [Figure 76] FIG. 76 is a schematic diagram of a communication system with at least one water vapor distillation device, according to one embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0026] Definitions. As used in this description and the appended claims, the following terms have other meanings unless the context requires otherwise. Unless otherwise required, terms and conditions shall have the meaning indicated.

[0027] The term "fluid" is used herein to include any type of fluid, including water. Therefore, the exemplary embodiment and various other embodiments are described herein with respect to water. Although described herein, the scope of the devices, systems, and methods includes any type of fluid. Also, as used herein, the term "liquid" refers to exemplary embodiments in which the fluid is a liquid. It may be used to

[0028] The term "evaporator-condenser" refers to a device that is a combined evaporator and condenser. As used herein, therefore, a structure may be used when the structure itself serves both functions. The evaporator-condenser structure is referred to herein as the evaporator / condenser, They are also called evaporators and condensers, or evaporators and condensers. When either the evaporator or the condenser are referred to individually, the term is not limiting and refers to the evaporator-condenser combination. It should be understood to refer to a condenser structure.

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

[0030] "Cleaner water" is used herein to refer to water that is cleaner as a product water than as a source water. Used.

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

[0032] The term "product water" refers to the cleaner water that exits the device.

[0033] As used in this specification and any accompanying claims, the term "purifying" refers to The term refers to the step of reducing the concentration of one or more contaminants or the step of reducing the concentration of one or more contaminants. This refers to the step of modifying the concentration.

[0034] As used herein, the term "specified level" refers to a level that is used for a particular application. "Specified level" refers to some desired level of concentration as established by the user. An example of a specified level is: Limiting contaminant levels in fluids to carry out industrial or commercial processes. One example is to measure the contaminant levels in a solvent or reactant during a chemical reaction (e.g., polymerization). ) to an acceptable level to enable industrially significant benefits. Another example of a designated level is a level regulated by a government or intergovernmental agency for safety or health reasons. It may also be the level of a certain contaminant in a fluid, as determined by the Concentrations of one or more contaminants in water used for certain health or medical purposes, World Health Organization These may include concentration levels established by organizations such as the U.S. Environmental Protection Agency or the International Chemical Substances Control Organization (ICCO).

[0035] As used herein, the term "system" refers to a steam distillation apparatus (water system steam distillation systems), and power sources such as Stirling engines refers to any combination of elements, including, but not limited to, a steam distillation apparatus with Good too.

[0036] In this specification, the process of converting dirty water, known as source water, into cleaner water, known as product water, is called An apparatus for distillation is disclosed. The apparatus is configured to evaporate water and separate particulates from the water. As used in this specification and any accompanying claims, " The term "purifying" refers to substantially reducing the concentration of one or more contaminants to below a specified level. gradually reducing or substantially improving the concentration of one or more contaminants to within a specified range. Refers to the step of changing.

[0037] The source water first passes through a counter-flow tube-in-tube heat exchanger to increase the temperature of the water. Increasing the temperature of the source water will increase the amount of heat required to evaporate the water in the evaporator / condenser. The source water absorbs heat energy from other fluid streams present in the heat exchanger. Typically, these other streams have a higher temperature than the source water. This allows thermal energy to flow from the higher temperature stream to the lower temperature source water.

[0038] The heated source water is received by the evaporator area of ​​the evaporator / condenser assembly. The membrane vaporizes the source water to separate contaminants from the water. The thermal energy is generated by the heating element and Typically, heating elements are used during initial start-up. Therefore, under normal operating conditions, the heat energy is provided by high-pressure steam. The source water fills the inner tubes of the evaporator section of the evaporator / condenser. High pressure steam flows onto the outer surface of these tubes. When condensed at , heat energy is transferred to the source water. After the source water is converted into low-pressure steam, the steam exits the tubes. The steam may then pass through a separator, which removes any remaining water droplets in the steam and passes them through a separator before entering the compressor. Ensure that the low pressure steam is dry.

[0039] Upon exiting the evaporator of the evaporator / condenser, the low pressure vapor enters the compressor. High pressure steam is produced by compressing low pressure steam. As the steam is compressed, The temperature of the steam increases. Once the steam is at the increased temperature and pressure, it exits the compressor. .

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

[0041] The level sensor housing includes a level sensor for determining the amount of product water and blowdown water in the device. These sensors measure the amount of product water being produced depending on the water level in the device. This allows the operator to adjust the volume or amount of incoming source water.

[0042] The water vapor distillation apparatus as described herein with respect to various embodiments further comprises: It may also be used in conjunction with a Stirling engine to form a distillation system. The power required by the steam distillation system is supplied by a starboard electrical The data may be provided by a processing engine.

[0043] Referring to Figure 1, one embodiment of a water vapor distillation apparatus 100 is shown. For purposes of illustration, the embodiment shown in FIG. 1 is referred to as an exemplary embodiment. Other embodiments are contemplated, and The system 100 includes a heat exchanger 102 and an evaporator / condenser. a condenser assembly 104, a regenerative blower 106, a level sensor assembly 108, and a bearing The water vapor distillation apparatus 100 may include a water pump 110 and a frame 112. See also Figures 1A-E for detailed views and cross sections.

[0044] 1F-H, these figures illustrate an alternative embodiment of a water vapor distillation apparatus 100. FIG. 1F shows an apparatus 120 having an alternative configuration of an evaporator / condenser assembly 122. Similarly, FIG. 1G discloses an apparatus having an alternative configuration of the evaporator / condenser assembly 132. Similarly, FIG. 1H illustrates the level sensor assembly 108 and bearing water supply from FIGS. 1-1E. Another embodiment of the device is shown that does not include a pump 110. (heat exchanger) Referring now to FIG. 2-2A, in an exemplary embodiment of a water vapor distillation apparatus, the heat exchanger comprises: The heat exchanger assembly 200 may be a counter-flow tube-in-tube heat exchanger assembly 200. In this embodiment, The heat exchanger assembly 200 includes an outer tube 202 and a plurality of inner tubes 204, as shown in FIG. 2A. , and a pair of connectors 206. Alternative embodiments of the heat exchanger assembly 200 include , the connector 206 may not be included.

[0045] Still referring to FIG. 2-2A, the heat exchanger assembly 200 includes several independent fluid paths. In the exemplary embodiment, the outer pipe 202 is connected to the source water and the four inner pipes 204. Three of these inner tubes 204 contain the product water produced by the device. The fourth inner tube may contain blowdown water.

[0046] Still referring to FIG. 2-2A, the heat exchanger assembly 200 increases the temperature of the incoming source water. When the source water contacts the outer surface of the inner pipe 204, the inner pipe 204 Heat energy is transferred through the wall from the higher temperature discharge water to the lower temperature source water. Source water with a higher temperature requires less energy to evaporate the water. Therefore, increasing the temperature of the source water increases the efficiency of the steam distillation apparatus 100. Reducing the temperature of the product water conditions the water for use by the consumer.

[0047] Still referring to FIG. 2-2A, in the exemplary embodiment, heat exchanger 200 includes several The tube-in-tube heat exchanger has an outer tube 202 that has a function. The outer tube 202 protects and contains the inner tube 204. The outer tube 202 provides a barrier between the inner tube 204 and the surrounding environment. In addition, the outer tube 20 2 also prevents the exchange of heat energy into the surrounding environment, thereby reducing the The outer tube 202 insulates the inner tube 204, reducing heat transfer to and from the surrounding environment. Similarly, the outer tube 202 resists heat transfer from the inner tube 204, reducing the heat transfer to the source water. The transfer may be concentrated to increase the efficiency of the heat exchanger 200 .

[0048] Still referring to FIG. 2-2A, the outer tube 202 may be made of any material, but may be made of a low High thermal conductivity is desirable. Low thermal conductivity is required because the outer tube 202 insulates the inner tube 204 from the surrounding environment. is important because thermally conductive materials reduce the heat energy loss or gain to the surrounding environment. The low thermal conductivity of the outer tube improves the efficiency of the heat exchanger. This reduces the amount of heat energy that may be transferred from the outer tube 204 to the outer tube 202. The resistance to the heat energy is such that more heat energy escapes from the device through the outer tube 202. Rather, it allows the heat to be transferred to the source water. Therefore, it is made of a material with low thermal conductivity. The outer tube 202 allows more heat energy to be lost to the surrounding environment rather than being gained. Rather, it allows the water to be transmitted to the source water.

[0049] Still referring to FIG. 2-2A, in the exemplary embodiment, the outer tube 202 is made of clear silicone. In addition to having low thermal conductivity, silicone materials are also corrosion resistant. This is an important characteristic for preventing corrosion of the heat exchanger 200. Water may contain chemicals and / or other highly reactive materials. may cause the outer tubing 202 made of other materials to decompose, reducing the useful life of the heat exchanger 200. In an alternative embodiment, the outer tube 202 may be made of a high temperature resistant plastic or rubber. Additionally, in one embodiment, the outer tube 202 may be made of other materials such as rubber to enhance mixing. The tubes are made of convoluted tubing to increase heat transfer efficiency.

[0050] 2B-C, another desirable feature is that the outer tubing 202 is The purpose of the present invention is to provide sufficient elasticity to support the placement of the heat exchanger 200 within the device 100. In some applications, the space for the distillation apparatus may be limited by other environmental or situational constraints. For example, in the exemplary embodiment, the heat exchanger 200 encases an evaporator / condenser. In other embodiments, the heat exchanger may also be configured to minimize heat loss or gain from the environment. In an exemplary embodiment, the heat exchanger may be incorporated into the insulating cover of the water vapor distillation apparatus. 200 may be configured in a coil as shown in Figures 2B-C. To do this, the inner tube 204 is slid into the outer tube 202 and then wrapped around a mandrel. A flexible outer tube 202 assists in locating the end of the heat exchanger 200 at a specific location within the device. Therefore, by having the elastic outer tube 202, the heat exchanger in the water vapor distillation apparatus 100 200 may be easily installed.

[0051] Still referring to Figures 2B-C, the resilience of the material of the outer tubing 202 is also affected by the wall thickness. Tubing with thick walls is less flexible. However, if the wall pressure is A thicker wall thickness improves the thermal properties of the tubing, as the thickness has better heat transfer resistance. In addition, the wall thickness of the tubing must be able to withstand the internal pressure generated by the source water within the tubing. However, tubing with increased wall thickness has reduced elasticity. and increases the size of the heat exchanger assembly. This requires a large bending radius, which affects the installation of the heat exchanger 200. Conversely, a wall thickness that is too thin may result in a loss of functionality. The tubing has a tendency to kink during installation. This deformation of the tubing can cause the flow of source water through the outer pipe 202. This can restrict flow and cause a reduction in the efficiency of the heat exchanger 200.

[0052] The diameter of the outer tube 202 may be any diameter capable of containing multiple inner tubes 204. However, the larger the diameter, the less flexible the tubing becomes. This may adversely affect the installation of a heat exchanger in the water vapor distillation apparatus 100. In the illustrated embodiment, the diameter of the outer tube 202 is 1 inch. This diameter is determined by the tube size upon final installation. Allows the tube-in-tube heat exchanger 200 to be wrapped around the evaporator / condenser 104 , contains four inner pipes 204 for transporting product water and blowdown water. , the heat exchanger may have as few as two inner tubes 204. Similarly, in other embodiments, the heat The exchanger may have five or more inner tubes 204 .

[0053] 2A and 2D, inner pipe 204 is for source water, product water, and blowdown water. In an exemplary embodiment, these pipes may provide separate flow paths for the product water and the discharge water. However, in other embodiments, the inner tube may contain additional fluid streams. The inner pipe 204 is used to separate clean and safe drinking water from contaminated and unhealthy source and discharge water. In the exemplary embodiment, there are three inner pipes 204 for the product water and one for the discharge. The source water travels through the outer tube 202 of the heat exchanger 200. In embodiments, the number of inner tubes may vary, i.e., a greater number of inner tubes may be included. More or fewer inner tubes may be included.

[0054] Still referring to Figures 2A and 2D, the inner tube 204 transfers thermal energy through the tube wall. The thermal energy is transferred through the tube walls to the hot product and reject water in the inner tube 204. Therefore, the inner tube 204 preferably has high thermal conductivity. The casing is made of a material that is resistant to corrosion and, in addition, is preferably made of a material that is corrosion resistant. In an embodiment, the inner tube 204 is made of copper. The inner tube 204 may be made of other materials such as brass or titanium. These other materials have the properties of high thermal conductivity and corrosion resistance. For applications where source water such as seawater and discharge water are highly concentrated, the inner pipe 204 may be made of, but not limited to, copper nickel, titanium, or thermally conductive plastic. Not determined.

[0055] In addition to the tubing material, the diameter and thickness of the tubing also affect the rate of thermal energy transfer. Increasing the wall thickness of the tubing also increases the resistance to heat transfer, so Inner tubing 204 with a thicker wall thickness may have less thermal efficiency. In this embodiment, the inner tube 204 has an outer diameter of 0.25 inches. A thinner wall thickness increases the heat transfer coefficient. However, the wall thickness must be sufficient to allow it to be molded or formed without deformation. Thinner walled tubing is more likely to kink, pinch, or collapse during formation. The wall thickness of the inner tube 204 must be sufficient to withstand the internal pressure generated by water passing through the tube. It must be.

[0056] Still referring to FIGS. 2A and 2D, additional heat transfer coefficient enhancements for the inner tube 204 include: A common method includes a non-uniform inner tube diameter and an extended surface on the inner tube to enhance heat transfer. Additionally, the outer tube 202 may have a textured inner surface, The flow of source water may be turbulent to enhance heat transfer. To create turbulence, the thermal conductivity is increased. The turbulence increases the thermal conductivity of the inner tube 204 where heat transfer occurs. In contrast, without a textured surface, water is more likely to be absorbed by the surface. This laminar flow ensures that only a limited amount of water comes into contact with the outer surface of the inner tube 204. Convective heat transfer between the water near the inner tube and the remaining water near the outer surface of the inner tube 204 The remaining water that is not in contact with the inner tube 204 does not transfer much heat energy because it is not as efficient as the inner tube 204. Some examples of textured surfaces are dimples, fins, ridges, or grooves. In another embodiment, the outer tube may include, but is not limited to, a This may increase the shell-side flow velocity and therefore enhance heat transfer.

[0057] Referring now to FIG. 2E, typically, the inner tubes 204 are arranged parallel to one another. However, in some embodiments, the inner tube 204 may be, as illustrated in FIGS. 2F-G, Braided or wound together to form a spiral or substantially helical shape Since the length of the inner tube 204 is longer than that of the parallel-arranged inner tube 204, the spiral shape is advantageous for heat transfer. Increase the amount of surface area. The increased surface area provides additional area for heat transfer, Thus, increasing the efficiency of the heat exchanger 200. In addition, the spiral shape This can induce turbulence in the source water to improve heat transfer efficiency as described above. In this embodiment, the heat exchanger 200 has four inner tubes arranged in a spiral configuration, as shown in FIGS. 2H-I. It has a tube 204.

[0058] The overall length of the tube-in-tube heat exchanger 200 is determined by the desired efficiency of the device. A heat exchanger 200 having a longer length results in better efficiency. Exchanger 200 is approximately 50 feet long. This results in an efficiency of approximately 90%. As such, a length of 25 feet yields an efficiency of approximately 84%.

[0059] 2, 2J, and 2K, the heat exchanger assembly 200 also includes a heat exchanger. The interchanger 200 may include a connector 206 at either end. In the heat exchanger 200, two connectors are located at either end of the assembly. These connectors 206 along the outer pipe 202 have an internal cavity for containing source water. Additionally, a connector is attached to the end of the inner tube 204 to allow the product water and blowdown water to exchange heat. Provides separate fluid paths to enter and / or exit interchanger 200. Connector 2 06 is a diagram showing how the heat exchanger assembly is mechanically connected to the evaporator / condenser and other equipment components. In some embodiments, the water to the heat exchanger 200 can be removed or An extension 207 is included in the heat exchanger 200 to provide an additional port for supplying Good too.

[0060] 2L-O, these figures show three inner tubes passing through connector 208. 2 illustrates an alternative embodiment of the heat exchanger 200 having a connector 208 connecting the outer tube 2 At either end of the heat exchanger 200, an inner tube 02 is provided to contain the source water. 204 and the outer tube 202. The connector 208 and the inner tube 204 are sealed and attached. An O-ring may be placed within the connector 208 to seal the interface between the two. The seal allows the inner tube 204 to move freely and independently of the connector 208. Additionally, the inner tube 204 may be arranged in a spiral configuration as shown in FIG. 74-74C, another embodiment of a connector 7400 is shown, which is herein It may be used in any of the embodiments described above.

[0061] 2P-R, these figures illustrate an alternative embodiment of heat exchanger 210. In this embodiment, the heat exchanger 210 has a metal plate 212 and a plastic plate 214. The metal plate 212 is made of any metal material such as stainless steel. Other embodiments may include plates made of titanium or metal alloys, although these may The plastic plate 214 can be any type of plastic that can function. In one embodiment, the plate heat exchanger 210 is made of metal and plastic plates. In another embodiment, the metal plates 212 are made of alternating metals, as shown in FIG. , which may be followed by two or more plastic plates 214. The flat plate heat exchanger 210 The plate 216 may start and / or end with a plate 216 made of the same or different material. In alternative embodiments, the plate 216 may be made of metal or plastic material. 212 consists of two metal plates stacked together as shown in FIG. 2R, and is used for fluid flow. Form a channel.

[0062] Referring now to FIG. 3, an exemplary embodiment of a counterflow tube-in-tube heat exchanger 200 The water vapor distillation apparatus may include a fitting assembly 300. The fitting assembly may include a water vapor distillation apparatus 100. Additionally, the fitting assembly 300 supports the placement of the heat exchanger 200 within the This allows the exchanger 200 to be easily separated from the equipment for maintenance. The assembly is shown in FIG. 3 as a first connector 302 (also identified as connector 206 in FIG. 2). The fitting assembly 300 may comprise a first connector 310 and a second connector 310. See also Figures 3A-B for a plan view.

[0063] Still referring to FIG. 3, in the exemplary embodiment, fitting assembly 300 is made of brass. Materials including but not limited to stainless steel, plastic, copper, copper-nickel, or titanium Other materials may be used to manufacture the fitting assembly 300, including, but not limited to, For installation purposes, fitting assemblies made of similar material to the tubing to which they are attached shall be Similar materials can be attached to the assembly using soldering or welding techniques. The fitting assembly 300 allows the fitting assembly to be installed in a steam distillation apparatus. is preferably made of a material that is corrosion resistant and heat resistant (250°F). , preferably allowing a fluid-tight connection when the assembly is installed. For applications where the water is highly concentrated, such as seawater, the fitting assembly 300 may be made of copper-nickel Alternatively, it may be made of, but is not limited to, titanium.

[0064] Still referring to FIG. 3, the first connector 302 has a first end 304 and a second end 306. 6. The first end 304 is attached to the heat exchanger 200 as shown in FIG. The connector is secured to the exterior of the first end 304 of the connector 302 using a hose clamp. The outer tube 202 may be attached to the heat exchanger 200 by tightening the outer tube 202. The inner tube 204 of the exchanger 200 is also connected at a first end 304 to a connector 302. These tubes are soldered to the heat exchanger side of the connector 302. Other attachment methods include may include, but are not limited to, welding, press fitting, mechanical fastening, or insert molding. See also Figures 3A-3B for a cross-sectional view of fitting assembly 300.

[0065] Referring now to FIG. 3C, in this embodiment, the first end 304 of the connector 302 includes: It may have five ports, three of which are mutually fluidly connected as shown in Figures 3D-E. This configuration may combine multiple produced water streams into one stream. There is more product water in the heat exchanger to provide heat energy to multiple The product water flow increases the amount of heat transfer from the product water to the source water. The remaining ports are separate and Provides fluid paths for blowdown and source water as illustrated in Figures 3E-F. Alternative embodiments include: There may be no ports that are fluidly connected to each other.

[0066] Still referring to FIG. 3C, connector 302 is adapted to mate with a second connector 310. The second end 306 has three ports for product water, source water, and , and may provide a path for blowdown water. The product flow path may include an extension 308. The extension 308 is positioned within the body of the second connector 310 rather than on the mating surface 310. To allow for a groove, extension 308 is provided to assemble connectors 302 and 310 together. By having an O-ring groove within the body of the second connector 310, The flow paths through the connector assembly are arranged adjacent to each other without overlapping sealing areas. This allows it to be done.

[0067] 3G-H, a second connector 310 includes a first end 312 and a second end 313. The first end 312 includes a first connector 302 and a second connector 314. The first end 312 mates with the first connector 302 as shown in FIG. This end may also include an extension 316 as shown in FIG. 3G. 16, the O-ring groove is located on the first connector 302 rather than in the surface of the end 306 of the first connector 302. In addition, the connector has a first end that can be positioned within the body of the connector 302. 312 may have a leak path 318. This path allows source water or effluent water to enter the production stream. The product water port is located around the product water port to prevent the ingress of the product water. may contain contaminants that affect the quality and safety of the produced water. Inlet and source water enters the product stream through drainage section 320, shown in Figures 3G-I. In addition to the drain 320, the exemplary embodiment The configuration may include three independent fluid paths within connector 310, as illustrated in Figures 3I-J. stomach.

[0068] The first connector 302 uses a Marmon clamp to allow for the use of the device. This type of clamp may be used to assemble the second connector 310. Provides easy connection separation / reassembly and provides additional strength and ease of assembly. The method includes steps using C-clamps or fasteners (i.e., bolts and nuts). In addition, the circumference of connectors 302 and 310 may be 3E-F and 3I-J to receive a clamp during installation of tool assembly 300. In other embodiments, the fitting assembly 300 may be tapered. The connectors may be permanently joined by welding or soldering them together. Evaporator / Condenser) Referring now to FIG. 4-4B, an evaporator-condenser (hereinafter, "evaporator / condenser" The exemplary embodiment of the assembly 400 (also referred to as an evaporator) includes a top and a bottom. The condenser chamber 402 may comprise a shell 410 and an upper tube The lower tube plate 412 may include a plate 414 and a lower tube plate 412. The lower tube plate 412 may include a plate 414 for retaining the incoming source water. Similarly, the upper tube plate 414 is provided with an upper flange 416. 06 is attached to the evaporator / condenser chamber 402. This flange connects the steam chamber 408 to the evaporator / condenser chamber 402. Within the evaporator / condenser chamber 402 are a plurality of rods 416, each of which is connected to a 4A and 4B, the water is surrounded by a pipe 418. The pipe 418 is connected to the water reservoir 4 04 and the top flange 406. See also FIG. 4C, which illustrates an alternative embodiment.

[0069] Referring now to FIG. 5, sump assembly 500 (also identified as 404 in FIG. 4) The heater includes an upper housing 502, a lower housing 504, a drain pipe fitting 506, a drain pipe 508, and a heating element. 5A for an exploded view of the basin assembly 500 and the upper casing 510. See also Figure 6 for a detailed view of the body 502. The water reservoir assembly 500 contains the source water. The source water is evaporated from the fluid and heated, and particulates carried by the source water are collected. Upon changing state to gas, the particulates are left behind and collected in the reservoir assembly 500 .

[0070] Still referring to FIG. 5-5A, the sump assembly 500 is corrosion and high temperature resistant. The reservoir may be constructed from materials suitable for use in water tanks because of exposure to high temperatures, humidity, and corrosive source water. Corrosion-resistant materials are preferred. In an exemplary embodiment, the sump is made of stainless steel. In an embodiment, the water reservoir, along with alternative configurations for mounting the heating element 510, may be L® or other high temperature plastics. For applications where the water reservoir assembly 500 may be made of titanium, copper, nickel, It may be made of, but is not limited to, naval brass or high temperature plastic.

[0071] Still referring to FIG. 5-5A, the source water is heated using the heating element 510 of the basin assembly 500. The heating element 510 may be heated using a source water heater during the initial start-up of the water vapor distillation apparatus 100. This element provides additional heat energy to vaporize the source water from a fluid. In the exemplary embodiment, the heating element 510 is 120 volts / 1200 watts. It may also be a resistor-type electric heater.

[0072] Still referring to FIG. 5-5A, the basin assembly 500 is configured to aid in the collection of particulates. The bottom housing 504 may include a bottom housing 504 having an angled bottom surface. The angle may be any angle sufficient to collect the radiation in one area of ​​the housing. In one embodiment, the bottom housing 504 has a bottom surface angled at 17 degrees. 04 may have a flat bottom.

[0073] Still referring to FIG. 5-5A, the exemplary embodiment includes a drain fitting 506 and a drain. The drain assembly may include a drain pipe assembly consisting of a pipe 508. The drain pipe assembly may include a drain pipe assembly. Provides access to the inside of the condenser evaporator to remove particulate buildup without the need to disassemble the unit. The drain assembly removes debris (accumulation of particulate matter) from the inner tubes of the evaporator / condenser. The debris may be located near the bottom of the basin to reduce debris buildup within the basin assembly 500. This is prevented by allowing the scale to be removed periodically. Fewer particles reduces the chance of particles getting into the evaporator / condenser tubes. In an embodiment, the drain assembly receives particulates from the angled underside of the bottom housing 504. The drain assembly may be attached to the bottom housing 504 and is resistant to It may be made of any material that is food and heat resistant. The fitting 506 is a flange-shaped sanitary fitting made of stainless steel. 3, the fluid path of the sump drain 7302 is shown. In some embodiments, The fluid path of the sump drain 7302 is provided to facilitate cleaning or flushing of the device 100. In some embodiments, the fluid path of the sump drain 7302 can be, for example, For example, the seal may be from the ambient environment by a valve, but the seal is not limited to a valve. In an embodiment, the valve may not be a manual valve, but may be, for example, a differential valve controlled by a control system. In some embodiments, cleaning and flushing may be at least partially automated. You may do so.

[0074] Still referring to FIG. 5-5A, drain fitting 506 has drain pipe 508 attached thereto. The drain 508 may be used to prevent particulates from flowing from the drain fitting 506 to the evaporator / condenser assembly. The drain 508 provides a fluid path for movement out of the assembly 400. The material of the drain 508 is corrosion resistant. and heat resistant and capable of being attached to the drain fitting 506. It may be made of any suitable material. In the exemplary embodiment, the drain pipe 508 is made of stainless steel. The diameter of the drain pipe 508 is preferably 1 / 4" to 1 / 4" wide, allowing for a finer flow from the sump assembly 500. Sufficient to allow removal of particles. A larger diameter pipe is desirable because it is less likely that the drain 508 will become clogged with particles. It's nice.

[0075] Referring now to FIG. 7, an evaporator / condenser chamber 700 (also identified as 402 in FIG. 4) An exemplary embodiment of the shell 702 (also identified as 410 in FIGS. 4A-B) is shown. ), a lower flange 704 (also identified as 502 in FIG. 5 and 600 in FIG. 6 ), and a lower A tube sheet 706 (also identified as 412 in FIGS. 4A-B), a plurality of tie rods 708, and a plurality of 4A-B) and an upper flange 712 (also identified as 418 in FIG. 4). 06) and upper tube plate 714 (also identified as 414 in Figures 4A-B) See also FIG. 7A for an assembly view of the evaporator / condenser chamber 700. I want to be.

[0076] Still referring to FIG. 7, the shell 702 is a structure for transferring heat energy from high pressure steam to source water. This heat transfer assists in the phase change of the source water from a liquid to a vapor. In addition, heat transfer also condenses the incoming steam into product water. It may be made of any material that has the necessary corrosion and strength properties. The structure 702 is fabricated from fiberglass. The shell is large enough to contain the desired number of tubes 710. Within the internal cavity of the shell is a high pressure steam source which enters the chamber. A plurality of tubes 71 having a surface area for transferring thermal energy from the air to the source water within the tubes 710. There is 0.

[0077] Still referring to FIG. 7, the evaporator / condenser chamber 700 is a condenser for condensing high pressure steam. The tubes define an internal cavity within which high pressure steam is released as the steam condenses on the exterior surfaces of the tubes. There are a plurality of tubes 710 that transfer thermal energy from the source water to the tubes. "Method and d Apparatus for Phase Change Enhancement As described in U.S. Patent Application Publication No. 2005 / 0183832A1, entitled Heat transfer through the tube walls causes the source water to undergo a phase change through a process called thin-film evaporation. .

[0078] Still referring to FIG. 7, within the evaporator / condenser tube 710, the inner surface of the tube 710 is in contact with the Taylor bubbles may be developed, having an outer surface including a thin film that is oriented along the Taylor axis. As the bubbles rise up the tube, they heat up, causing the fluid in the thin film to transform into a vapor within the bubbles.

[0079] Referring now to FIG. 7B, typically, evaporators operate in pool boiling mode or thin film mode. In thin film boiling, a thin film of fluid boils over the tube. The heat transfer efficiency of the phase change is typically Typically, it increases in thin film mode compared to pool boiling mode. As a function of condenser pressure for pool boiling and thin film boiling under similar conditions for the condenser, The bottom curve 70 corresponds to pool boiling, while the middle curve 71 corresponds to distillate production flow rate. The middle curve 75 corresponds to thin film boiling. As can be seen from these two curves, the thin film boiling mode The thin film boiling mode offers significantly higher efficiency than the pool boiling mode. , which is more difficult to maintain than pool boiling. Thin film evaporation is typically very small. This is accomplished using a device that includes an opening. This device is particularly useful for detecting if the source fluid contains contaminants. In addition, in the thin film mode, the water level is typically The fuel is supported marginally above the top of the tubes in the tubular evaporator. The device may also be sensitive to movement and positioning of the device.

[0080] Referring again to FIG. 7, in the exemplary embodiment, the tube 710 has an outer diameter of 0.75 inches. In an alternative embodiment, the tube 710 may be made of nickel copper or other composite material. It may also be made of other materials, including but not limited to aluminum. , the diameter of the tube may be different, i.e., smaller or larger. For possible applications where the water may be seawater, the tube 710 may be made of copper nickel or titanium. These materials may be used to reduce the strength of the pipe when exposed to high concentrations of source water, such as saline water. It has high corrosion resistance so as to maintain its heat transfer properties. The diameter of the tube 710 is also subject to many variables. The diameter of the tubes 710 may vary depending on the inner diameter of the shell 702 and the desired amount of heat transfer. Another constraint may be availability. The smaller diameter limits access to the inner surface of the wall, making it difficult to remove flakes from it. The length of the tube 710 is determined by the thickness of the shell 702 and the tubesheets 706 and 714. In an exemplary embodiment, the length of the internal cavity is determined by the thickness of the internal cavity. , tube 710 extends beyond the edge of the tube sheet into lower flange 704 and upper flange 712 You may do so.

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

[0082] Referring now to FIG. 9, the improved efficiency of the phase change operation is achieved by increasing the temperature within the evaporator / condenser tube 904. This may be achieved by providing a filler. The introduction of such a filler may involve the use of a fluid, a filler The interaction between the fill and the tube 904 causes the evaporator to exhibit some of the thin film mode characteristics. The filling may be such that the material preferentially fills the volume near the inner wall of the tube and In contrast, any shaped material may be used to fill the volume of the tube 904 near the tube's longitudinal axis. Such packing material may be used to direct steam near the tube walls for efficient heat exchange. For example, in the exemplary embodiment, the packing may comprise rods 902. Each rod 902 may be of any cross-sectional shape, including cylindrical or rectangular. The cross-sectional area of ​​the rods 902 may be any area that fits within the cross section of the tube. The area may vary along the length of the rod. A given rod 902 may have a given evaporator tube 904 or The rod material is hydrophobic and can withstand repeated thermal cycling. In an exemplary embodiment, the rod 902 is filled with glass fiber. Manufactured from RYTON® or glass-filled polypropylene.

[0083] Still referring to FIG. 9, each rod 902 is positioned within a tube 904, preferentially including the upper portion of the tube. In one specific embodiment, each rod may be positioned approximately half the length of the associated tube. and is located approximately in the top half of the tube. The top curve 80 in FIG. 7B indicates that the evaporator tube is located at the top of the tube. The increase in boiling efficiency for thin film boiling is shown for a representative evaporator containing half the packing material. With such packing, the phase change efficiency also varies depending on the fluid level above the tube, the tube relative to the vertical, Advantageously, the tube orientation, the supply pressure to the tube, and other operating parameters of the evaporator are varied. In the exemplary embodiment, the rod 902 has approximately the same length as the tube 904.

[0084] Referring now to FIG. 9A, in an exemplary embodiment, the rod 902 has a plurality of ribs extending from the center of the rod 902 to the outside. The rod 902 may have a plurality of members 906 extending along the longitudinal axis of the rod 902. Member 906 maintains rod 902 in the center of tube 904 to create the most efficient flow path for the source water. Any number of members may be used, but it is preferred to use a member that maintains the rod 902 in the center of the tube 904. In an alternative embodiment, rod 902 does not have members 906. In an alternative embodiment, the rod 902 may be a wire or a cross borehole within the rod 902. By wrapping the rod 902 in the tube 904, it is held in place within the tube 904. This may assist in the placement of pins that position the rod 902.

[0085] Referring again to FIG. 7, tube 710 (also identified as 800 in FIG. 8 and 904 in FIG. 9) The tubes (706 and 714) are held in place by a pair of tube plates 706 and 714. Rods 708 are used to secure the shell 702 to each end. The tubesheets 706 and 714 are It has a number of openings that provide a path for source water to enter and exit the pipe 710. When tube 710 is installed in chamber 700, the openings in tube sheets 706 and 714 allow for the passage of tube 710 The lower tube plate 706 (also identified as 1002 in FIG. 10) receives the end of the shell 7 Attached to the bottom of the upper tube. See Figure 10 for a detailed view of the lower tube plate. Plate 714 (also identified as 1004 in FIG. 10A) is attached to the top of shell 702. For a detailed view of the upper tube plate, see FIG. 10A. Both tubesheets have similar dimensions, except for an additional opening located in the center of the tubesheet. This opening provides an opening for high pressure steam to enter the evaporator / condenser chamber 700. To provide.

[0086] Still referring to FIG. 7, in the exemplary embodiment, the upper tube sheet 714 and the lower tube sheet 706 are: This material may be manufactured with RADEL®, which has low creep, hydrolytic stability, It has thermal stability and low thermal conductivity. Furthermore, tubes made from RADEL® The plate may be formed by machining or injection molding. In an alternative embodiment, the tube sheet is It may also be made from other materials, including but not limited to G10.

[0087] Still referring to FIG. 7, a plurality of tubes 710 are provided in tubesheets 706 and 714 for receiving the tubes 710. The size of the openings is determined by the outer diameter of the tube 710. These openings receive the ends of the tube 710. It must be sufficient to contain the seal. Typically, it will receive an O-ring. An O-ring groove is provided in the tube sheet to secure the inner tube 710 to the tube sheet 706. and 714. This type of seal also simplifies the construction. , facilitating the use of dissimilar materials within the evaporator / condenser, and ensuring that the tube 710 remains stable during repeated thermal cycles. This seal prevents product water from entering the sump 500 of FIG. , or source water from entering chamber 700. In an alternative embodiment, tube 710 Depending on the tubesheet material, the seal may be soldered, welded, press-fit, or glued (i.e., silicone, RTV) , epoxy, brazing, or swaging, but are not limited to The tube sheets 706 and 714 may be installed within the openings in the tube sheets 706 and 714 by using a method.

[0088] Referring now to FIG. 10, in an exemplary embodiment, O-ring grooves are provided in the tubesheet 1 at various depths. Located in 002 and 1004. O-ring grooves from adjacent tubes do not overlap each other Therefore, the different depths of the O-ring grooves allow the tubes 710 to be positioned closer together. Overlapping O-ring grooves do not provide an adequate seal, so each O-ring groove must Must be independent of other O-ring grooves in the tubesheet. As a result of varying the location of the O-ring grooves, adjacent O-ring grooves do not overlap each other and the tube This allows the tubes to be positioned closer together. 710 allows more tubes to be placed within the evaporator / condenser chamber 700. This makes it possible to

[0089] Referring again to FIG. 7, tubesheets 706 and 714 are also connected to the bottom using connecting rods 708. The lower flange 704 (502 in FIG. 5) is fixed to the upper flange 712. 6) converts the sump 500 of FIG. 5 into the evaporator / condenser of FIG. 7. In addition, a lower flange 704 is disposed on a lower tube plate 706. The lower flange 704 provides a fluid connection for the ingredients in the basin to the inlet of the pipe 710. is sufficient to allow for even distribution of source water entering pipe 710, It can be any height. Typically, a flange with a height of 1 to 2 inches is used to secure the pipe 7 10. In an alternative embodiment, the height of the flange is It may be larger to increase the collecting capacity of the basin.

[0090] Still referring to FIG. 7, upper flange 712 (also identified as 1100 in FIG. 11) 4. In addition, the upper flange 714 provides a fluid connection between the outlet of the tube 710 and the steam chest 408 of FIG. The transformer 712 converts source water removed from the low pressure steam as the steam passes through the steam chamber 408. This water is then discharged through a discharge port located in the side of the upper flange 1100 of FIG. The liquid is transported out of the device through port 1102.

[0091] Still referring to FIG. 7, the lower flange 704 and the upper flange 712 have sufficient structural strength. It may be made of any material that has the strength and corrosion and heat resistance. The flange may be manufactured from RADEL®. In an exemplary embodiment, the flange The lower flange may be made of nickel-plated aluminum. The range is made of materials including, but not limited to, stainless steel, titanium, and copper-nickel. It may also be manufactured by

[0092] Referring to FIG. 7-7A, near the outer edges of the lower flange 704 and the upper flange 712, A number of openings are located to receive connecting rods 708. These rods are concentric with the shell 702. Located longitudinally on the bolt circle and along the periphery of the shell 702. The length of the shell 702, as well as the length of the lower tube plate 706, the lower flange 704, the upper flange The thickness of the connecting rod 708 is determined by the thickness of the tube 712 and the upper tube sheet 714. The connecting rod 708 has a screw on each end of the rod. It has threaded ends for mounting screw-type fasteners and holds the evaporator / condenser components together. Additionally, the connecting rod 708 may be made of a material strong enough for the purpose, such as stainless steel. The connecting rod 708 may be made of any material suitable for this purpose. The material may also be made of other materials, including but not limited to carbon steel. In one embodiment, the connecting rod 708 is adapted to receive a device that holds the rod in place during installation. The axially extending portion may have flats machined near each end to provide a flat surface.

[0093] 12-12C, upper flange 1100 (also identified as 712 in FIG. 7) ) may be connected to a steam chamber 1200 (also identified as 408 in FIG. 4 ). In the exemplary embodiment, the steam chest 1200 includes a base 1202 and a steam separator assembly 12 1204, a cap 1206, and a vapor tube 1208. The base 1202 to receive the low pressure steam generated within the tubes 710 in the evaporator region of the evaporator / condenser chamber 700. The base 1202 defines an internal cavity that allows water droplets contained within the steam to separate. The steam chamber may have any height so long as there is sufficient space for the steam to function. Water carried by the air and forced out of the outlet of the tube 710 by the rapid release of steam bubbles The droplet slows down and retreats toward the upper flange 712 (also identified as 1100 in FIG. 11). This makes it possible to do so.

[0094] Still referring to FIGS. 12-12C, within the base 1202 is a steam separator assembly 12 04. This assembly may include a basket and net (not shown in Figures 12-12C). The basket contains a quantity of wire mesh. In an exemplary embodiment, the steam separator assembly Assembly 1204 converts incoming low pressure steam into a steam generator by manipulating the steam through a layer of wire mesh. Remove water droplets. As the steam passes through the mesh, water droplets begin to collect on the surface of the mesh. These droplets may contain contaminants or particulates. As the droplets increase in size, As the water falls to the bottom of the basket, it allows the water to collect within the upper flange 712. A plurality of openings may be located at the bottom of the basket so that the openings , providing a fluid path for low pressure steam to enter the steam separator assembly 1204. Therefore, the wire mesh is located within the top flange 712 of the evaporator / condenser to provide an obstacle from splashing out water. Provide a wall.

[0095] Still referring to FIGS. 12-12C, in an alternative embodiment, a steam separator assembly 120 4 collects water droplets from low-pressure steam as the steam passes through or around each plate. The plate may contain a series of plates for manipulating the steam to cause water droplets to collect on the plate. The plates are positioned to create a sharp bend in the steam flow path, allowing water to collect in the assembly. These bends reduce the velocity of the steam and change its direction. The droplets may then continue along their initial trajectory. The water may be allowed to hit the wall or plate of the assembly. If sufficient water droplets collect on the wall or plate of the assembly, When the water droplets reach the evaporator / condenser, they may fall towards the top flange 406 of the evaporator / condenser.

[0096] Still referring to FIGS. 12-12C, the base 1202 may also include an observation window 1210. This window allows the person operating the equipment to visually observe the interior of the steam chamber and ensure that the equipment is operating properly. In another embodiment, the steam chamber 120 may be configured to determine whether the steam chamber 120 is functioning properly. The optical fiber 1200 may not include an observation window 1210. This alternative embodiment is illustrated in FIG. 12D. In still other embodiments, the size and shape of the window may vary. Alternatively, the steam chamber may include multiple windows.

[0097] In an exemplary embodiment, the steam separator assembly may be fabricated from stainless steel. However, other materials are used due to their corrosion resistance and high temperature resistance. Other types of materials include RADEL®, titanium, copper nickel, and plating. Materials may include, but are not limited to, coated aluminum, fiber composites, and high temperature plastics. Not limited.

[0098] Still referring to Figures 12-12C, attached to base 1202 is cap 1202. 206. The cap and base define an internal cavity for separating water from low pressure steam. In addition, the cap 1206 may be configured to have a cap 1206 that is detachable from the outlet 1204 shown in FIGS. 12B, 12E, and 12F. It may have two ports: port 1211 and inlet port 1212. The port provides a fluid path for dry low pressure steam to exit the steam chest 1200. In an embodiment, by locating the port away from the exit of the evaporator / condenser tube 710, To promote drier vapor, the outlet port 1211 is located on the top surface of the cap 1206. However, in an alternative embodiment, the outlet port 1211 is located near the cap 1. 206. Similarly, the inlet port 1212 is configured to allow high pressure steam to enter the steam It provides a fluid path for entry into the high pressure steam line 1208 within the chamber 1200. In this embodiment, the inlet port 1212 is located near the top surface of the cap 1206. In some embodiments, the inlet port 1212 may have a different location within the cap 1206. In a preferred embodiment, the cap 1206 is made of plated aluminum. Materials of this type may include stainless steel, plastic, titanium, and copper-nickel. The size of these ports affects the pressure drop across the compressor. Sometimes this happens.

[0099] Still referring to Figures 12-12C, an inlet port 1212 in the steam chamber 1200 is The trachea 1208 is connected to the steam chamber. This tube carries high pressure steam through the steam chamber and into the evaporator / condenser chamber. The inner diameter of the steam pipe 1208 provides a fluid path for the steam to enter the condenser of the cylinder. Any suitable means should be used to avoid adversely affecting the flow of high pressure steam from the blower to the evaporator / condenser chamber. In the exemplary embodiment, the steam pipe 1208 is made of stainless steel. Other materials may be used to manufacture the steam pipe 1208, but these The material must have sufficient corrosion resistance and high temperature resistance. These may include burnished aluminum, plastic, titanium, and copper-nickel, For applications where the source water may be highly concentrated, such as seawater, the steam chamber 1 200 may be made from titanium, nickel, bronze, nickel-copper, and copper-nickel. , but not limited to.

[0100] 13-13C, an alternative embodiment of an evaporator / condenser assembly 1300 In this embodiment, the evaporator / condenser assembly 1300 includes a water reservoir 13 02, an evaporator / condenser chamber 1304, a mist eliminator assembly 1306, and multiple The connecting rod 1308 includes a lower flange 1310 and an upper flange 1312. For a detailed view of the evaporator / condenser assembly without 2, see FIG. 13D.

[0101] Referring now to FIG. 13E, the evaporator / condenser chamber comprises a shell 1314 and a plurality of The evaporator / condenser includes a pipe 1316, a lower flange 1310, and an upper flange 1312. Chamber 1304 defines an interior cavity for condensation of high pressure steam. When condensed on the exterior surface of the tube 1316, it transfers heat energy from the high-pressure steam to the source water within the tube. In this embodiment, the tube 1316 has an outer diameter of 0.75 inches and may be made of copper. In alternative embodiments, the tube 1316 may include, but is not limited to, nickel copper or other composite materials. The diameter of the tube 1316 may also vary depending on many variables. May vary. See previous discussion in exemplary embodiments regarding tube diameter. The length of the tube 1316 is determined by the shell 1314 and the bottom flange 1310 and top flange 1312. This may be determined by the length of the cavity defined by the thickness of 312.

[0102] Still referring to FIG. 13E, tube 1316 is shown in FIGS. 13B, 13C, and 13E. The outer shell 1314 is formed by a lower flange 1310 and an upper flange 1312. Each flange is supported within an internal cavity defined by a flange axially extending about the center of the flange. These openings may contain the ends of the tubes 1316. Additionally, the bottom flange 1310 and top flange 1312 also hold the shell 1314 in place. and provides a path to the water reservoir 1302 and mist eliminator assembly 1306. As the water fills the reservoir 1302, some water is drawn into the interior cavity of the shell 1314. The heat energy is transferred to the source water in the tube 1316. As the water vapor rises, it begins to evaporate. The source water vapor flows through pipe 1316 into the mist eliminator assembly. The steam travels into the nozzle 1306. The steam travels through openings located in the upper flange 1312 to form a mist. Enter the excluder.

[0103] Still referring to FIG. 13E, the shell 1314 is constructed using multiple connecting rods 1308. , are fixed to the lower flange 1310 and the upper flange 1312. These connecting rods are The connecting rod 1308 is also disposed axially outwardly around the outer periphery of the structure 1314. The mist eliminator 1306 is attached to the upper flange 1312, and the water reservoir 1302 is attached to the lower flange 131. The length of the connecting rod is determined by the length of the shell 1314 and the length of the bottom flange 1310. , determined by the thickness of the upper flange 1312, the water reservoir 1302, and the mist eliminator 1306. The connecting rod 1308 has threaded ends for attaching threaded fasteners on each end of the rod. Alternatively, the evaporator / condenser components may be secured together. The connecting rod 1308 may be made of any material of sufficient strength, such as stainless steel. , titanium, fiberglass composites, and other materials including but not limited to carbon steel It may also be manufactured.

[0104] Still referring to FIG. 13E, in the exemplary embodiment, the shell 1314 is made of fiberglass. The material is corrosion resistant, has low thermal conductivity, and is and sufficient structural strength to withstand the internal pressures developed during operation. Materials may be used. Discussion of exemplary embodiments regarding the size of the inner diameter of the shell Please refer to the resolution.

[0105] Still referring to FIG. 13E, the sump 1302 is connected to a bottom flange 1310 and is used to The sump 1302 is in fluid communication with the tube 1316 of the condenser / water purifier assembly chamber 1304. The system collects incoming source water from the heat exchanger. The source water passes through an inlet port located in the side wall of the basin. In other embodiments, the inlet port is located in a different location (i.e., In this embodiment, the water reservoir 1302 is made of G10 plastic. In other embodiments, the water reservoir 1302 is made of a composite material such as quartz. It may also be made of any other material that is resistant to high temperatures. Other materials include aluminum RA Including, but not limited to, DEL® and stainless steel. The system may also include a heating element to provide thermal energy to the source water. - helps the source water change from a fluid to steam.

[0106] Referring now to Figures 14-14C, attached to the top flange 1312 is a The filter assembly 1400 (also identified as 1306 in FIG. 13) is a filter displacer assembly 1400. The assembly includes a cap 1402, a steam pipe 1404, and a mist pipe 1406, as shown in FIG. The cap 1402 may consist of a separator 1406. The cap 1402 may be formed from the evaporator of the evaporator / condenser. The cap 1402 contains the low pressure steam generated by the vaporizer. The nozzle may have three ports 1408, 1410, and 1412 for removing water droplets. See the discussion of the steam chest in the exemplary embodiment regarding volume height. The cap 1402 includes a mist eliminator 1406 shown in Figures 14, 14C, and 14D. The cavity includes a cavity having a cavity opening.

[0107] Still referring to FIGS. 14-14C, the first port 1408 is located on the top of the cap 1402. The steam pipe 1404 may be located in the center of the surface and is intended to receive a first end of the steam pipe 1404. This port is used to allow high pressure steam generated by the compressor to pass through the first port of the steam pipe 1404. The steam pipe 1404 allows the steam to re-enter the evaporator / condenser through the end. The high pressure steam is misted without mixing with the low pressure steam entering the mist eliminator assembly 1400. Provides a fluid path through the scavenger assembly 1400 and into the evaporator / condenser In this embodiment, the steam pipe 1404 is made of stainless steel. The steam pipes are made of plated aluminum, RADEL®, and copper-nickel The steam pipe 14 may be made of materials including, but not limited to, titanium. The length of 04 is sufficient to connect to the compressor and to run the entire mist eliminator assembly 1400. The second end of the steam pipe shall be sufficient to allow the steam to pass through the upper The steam pipe 1404 is received within a centrally located port of the pressure vessel 1312. Another effect on the system may be the pressure drop across the steam condenser. The nozzle 1404 reduces the effective volume within the mist eliminator, removing water droplets from the low-pressure steam. be.

[0108] Still referring to Figures 14-14C, the steam pipe 1404 also serves as a mist separator 140. The mist eliminator 1406 may have a plurality of external grooves for receiving the mist eliminator 1406. The openings allow low pressure steam to pass through the plate. In the steam pipe 1404, a number of mist separators are installed in the grooves. In addition, the plate closest to the exit port 1410 is oriented at 180° from the plate. The plate is oriented so that the opening is 180° from the port. The plate may include grooves on its upper surface to collect water droplets. allowing the mist to flow off the plate and fall towards the base of the mist eliminator assembly 1400 The mist separator 1406 may be tapered to a point where it is inclined. The steam pipe 1404 may be secured using a corrugated washer.

[0109] Still referring to FIGS. 14-14C, the second port 1410 also includes a cap 1402. and the dry low pressure steam exits the mist eliminator assembly 1400. See for example embodiments regarding the size and location of the exit port. , see previous discussion.

[0110] Still referring to FIGS. 14-14C, a third port 1412 is provided in the sidewall of the cap 1402. This port may be located within the device to allow water removed from the low pressure steam to exit the device. The location of the port is preferably such that it does not allow excess buildup of blow-off water within the assembly. The height is such that the discharge water can exit the mist eliminator assembly 1400 without The height of the port should not be too low, but should be high enough to cover the outlet of the tube. In the exemplary embodiment, the tube is connected to port 1412. The blowdown water may be connected to the level sensor housing 108 and The heat exchanger 102 may also pass through the heat exchanger 102 .

[0111] Still referring to FIGS. 14-14C, the mist eliminator assembly 1400 is substantially corrosion resistant. It may be made of any material that is durable and can withstand high temperatures. The assembly is manufactured from stainless steel. Manufactured from other materials including but not limited to stainless steel, titanium, and copper-nickel You may do so. (Compressor) The water vapor distillation apparatus 100 may include a compressor 106. In an exemplary embodiment, the compressor is a regenerative blower. For the purposes of this application, a regenerative compressor is used, although other types of compressors may be implemented. A regenerative blower is shown and described with respect to an exemplary embodiment. , compressing low-pressure steam exiting the evaporator section of the evaporator / condenser to produce high-pressure steam; Increasing the steam pressure increases the steam temperature. Condensation on the tubes in the condenser section transfers heat energy to the incoming source water, so that this temperature The heat energy transferred from the high pressure steam is used to supply the low pressure steam to the regenerative blower. This heat transfer is important because

[0112] The change in pressure between the low pressure steam and the high pressure steam is determined by the desired output of product water. The output of the evaporator / condenser is related to the flow rate of high pressure steam. If the steam flow rate is greater than the condenser's capacity to accept the steam, the steam will be superheated. Conversely, if the evaporator side of the evaporator / condenser produces more vapor than the compressor can compress, When this occurs, the condenser side of the evaporator / condenser is confined by the limited flow rate of high pressure steam from the compressor. may not operate to its full potential.

[0113] 15-15G, an exemplary embodiment provides a condenser / evaporator section. The system may include a regenerative blower assembly 1500 for compressing low pressure vapor from the The power supply assembly 1500 includes an upper housing 1502 that defines an interior cavity, as shown in FIG. 15C. 15. The upper and lower housings 1502 and 1504 are shown in detail in FIG. See Figures 15D-G for details. Located within the internal cavity is an impeller assembly 1506. (registered trademark), ULTEM (registered trademark), or polysulfone, but various plastics Alternatively, the housing may be made of titanium, copper nickel, and aluminum. It may be made of materials including, but not limited to, nickel bronze. In an alternative embodiment, the upper and lower housings 1502 and 1504 are made of aluminum. The material must be selected to be resistant to high temperatures and corrosion, not absorb water, and have sufficient structural strength. Other materials may be used if desired. The housing preferably includes an impeller assembly and The housing is preferably of sufficient size to accommodate the casing and associated internal passages. Provide sufficient clearance between the housing and the rotating impeller to avoid sliding contact and to prevent leakage from In addition to the gap, the upper housing 1502 and the lower housing 1503 are 504 may be mirror images of each other.

[0114] 15D-F, upper and lower housings 1502 and 1504 are shown with an inlet port. The low pressure vapor from the evaporator / condenser may have an inlet 1510 and an outlet port 1512. , enters blower assembly 1500 through inlet port 1510. In the exemplary embodiment, In this example, the inlet ports are arranged around the periphery of the annular flow channel in the upper and lower housings 1502 and 1504. After compressing the low pressure steam, the high pressure steam exits the outlet port 15. 12. The inlet port 1510 and the outlet port 1512 of the upper housing 1502 and the lower housing 1504 Between port 1512 and the assembly, high pressure steam exits the blower assembly. The gap is reduced to prevent mixing of the incoming low pressure steam. The upper housing 1502 and the lower housing 1504 may include an upper plate 1516. The open flow channels provided in 4 allow only the high pressure steam within the impeller blades to pass through the inlet region. 15. The inlet port 1510 allows the air to pass through a region near the inlet port 1510 called the inlet region.

[0115] Still referring to Figures 15D-F, the stripper plate 1516 is inserted into the entrance area. High pressure steam carryover occurs as the flow enters the blower assembly 1500 through the inlet port 1510. The steam may be irreversibly mixed with the incoming low-pressure steam. Mixing of the steam causes an increase in the temperature of the incoming low-pressure steam. High pressure steam carryover may also occur due to the expansion of high pressure steam in the inlet region. The inflow of pressurized steam may be blocked. 514 extracts the compressed steam trapped in the impeller blades and releases the steam into the inlet region. This may be used to block incoming low pressure steam.

[0116] Still referring to FIGS. 15D-F, between the inlet port 1510 and the outlet port 1512 The distance is controlled by the size of the stripper plate 1516. In an exemplary embodiment, The tripper plate area reduces the amount of high pressure steam carryover into the inlet area and allows the upper enclosure 1502 and optimized to maximize the working flow channels within the lower housing 1504.

[0117] 15H-K, in an exemplary embodiment, the shaft 1514 is Pressurized water supply bearing 1516 pressed into assembly 1506 and supported by shaft 1514 In this embodiment, the bearing may be made of graphite. Alternative Embodiment In the It may also be manufactured by

[0118] Still referring to FIGS. 15H-K, water enters the compression chamber of the blower assembly 1500. When it is permitted to enter, the water supplied to the pressurized water supply bearing 1516 is preferably clean water. When water enters the compression chamber, it will likely mix with pure steam. The mixing of contaminated water results in contaminated high pressure steam. In an exemplary embodiment, the product water is supplied to the bearings. will be done.

[0119] Hydrodynamic lubrication is desired for the high speed blower bearing 1516 of the exemplary embodiment. In dynamic operation, the rotating bearing rides on a film of lubricant and does not contact the stationary shaft. This mode offers the lowest coefficient of friction and, since there is no physical contact of the components, wear is essentially Does not exist.

[0120] Operation in other lubrication regimes, such as mixed film lubrication and boundary lubrication, is more sensitive than hydrodynamic operation. In an exemplary embodiment, the blower uses a fluid power The bearing may operate with chemical lubrication, film lubrication, or a combination of both. The operating clearance between the bearing and the bearing, the rotational speed of the bearing, and the lubricating fluid pressure and flow are This may affect the

[0121] Referring now to Figures 15H-K, in hydrodynamic bearings, the limiting load rate is determined by the heat dissipation capacity. Compared to non-lubricated (or boundary lubricated) bearings, hydrodynamic bearings: It has an additional mechanism for dissipating heat. This is the most effective way for hydrodynamic bearings to dissipate heat. The purpose of the lubricating fluid is to allow the lubricating fluid to carry away heat energy. In this embodiment, the bearing supply water removes heat energy from the bearing 1516. The volume of water flowing through the bearing should preferably be sufficient to maintain the bearing temperature within operating limits. Additionally, the diametric clearance may be varied to control the flow rate of the bearing feed water. Preferably, these gaps are not so large as to create hydrodynamic pressure losses.

[0122] Still referring to Figures 15H-K, the amount of bearing feed water supplied to bearing 1516 is preferably Preferably, the amount of water supplied to the bearings is sufficient to maintain hydrodynamic lubrication. For example, excess water can quench high-pressure steam and cause Another negative effect of excessive bearing water supply is that it can unnecessarily reduce the thermal efficiency of the equipment. This allows excess bearing feed water to be expelled outward from the impeller assembly, hitting the housing wall and the passing impeller. The shear of the water as it is forced between the rub blades can cause a loss of power.

[0123] Referring to FIG. 15L, in an exemplary embodiment, excess bearing feed water is pumped into the impeller buckets. A return path 1526 for bearing supply water is provided within the blower to prevent ingress .

[0124] Referring again to Figures 15H-K, in an exemplary embodiment, the bearing feed pump is connected to a pressurized water supply. Maintain a pressure of 2 to 5 psi for the input to the bearing 1516. The flow rate of the bearing supply water is This may be maintained by having a constant bearing supply water pressure. The pressure of the bearing supply water is controlled to ensure a flow rate of the bearing supply water to the bearing 1516. good.

[0125] Still referring to FIGS. 15H-K, in an exemplary embodiment, the impeller assembly The mechanical seal may be driven by a motor using a magnetic drive linkage rather than a mechanical seal. The lack of a mechanical seal eliminates the friction losses associated with moving parts contacting each other. In this configuration, the magnetic drive coupling includes an inner rotor magnet 1518, a containment shell 1520, and an outer It may include a side magnet 1522 and a drive motor 1508 .

[0126] Still referring to Figures 15H-K, an inner magnet rotor 1518 is embedded within the cup. In an exemplary embodiment, the magnets are arranged axially. The directions may be radially arranged. The cup may be made of plastic or metal material. In some embodiments, the cup material is RYTON®, ULT The polymer may be, but is not limited to, EM®, or polysulfone. In addition, magnets are made of ferrite, aluminum-nickel-cobalt, samarium-cobalt, and The electrodes may be fabricated from materials including, but not limited to, neodymium iron boron and neodymium iron boron. In an embodiment, the cup is attached to the impeller assembly 1500. In this example, the cup is press fit onto the stem 1514. Another method of attaching the cup is to use a spring. These may include, but are not limited to, lines and set screws.

[0127] Still referring to FIGS. 15H-K, the magnetic coupling shell 1520 connects the inner rotor magnet 15 18 and the outer rotor magnet 1522. The magnetic coupling shell 1520 is A containment shell for a vessel or blower assembly 1500. The shell The steam compressed within the assembly 1500 is sealed to prevent the steam from leaking into the surrounding environment. Prevent this.

[0128] 15H-K, a shell 1520 is shown with an inner rotor magnet 1518 and an outer Since it is located between the rotor magnet 1522, eddy current loss may occur. If 1520 is conductive, the rotating magnetic field will cause a current to flow through the shell, generating power. Conversely, to reduce the amount of eddy current loss, a high electrical resistance is required. Preferably, the shell 1520 is made of a compliant material. Titanium may be used to manufacture 1520. This material has high electrical resistance and provides a combination of excellent bearing and corrosion resistance. In other embodiments, the shell 1520 may have a higher electrical resistance. These alternative embodiments may be made of a plastic material that is resistant to corrosion. The shell 1520 is made of RYTON®, ULTEM®, or polysilicon. The hose may be made of materials including, but not limited to, PET, and PEEK.

[0129] Still referring to FIGS. 15H-K, the outer rotor magnet 1522 is attached to the drive motor 1508. This motor rotates the outer rotor magnet 1522 and the inner rotor magnet The impeller assembly 1506 is rotated to fit into the upper and lower housings 1502 and 1504. This allows for the compression of low pressure steam within the defined cavity. The drive motor may be an electric motor. In an alternative embodiment, the drive is an internal combustion or spark plug. The engine may be, but is not limited to, a ring engine.

[0130] Still referring to Figures 15H-K, the blower assembly 1500 may comprise two single-stage blowers or It may be configured as a two-stage blower. In two single-stage blower operation, the evaporator / condenser The incoming low pressure steam from the evaporator side of the blower is simultaneously introduced into both inlet ports of two separate stages of the blower. The first stage is located at the bottom between the lower housing 1504 and the impeller assembly 1506. 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 inlet ports of both stages The inflowing low pressure steam from 1510 is simultaneously compressed, and the high pressure steam is released from the outlet port of the upper housing 1502. The air exits through outlet 1512 and outlet port 1512 of bottom housing 1504 .

[0131] Also referring to Figures 15H-K, in contrast, a two-stage blower uses two different compression cycles. During the first compression cycle, low-pressure vapor from the evaporator of the evaporator / condenser is pumped through the lower housing. The compressed steam from the first stage is fed to the inlet port 1514 of the lower housing. The compressed air exits through the first stage and is fed to the inlet port 1510 of the upper housing 1502. This vapor is compressed again during the second stage. After the second compression cycle, the vapor is compressed at an increased pressure. The force exits the blower assembly 1500 through the outlet port 1512 in the upper housing 1502. You can go.

[0132] For a given blower design, both the single-stage and two-stage blower configurations have unique These curves show that two single-stage blowers produce a higher pressure differential. This shows that a higher steam flow rate can be generated compared to a two-stage blower. Based on this, the flow rate and efficiency of the blower depend on the flow characteristics of the blower. Depending on the pressure differential across the assembly, one configuration may be preferable to another. In the exemplary embodiment, blower assembly 1500 has a two single-stage blower configuration.

[0133] Referring now to FIG. 16-16A, an upper housing 1502 and a lower housing 1504 Within the internal cavity defined by the impeller assembly 1600 (also identified as 1506 in FIG. 15 ). The impeller assembly 1600 has multiple impellers on each side of the impeller 1602. In the exemplary embodiment, the impeller 160 includes impeller blades and a spindle 1604. 2 may be manufactured by Radel®, and the impeller spindle 1604 may be manufactured by Al. In alternative embodiments, these parts may be made of titanium, PPS, UL They may be made of materials including, but not limited to, TEM®. To manufacture these parts, the material must be able to withstand high temperatures and not absorb water. Other materials may be used. In addition, the impeller spindle 1604 is configured to receive bearing feed water. These passages allow the bearing feed water to flow to the impeller buckets and back to the reservoir. Prevent entry.

[0134] Still referring to Figure 16-16A, the blades move in a series as the impeller rotates. The impeller 1602 is designed on each side of its periphery to create a spiral flow. The motion occurs due to the additional energy as the steam flows through the open annular channel. The steam is passed repeatedly through the blades. The number of blades and the volume of the buckets are determined by the desired flow rate. The number of blades and the size of the bucket may be designed to optimize the speed and pressure difference. The products are inversely proportional to each other, so increasing the number of blades results in a higher pressure difference. The labyrinth grooves on the outer periphery of the impeller 1602 create a flow rate that is lower than that of the blower. Assembly prevents steam leakage over 1500 stages, thereby increasing blower efficiency. Can.

[0135] Referring again to FIGS. 15H-K, the shaft 1514 is connected to the upper and lower housings 1502 and 1504. In the exemplary embodiment, the shaft 1514 is made of titanium. In other embodiments, the shaft 1514 may be made of aluminum oxide, silicon oxide, or titanium. and stainless steels with coatings to increase wear and corrosion resistance. However, the shaft 1514 may be made of materials such as, but not limited to, a material such as a tubular member. There may be passages for carrying bearing supply water.

[0136] 15H-K, the two-stage blower assembly 1500 includes a lower This force may be generated at the top of the impeller assembly 1506. The second stage, located at the bottom of the impeller assembly 1506, generates a higher pressure compared to the first stage, located at the bottom of the impeller assembly 1506. In an alternative embodiment, this driving force is generated by the inner rotor magnet 1518 and an equal and opposite magnetic field generated by offsetting the outer rotor magnets 1522. This configuration may be balanced by a magnetic force in the opposite direction. Prevents excessive wear on the propulsion surfaces.

[0137] 17-17E, an alternative regenerative blower embodiment 1700 is shown. This embodiment includes an impeller housing assembly 1702, a mounting plate 1704, and a mounting A cross-sectional view of the regenerative blower assembly 1700 is shown in FIG. 17B-D. For an exploded view of the regenerative blower assembly 1700, see FIG. See also 17E.

[0138] 17-17E, a mounting plate 1704 includes a mounting flange 1706. The mounting plate also connects to the propeller housing assembly 1702. Ports are also provided that provide fluid passageways within the lower housing 1708 of the impeller housing assembly 1702. In addition, the mounting plate provides a passage for bearing feed water to exit the blower assembly 1700. Provide a passageway.

[0139] 17F-I, the impeller housing assembly 1702 is mounted in the lower housing 170 8, an impeller assembly 1710, and an upper housing 1712. See also Figures 17H-I for cross-sectional views of the laser housing assembly 1702.

[0140] 17F-I, the lower housing 1708 and the upper housing 1712 are The impeller defines an internal cavity containing the assembly 1710. The cavity is formed by an impeller passing through the inlet low pressure steam The lower housing 1708 and the upper housing 1712 provide a volume for compressing the vapor. Low pressure steam may enter the impeller housing assembly through an inlet port located in the impeller housing assembly. After being compressed by the propeller assembly 1710, the high pressure steam passes through the lower housing 1708 and the upper housing The fluid may exit through an exit port located in the lower housing 1712. 17J-K. In addition, the lower housing 1708 and the upper housing 1712 , aluminum, titanium, PPS, and ULTEM®, Not limited to these.

[0141] Still referring to FIGS. 17F-I, upper housing 1712 is attached to the top surface of the housing. The upper housing 1 may include an access cover 1714. See Figure 17L for a top view of 712. This cover is located inside the upper housing cover. Allows access to the port located in the access cover 1714 is not installed. See FIG. 17M, which provides a top view of the upper housing 1712. This view shows the upper housing 171 2 illustrates the inlet and outlet ports located within the casing.

[0142] Referring now to FIG. 17N, the lower housing 1708 and the upper housing 1712 are These features may include a vacuum conduit 1716 and a strip plate 1718. It performs similar functions as those described in the exemplary embodiment of the lower assembly 1500.

[0143] Referring now to FIG. 18-18A, a lower housing 1708 and an upper housing 1712 The internal cavity defined by the impeller assembly 1800 (also identified as 1710 in FIG. 17) This assembly includes a spindle 18, as shown in FIG. 18-18A. 18. The impeller 1804 may include a low pressure steam pump. Upon entering the internal cavity of 1702, impeller assembly 1800 rotates The vapor is compressed as it is heated.

[0144] Still referring to FIG. 18-18A, the drive motor provides rotational energy to drive the impeller. The rotor 1804 and the blade rotate. Between the inner surface of the spindle and the shaft, a bearing 171 6 may be located. 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 an alternative embodiment of the device, low pressure steam is Pressurized Vapor Cycling, published on January 27, 2005 U.S. Patent Application Publication No. 2009 / 003004 entitled "Liquid Distillation" It may be compressed using a liquid ring pump such as that described in 5 / 0016828A1. stomach. (Level Sensor Assembly) Referring now to FIG. 19, an exemplary embodiment of the water vapor distillation apparatus 100 also includes a level sensor. The sensor assembly 1900 (also identified as 108 in FIG. 1) may also be included. The assembly measures the amount of product water and / or blowdown water produced by the device 100. .

[0146] 19-19A, an exemplary embodiment of a level sensor assembly 1900 An embodiment may include a settling tank 1902 and a level sensor housing 1904. The discharge level sensor tank 1912 detects the amount of microparticles carried in the discharge water before the water enters the discharge level sensor tank 1912. The tank collects particles by reducing the velocity of the water as it flows through the tank. The settling tank 1902 defines an interior volume. A filter extends from the side wall opposite the drain port 1908 in close proximity to the drain port 1908. By using the fin 1905, it may be split almost in half. The discharge may proceed through the inlet port 1906. and the periphery of the fins 1905 before water may enter through the level sensing port 1910. As the release enters the body of the container, the increase in area Any particles in the release may settle out of suspension due to the velocity reduction. The settling tank 1902 may be made of any material that is corrosion-resistant and heat-resistant. In an exemplary embodiment, the housing is manufactured from RADEL®. The urinary vessel 1902 may be made of any material, including but not limited to titanium, copper nickel, and stainless steel. It may be made of other materials than those mentioned above.

[0147] Still referring to FIG. 19-19A, the settling tank 1902 includes an inlet 1906, a drain 1908, and a , and a level sensor port 1910. The tank 1906 may be located within the upper surface of the settling tank 1902, as shown in Figures 19A-B. Optionally, it may be adjacent to the separation fin 1905 and opposite the drain port 1908. The port allows the discharge water to enter the tank. It may be located at the bottom of the settling tank 1902, as shown at AB. provides access to the reservoir to facilitate removal of particulates from the tank. In this configuration, the bottom of the tank may be sloped toward the drain, as shown in FIG. 19B. The level sensor port 1910 is located within the upper surface of the tank as shown in FIG. 1905, but on the opposite side of the inlet port 1906. This port provides a fluid path to the discharge level sensor reservoir 1912. Port 4 is not shown in Figure 19A. This port is used to direct the discharge water to the level sensor assembly. This port allows the water to exit the settling tank 1900 and enter the heat exchanger. Located inside one of the side walls of the upper half of 902 and away from the inlet port 1906. do.

[0148] Still referring to Figures 19-19A, in the exemplary embodiment, a strainer is provided to prevent the blowdown water from flowing out. The outlet level sensor is installed in the flow path after exiting the reservoir 1912 and the settling tank 1902. The strainer may be configured to: The strainer may be made of a corrosion resistant material. In an exemplary embodiment, the strainer is made of stainless steel. The strainer may be removable to aid in cleaning the element. This limits the amount of particulates that enter the heat exchanger. Excess particulates in the blowdown water can The inner tubes of the heat exchanger can become clogged with scale and deposits, reducing the efficiency of the heat exchanger. Additionally, particulates can cause blockages that impede the flow of blowdown water through the heat exchanger.

[0149] Still referring to FIG. 19-19A, the settling tank 1902 includes a level sensor housing 1904 and The housing includes a discharge level sensor reservoir 1912, a product level sensor reservoir 1914, and a fluid connection. reservoir 1914, and bearing feed water reservoir 1916. The discharge level sensor reservoir 1912 may include an internal reservoir for detecting contaminants in the product water. It is separate from other reservoirs to prevent mixing with the discharge water. Body 1904 may be made of any material that is corrosion and heat resistant. In one embodiment, the housing is made of RADEL®. In another embodiment, the housing is made of titanium. Other materials may be used, including but not limited to copper, copper-nickel, and stainless steel. In other embodiments, the ball float may have a 45 degree range of motion, and during this movement The housing may be shaped differently, with the preference being to have a constant change in volume of the fluid level. stomach.

[0150] Still referring to FIG. 19-19A, within the level sensor housing 1904 is a discharge level sensor. The reservoir includes a measurement port 1912 located within the upper surface of the tank 1902. The reservoir is fluidly connected to the settling tank 1902 via a port 1910. The velocity of the discharged water may be measured using a level sensor 1918. As the effluent fills the settling tank, some of the water passes through measurement port 1910. vent port 1923 into the reservoir 1912. The port may be located within the top of the reservoir. This port may allow air to escape from the reservoir. This allows the discharged water to fill the cavity. The volume of the reservoir is sufficient to maintain the water level. Enclosures with too small a volume will fill and drain quickly, resulting in a level In contrast, a reservoir with a large volume may have a negative effect on the function of the sensor. A small change in fluid level height for a given increase or decrease in product will result in a slower The level sensor response time may be longer. Larger volumes may also be affected by the operation of the device. It may also mitigate fluctuations in the water level that are generated. Referring now to Figure 73, the discharge drainage 73 The fluid path is contained in the level sensor assembly and is in fluid communication with the level sensor assembly. In some embodiments, the discharge drain 7300 fluid path may be It can be used to facilitate cleaning or flushing. In some embodiments The discharge drain 7300 fluid path may be sealed from the ambient environment, for example by a manual ball valve. In some embodiments, the valve is a manual valve, but the seal is not limited to a manual ball valve. It may not be necessary to provide a valve, for example, a differential valve controlled by a control system. In some cases, cleaning and flushing may be at least partially automated.

[0151] Still referring to FIG. 19-19A, a product level sensor reservoir 1914 detects the release level. The product level reservoir 1914 may be located next to the inlet port. The product water passes through the inlet port 1920 and the outlet port 1922. The fluid enters the reservoir through the outlet port 1922 and exits the reservoir through the outlet port 1922. 2 is located below the low end measuring point of the level sensor to improve the outflow of water from the reservoir. Similarly, the inlet port 1920 may be positioned to minimize disruptions caused by inflowing water. It may be located below the low end measurement point of the level sensor to minimize the size. Inlet port 1920 and outlet port 1922 are level, as shown in FIG. 19A. This reservoir may be located on the side of the sensor housing 1904. Additionally, the vent port 1923 provides a space for measuring the velocity of the product. The port may be located in the top of the reservoir. This port allows product water to fill the cavity. This allows air to escape from the reservoir.

[0152] Still referring to FIG. 19-19A, the product level sensor reservoir 1914 is a bearing supply. The external port 1924 is in fluid communication with the water reservoir 1916. The product water flows between the product level sensor reservoir 1914 and the bearing supply water reservoir 1916. The product water is pumped through an external port 1924 to the bearing feedwater reservoir 19 16. Additionally, a bearing feed water reservoir 1916 is provided through the supply port 1916 shown in FIG. 19C. The supply port 1926 is connected to the regenerative blower assembly. Similarly, return port 1928 provides a fluid path for lubricating the bearings within the valve. Provides a fluid path for product water to return from lubricating the bearings of the regenerative blower assembly. The supply and return ports are located on the side of the level sensor housing 1904, as shown in FIG. 19C. It may be located at.

[0153] Still referring to FIG. 19-19A, the amount of product water in the bearing supply water reservoir 1916 is monitored. In an exemplary embodiment, an optical level sensor is provided. The sensor may be located about two-thirds of the way up in the bearing feedwater reservoir 1916. senses the presence of water in the reservoir and determines that there is enough water to lubricate the bearings. The sensor is also installed by threading the sensor into the level sensor housing 1904. The sensor may include an O-ring to provide a watertight seal. In form, the sensor may be a conductivity sensor, a float switch, a capacitance sensor, or an ultrasonic It may be, but is not limited to, a sensor.

[0154] 19D-F, an alternative level sensor housing 1 having two reservoirs is shown. 930 is shown. Within the level sensor housing 1930 is the discharge level sensor reservoir 19 32. This reservoir is connected to the aforementioned release reservoir 1912 in the level sensor housing 1904. In contrast, the product level sensor reservoir 1934 contains the product water that feeds the bearings of the regenerative blower. Level sensor housing 1904 The bearing feed water reservoir 1916 is eliminated from this configuration. Instead, the product water is pumped to the reclaimed block. The product level sensor draws from the reservoir to provide water for the lowers.

[0155] Still referring to Figures 19D-19F, the product level sensor reservoir 1934 is port 1935, outlet port 1936, return port 1938, and supply port 1940. An inlet port 1935 allows product water to enter the reservoir. Similarly, outlet port 1936 provides a fluid path for the product water to exit the housing. Additionally, supply port 1940 allows product water to leave the reservoir and lubricate the bearings of the regenerative blower. After passing through the regenerative blower bearings, the product water returns through return port 1938. These ports may be located anywhere within the enclosure. The supply port 1940 and return port 1938 may be located near the bottom of the housing. By doing so, adverse effects on the function of the level sensor may be suppressed.

[0156] 19G-H, receiving input from a level sensor assembly 1918 The sensor 1942 may be located outside the level sensor housing 1904 so that Upon receiving input from the bell sensor assembly 1918, the sensor 1942 In an exemplary embodiment, the sensor signals that the position is within a particular range or at a particular level. , or a continuous analog sensor. This type of sensor is included in the level sensor assembly 19 Provides continuous feedback for 18 positions. A magnet inside the level sensor changes position This causes a voltage change that 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. FIG. 19H shows a level sensor including a set of floating magnets 1944 and position magnets 1946. 19 illustrates one possible alternative embodiment of the sensor assembly. The sensor is attached to the side of the housing 1904.

[0157] Referring now to FIG. 20-20A, the release level sensor reservoir 1912 and the product level Within the level sensor reservoir 1914 is a level sensor 2000 (see FIG. 19A and 19E). 18). These sensors are located in the base 2002 and the arm 2004. and a floating ball 2006.

[0158] Still referring to FIGS. 20-20A, an exemplary embodiment of the level sensor 2000 includes an articulated The assembly may include a base 2002 that supports a frame 2004 and a floating ball 2006. The base also includes two magnets (not shown). The base is connected to the arm and floating ball assembly. The assembly pivots on a small shaft (not shown). These magnets are positioned 180 degrees from each other and are located on the surface of the base 2002. In addition, these magnets are positioned at the pivot point in the base 2002 and parallel to the pivot. In an exemplary embodiment, the magnets are cylindrical with an axial magnetization direction. It may also be a magnet.

[0159] Still referring to FIGS. 20-20A, the level sensor 2000 includes an arm with respect to a pivot. and measure the rotation of the ball assembly. In the exemplary embodiment, the maximum displacement angle is 45 degrees. In this embodiment, the level sensor is located directly below the pivot point of the floating ball 2006. In other embodiments, the maximum displacement angle is as large as 80 degrees. The sensor may monitor the magnet through the wall of the enclosure. prevents exposure to corrosive water discharges and allows the level sensor housing to be sealed The base may be made of any material that is corrosion-resistant, heat-resistant, and non-magnetic. In the illustrated embodiment, the base 2002 is made from G10 plastic. The base 2002 is made of RADEL® titanium, copper nickel, and fiberglass composite. It may also be made of other materials including, but not limited to, laminates.

[0160] Still referring to Figures 20-20A, base 2002 has arm 2004 attached thereto. An arm 2004 connects the base 2002 with a floating ball 2006. In the exemplary embodiment, The Arm 2004 is made of G10 plastic material, which has sufficient high temperature resistance. Other materials may be used to manufacture the arm 2004 if one has preferences. Other materials include stainless steel, plastic, RADEL®, titanium, and The length of the arm may include, but is not limited to, copper nickel. In addition, the exemplary embodiment has a longitudinal axis of the arm and a vertical axis. These openings reduce the weight of the arms and allow the arms to Allows for greater sensitivity to level changes.

[0161] Still referring to FIG. 20-20A, the other end of the arm 2004 has a floating ball 2006. The floating ball 2006 provides a surface area for the water flow to contact. The force applied to the floating ball 2006 causes the level sensor assembly 2000 to pivot about a small diameter axis. The change in position of this arm indicates the amount of water in the device. It may be made of any material that is resistant to heat and moisture. In addition, the material preferably has low water absorption. In an exemplary embodiment, the floating ball is made of hollow stainless steel. For applications with high concentrations of water, the Floating Ball 2006 is suitable for plastics, titanium, and It may be made of any highly corrosion resistant material, including but not limited to copper-nickel. Additionally, the floating ball 2006 is preferably adapted to be disposed within the level sensor housing 1904. Because of its positive size, the floating ball can move freely. The size of the level sensor reservoir is determined by the size of the level sensor reservoir.

[0162] 21-21A, the supply port 1926 of the bearing supply water reservoir 1916 A bearing feed pump 2100 (also identified as 110 in FIG. 1-1A) is connected to The pump 2100 pumps product water from the bearing feedwater reservoir 1916 to the regenerative blower. In an exemplary embodiment, the flow rate is 60 ml / min and the pressure is 2 p si to 2.5-1 / 4 psi. Pump maintains proper lubrication flow to bearings in regenerative blowers. Any type of pump can be used, with the preference being to provide sufficient volume to Additionally, the pump 2100 preferably is adapted to withstand the high temperatures of the surrounding environment and the pump. It is heat resistant to withstand the high temperatures of the hot product water passing through it. The water pump 110 is a GOTEC linear positive displacement pump, model number ETX-50-VIC. In an alternative embodiment, the pump may be able to operate at higher temperatures, allowing for a longer service life. Other pump types may also be used, such as a cardioplegic pump. (Control equipment) The device may also include a manifold with multiple control valves for different water flow paths. Essentially, the manifold is connected to the inlet piping for the source water to control the amount of water entering the system. It may also include a control valve, which at excessive pressure may fail to open, or Once opened, it may not be possible to close it, so please use it to adjust the source water pressure. , a regulator may be included in the inlet piping.

[0163] Similarly, the manifold may also include a control valve in the outlet piping that conveys the blowdown water out of the system. This valve allows the operator to control the amount of blowdown water exiting the device.

[0164] The control manifold may also include a control valve in the outlet line for the product water. In an exemplary embodiment, the outlet There is one control valve for each section of piping. Similarly, the unit is The vent valve allows a small amount of vapor to escape, preventing the device from Maintains the operating conditions of the equipment. Prevents the equipment from overheating by releasing steam. Similarly, condensers, which release steam and can prevent the device from functioning, It also prevents the accumulation of compounds in the air.

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

[0166] The apparatus is also disclosed in 2005 Sept. 2005, the contents of which are incorporated herein by reference. A U.S. patent entitled "Backpressure Regulator" was issued on the 8th of this month. It may also include a back pressure regulator, such as that described in published application 2005 / 0194048A1. good.

[0167] The water vapor distillation apparatus may include a voltage regulator. Typically, the apparatus is connected to a conventional wall outlet. However, in other countries, the voltage may be different. To handle this voltage difference, the correct type of voltage must be installed in the electrical configuration of the device. A voltage regulator may be included in the device to ensure that the components are supplied with

[0168] In addition, a battery may be included in the system to provide electrical energy to the device. If the electrical energy is supplied from a battery, the device preferably directly converts the incoming electricity In another embodiment, the device includes an electrical inverter that converts current to alternating current. These embodiments may receive electrical energy from a turbine and an internal combustion engine. may also require an electrical inverter. In other embodiments, the device may A boost loop is used to increase the amount of voltage delivered to the device to power it. It may include. (How to distill water) The present invention relates to a method for preparing a water purification system, comprising the steps of filtering source water, heating the source water using a heat exchanger, and converting source water into low-pressure steam; and converting the source steam into water to produce dry low-pressure steam. and compressing the dry low-pressure steam into high-pressure steam. and condensing the resulting mixture into water.

[0169] Referring now to Figure 22-22A, source water is converted into steam, which is then called product water. 22 shows the flow of source water in a previously disclosed device. The source water flows through an inlet pipe connected to a heat exchanger as shown in Figure 22A. Typically, a pump directs source water through an inlet pipe into the heat exchanger. The inlet pipe may be provided with a heat exchanger and a feedstock where the feedstock enters the pipe. There may be a strainer 2202 installed between the connection (see FIG. 22A). In this embodiment, a regulator 2204 is provided in the inlet pipe to regulate the flow of source water into the device. Similarly, in one embodiment, a valve 22 may be provided to isolate the device from the water source. 06 may be disposed within the inlet pipe.

[0170] Still referring to FIG. 22-22A, in operation, source water passes through strainer 2202. These large particles are removed by the inlet and discharge valves or heat exchangers. This may cause clogging of the inner tube of the device, adversely affecting the operation of the device. The particles may accumulate on the evaporator / condenser tubes, reducing the efficiency of the device. In an embodiment, the strainer 2202 is located before the control valve. The strainer may be located before the inlet pump (not shown). The cleaner 2202 has a 50μ user cleaner unit. In an alternative embodiment, the device , the strainer 2202 may not be included. After the source water passes through the strainer 2202, the water enters the heat exchanger 2208.

[0171] Referring now to FIG. 22B, upon entering heat exchanger 2208, the source water The outer tube of 208 may be filled. In an exemplary embodiment, the heat exchanger includes a counterflow tube inch. The source water enters the heat exchanger at approximately ambient temperature. The source water and blowdown water enter the heat exchanger at a temperature higher than the ambient. The source water enters the heat exchanger at the other end, and the product and blowdown water enter the heat exchanger at the other end. As it flows through the heat exchanger, the high thermal energy of the product and reject water is transferred from the inner tubes of the heat exchanger. This increase in temperature of the source water is transferred to the water This allows the gas to be converted to steam more efficiently.

[0172] Now referring to Figures 22C-D, once the source water is introduced into the counter-flow tube-in-tube heat exchanger, After passing through the heat exchanger, the water exits the heat exchanger and enters the regenerative blower motor cooling loop. During this time, the regenerative blower motor 2210 generates heat energy. The water must be removed from the blower motor 2210 for the blower to operate properly. As the heat passes through the blower motor cooling loop, Energy is transferred to the source water. Heat transfer allows the blower motor to maintain a lower operating temperature. This allows for the temperature of the source water to be increased. Higher source water temperatures increase the efficiency of the device. However, it requires less energy to cause the phase change of the source water to steam. The source water comes from the regenerative blower motor cooling loop and is shown in Figure 22E. The water passes through a sump 2212 into the evaporator / condenser.

[0173] Now, as shown in Figure 23-23A, the system also contains highly concentrated source water, called effluent. This water removes particulates from the system and prevents scale buildup on the evaporator / condenser tubes. This fluid contains non-volatile contaminants that were present in the source water. These contaminants may be particles from pollutants, heavy metals, or organic compounds. Specifically, these contaminants may include, but are not limited to, calcium carbonate. In addition, the bleed water may contain, but is not limited to, sodium hydroxide, magnesium carbonate, and magnesium carbonate. As it passes through the heat exchanger, it transfers heat energy to the source water. The fluid path of the blowdown water within the device is shown. The blowdown water passes through the steam chamber 230 as shown in FIG. 23A. As the low pressure steam passes through the steam chamber 2302, water droplets separate from the steam. These water droplets accumulate at the bottom of the steam chamber 2302 and add to the existing discharge water. As the discharge water level increases, water exits the steam chamber 2302 through the port. Through the port, the blowdown water leaves the steam chamber 2302 and passes through the level sensor shown in FIG. 23A. Enter the sub-casing 2304.

[0174] 23B-C, blowdown water enters the level sensor housing 2304 and sinks. Fill the settling tank 2306. As the effluent passes through the settling tank 2306, particulates in the water are removed. The particles settle to the bottom of the tank, thus separating the water from the particles. This prevents particles from entering the heat exchanger. The presence of particles can have a detrimental effect on the heat exchanger. Particulates can reduce the discharge flow through the inner pipe and can cause the exchanger to be less efficient. This can reduce the amount of heat energy that can be transferred. A cluster of particles can cause blockages in the inner tubes, obstructing the flow of discharge water through the heat exchanger. As the blowdown water fills the settling tank 2306, the water also flows into the blowdown level illustrated in FIG. The bell sensor reservoir 2308 may be filled.

[0175] 23D-G, blowdown water exits the level sensor housing 2304. In doing so, it passes through a strainer 2310 before entering the heat exchanger 2312 shown in FIG. 23E. The strainer 2310 may be configured to allow the water to pass through the settling tank 2306 of the level sensor housing 2304. Remove particulates from the effluent that remain after flowing. This reduces particulate buildup in the heat exchangers and valves in the system. As shown in FIG. 23E, the water enters the heat exchanger 2312 and fills one of the inner tubes. Fill the heat exchanger 2312 as shown in 23F. The blowdown water passes through the heat exchanger. As the water flows, the higher temperature discharge water is transferred to the lower temperature source water through a pipe containing the discharge water. The heat energy is transferred to the effluent water, which exits the heat exchanger shown in FIG. 23G. After leaving the heat exchanger, the discharge fluid passes through a mixing can 2314 before being discharged from the device. Prevent vapors from potentially causing harm to individuals or nearby objects. The condenser space may be periodically vented to maintain a constant energy balance. Similarly, gaseous vapors (e.g., volatile organic compounds, air) must be present to maintain proper operation of the equipment. Both steam and gaseous vapors must be purged from the condenser space to prevent the The steam is discharged into a mixing vessel 2314 with the discharge water. Thus, condensing the vapor allows the vapor to be safely released. is used to separate the mixing vessel from the device or to regulate the flow rate of the discharge water exiting the device. There is a valve located in the tubing connecting the heat exchanger 2312 and the mixing vessel 2314. Good too.

[0176] Referring now to Figure 24-24A, when contacting the outer surface of the tubes in the evaporator / condenser, high pressure As the steam condenses, product water is formed. Figure 24 shows the product water in the previously disclosed device. The fluid paths are shown. The product water is evaporated in the evaporator / condenser 2402 as shown in FIG. As high pressure steam condenses against the exterior surface of the evaporator / condenser tubes, it creates water droplets. These water droplets accumulate at the bottom of the evaporator / condenser 2402, creating product water. As the production water level increases, water exits the evaporator / condenser 2402 through a port and enters the level sensor housing 2404 shown in FIG. 24A.

[0177] Referring now to Figures 24B-24E, the product water is fed to the product level separator shown in Figure 24B. The fluid enters the level sensor housing 2404 through a port connected to the level sensor reservoir 2406. The reservoir may collect the incoming product water and measure the amount of water produced by the device. The water exits the product level sensor reservoir 2406 and passes through the heat exchanger shown in FIG. 24C. 2408. While passing through heat exchanger 2408, the hot product water is The heat energy is transferred to the low temperature source water through the inner tube of 8. After passing through the heat exchanger 2408, the product water is shown in FIG. In the exemplary embodiment, the system includes a product bypass valve 2410 and and a product valve 2412. The product valve 2412 allows the operator to exit the device. Allows for regulating the flow of produced water. Typically, once the reservoir is 50 percent Once filled, the production is adjusted so that the amount of water entering the reservoir is equal to the amount leaving the reservoir. During the initial start-up of the system, the valve 2412 is cycled. The product water is rejected as waste by opening the product bypass valve 2410. Once the product is determined to be of sufficient quality, product bypass valve 2410 is closed and product valve 241 2 starts working.

[0178] 24F-24H, product water passes through the product level sensor reservoir 2406. As it fills, water may also enter the bearing feed water reservoir 2410. Section 2410 collects incoming product water for lubricating the bearings in regenerative blower 2412. The product water exits the bearing supply water tank 2410 and is pumped through pump 241 as shown in FIG. 24G. 4. Pump 2414 moves the product water to the regenerative blower. After exiting 14, the product water enters a regenerative blower 2412, shown in FIG. 24H.

[0179] 24H-24I, upon entering the blower 2412, the product water flows through the shaft It provides lubrication between the receiver and the blower shaft. After exiting the regenerative blower 2412, the product water , and may re-enter the level sensor housing 2404 through the bearing feed water reservoir 2410 (see FIG. See 24I).

[0180] Referring now to Figures 25-25C, to assist in the flow of water throughout the device: Ventilation paths may be provided. These paths allow for the removal of air or vapor from the device. This aids in the flow of water through the device. The ventilation channels are shown in Figure 25. Figure 25A shows the release level. 25 shows the airflow path from the sensor reservoir 2502 to the vapor chamber 2504 of the evaporator / condenser 2508. This path allows the air in the reservoir to escape, allowing more of the released water to escape. Similarly, FIG. 25B illustrates the product level sensor reservoir 2. 506 to the evaporator / condenser 2508. This path is Allows the air to exit and allows product water to enter the reservoir. FIG. 25C shows the air inside the device exiting the device through a mixing can 1510 into the surrounding atmosphere. 2508. In addition, the evaporator / condenser 2508 has a vent path from the condenser area that allows The ventilation passage helps maintain equilibrium in the unit by venting a small amount of vapor from the unit. Assist.

[0181] Referring now to FIG. 26, in operation, source water is steamed in the manner described in FIGS. 22-22E. The source water first enters the basin 2602 of the generator / condenser 2608. Additional heat energy may be transferred to the water using a heating element. The heating element may be used during the initial start-up of the steam distillation apparatus. As the amount of source water in the basin increases, water flows out of the basin. 26, located between the water reservoir 2602 and the evaporator / condenser 2608. The gas flows through a port inside the plate 2606 and into the evaporator / condenser tubes 2604. During initial startup, the evaporator portion of the evaporator / condenser 2608 is fully charged into the emission level sensor reservoir. After initial start-up, the pipe 2604 is filled with source water until a sufficient amount of water is present. It is still full of source water.

[0182] 26A-26E, once inside the pipe 2604, the source water flows through the pipe It is heated by the conduction of heat energy from the high pressure steam outside the tube through the tube wall. FIG. 26A illustrates wet low-pressure steam flowing through tubes 2604 of an evaporator / condenser 2608. The wet low pressure steam travels through the tubes 2604 of the evaporator / condenser 2608, as shown in FIG. The steam enters the steam chamber 2610 shown in FIG. B. Steam flows through the interior of the steam chamber 2610. As the steam is heated, the water droplets within the steam are separated from the steam. These water droplets are then transported to the base of the steam chamber 2610. This collects in the water column and adds to the discharge water already present at the base (see Figure 26C-D). The water leaves the device in the manner described in Figures 23-23G. Dry low-pressure steam leaves steam chamber 2. 610 and enters the regenerative blower 2612 as shown in Figures 26E-F.

[0183] Now referring to Figures 26F-H, once inside the regenerative blower 2612, the dry low The compressed steam is compressed to produce dry high-pressure steam. After the dry steam is compressed, the high-pressure steam is , exits the regenerative blower 2612 and enters the steam pipe 2614 of the steam chamber 2610. 2 illustrates steam exiting 2612 and entering steam pipe 2614 of steam chest 2610. See 6G-H.

[0184] 26H-J, the vapor pipe 2614 is located inside the evaporator / condenser 2608. The steam pipe 2614 is in fluid communication with the cavity. 2608. The high pressure steam provides an independent path for entry to the condenser side of the The steam is separated to maintain a constant temperature and to ensure that the steam is free of contaminants. The dry, high pressure steam exits the steam chamber 2610 through steam pipe 2614 and passes through the evaporator / condenser 2608. 26. Entering the internal cavity. FIG. 26 shows the internal cavity of the evaporator / condenser 2608 containing high pressure steam. See 26I. When high pressure steam contacts the exterior surface of the tubes 2604 of the evaporator / condenser 2608, As the steam flows, it transfers heat energy to the tube 2604. This energy penetrates the tube walls The energy is transferred from the steam to the tube wall. When the steam is released, it condenses from the vapor into a fluid known as product water. As water droplets form on the outside of the tube walls, they flow to the base of the evaporator / condenser 2608. See FIG. 26J, which shows the formation of product water within the internal cavity of the evaporator / condenser 2608. When the amount of produced water in the cavern is sufficient, the produced water will It may flow out of the evaporator / condenser as shown.

[0185] Referring now to FIG. 27, there are several factors that may affect the performance of the described device. One of these factors is the pressure differential across the regenerative blower. is the amount of energy required to produce one liter of product versus the amount of energy required for a regenerative blower. 1 is a graph illustrating the relationship between the change in pressure due to the temperature change. It is desirable to operate the blower so that the maximum amount of product water is produced. Therefore, operating the blower at a pressure differential between 1.5 psi and 2 psi requires the least amount of energy. Use the pressure range to produce 1 liter of product water. This increases the amount of energy required to produce one liter of water.

[0186] Referring now to FIG. 28, another factor that may affect the performance of the device is evaporation. The number of heat transfer tubes installed in the internal cavity of the regenerator / condenser assembly. For a given change in pressure across the row, the relationship between the number of heat transfer tubes and the product water production flow rate From this graph, it can be seen that the more heat transfer tubes there are, the more product water is produced. In this graph, the configuration that produces the most product water per hour is the one with 85 tubes. The configuration that produces the least amount of water is 43 for pressures of 2 psi or less. The assembly has a chisel tube.

[0187] Referring now to FIG. 29, this figure illustrates the product water generated by different heat transfer tube configurations. This graph shows that the configuration with 102 heat transfer tubes produces the highest amount of produced water. In contrast, a configuration with shorter tube lengths and only 48 tubes produced a minimum of produced a quantity of product water.

[0188] Referring now to FIG. 30, despite having fewer tubes than other configurations, 4 The eight heat transfer tube configuration produces more water per surface area. Figure 30 shows the amount of water produced. This graph illustrates the relationship between the amount of product and the amount of heat transfer surface area. It is shown that the 48 heat transfer tube configuration with a tube length of 1000 is the most efficient design. The less efficient configuration is the 102 heat transfer tube design. Having more tubes can produce more water, but a design with fewer tubes can The plan may provide the most efficient use of resources.

[0189] Referring now to Figure 31, this graph shows the difference in performance between two 48 tube designs. In this graph, the difference between the designs is the length of the pipe. In terms of power change, this graph shows the amount of energy used and the amount of water used for the two configurations. The configuration with the 20-inch long pipe produced slightly more. While producing slightly less energy at a uniform pressure differential across the regenerative blower Consumes energy. (Control method) The pressure difference across the compressor directly determines the amount of product water the unit can produce. The pressure differential across the compressor can be adjusted to ensure a constant product water output. Increasing the evaporator speed typically results in an increase in the pressure differential across both the evaporator and condenser. Increasing the pressure differential 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 time required to operate the machine. The amount of blowdown water required. Without sufficient blowdown water, the particulates separated from the source water will be This buildup of particulates can adversely affect the operation and efficiency of the device.

[0191] To ensure that particles are removed from the device, There must be sufficient blow-off water to operate the equipment in the particular environment. It is necessary to know the amount of water entering the system (source water) to determine how much blowdown water is required. If the source water has a high concentration of particulates, the device must be designed to absorb and Conversely, if the source water has a low concentration of particulates, more bleed water is required to remove them. If this is the case, less blowdown water is required.

[0192] To control and monitor the amount of product and blowdown water produced by the equipment, several Several different control methods may be implemented. These methods include controlling the amount of water in a reservoir located within the device. measuring the water levels of the product water and the discharge water of the device; measuring the flow rate of the effluent water, measuring the amount of influent source water, and measuring the flow rate of the produced water This may include, but is not limited to, measuring force.

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

[0194] Changes in the position of the level sensor assembly, the area of ​​the reservoir, and the time associated with changes in the water level By knowing the time, the water flow rate may be determined. Since there is no drop, it is advantageous to use a floating sensor to determine the flow. It may also indicate the performance of the device and whether that performance is consistent with normal operation of the device. The information allows the operator to determine whether the equipment is functioning properly. For example, if the operator determines that the flow rate is below normal operating conditions, the operator may Also check the strainer in the inlet piping or the evaporator / condenser tubes for scale. Similarly, the operator may use the flow rate to make adjustments to the device. The method may include varying the amount of blowdown water and product water produced. This measurement may indicate the performance of the device, but is not required.

[0195] The quality of either the influent source water or the effluent product water to control the operation of the steam distillation unit. This control method determines the operation of the machine based on the water quality. In this mode, the conductivity of the product water is monitored. If the conductivity exceeds a specified limit, the sensor will shut down the unit. In some embodiments, the sensor may be a conductivity sensor. In an alternative embodiment, the step of monitoring the conductivity of the bleed water may be, but is not limited to, If the conductivity of the effluent water exceeds a specified limit, a sensor may be provided to measure the amount of source water entering the device. Increasing the source water reduces the conductivity of the blowdown water. In the case of a water treatment system, the conductivity of the source water may be monitored. If the conductivity exceeds a specified limit, a sensor Sends a signal to adjust the flow rate. Higher source water conductivity leads to higher source and discharge water conductivity. A flow rate may be provided.

[0196] In an alternative embodiment, the device may include a control scheme in which the device has a steady mode. While in this mode, the device reduces the amount of power consumed. During this time, the heating element may continue to maintain a particular temperature or temperature range of the source water in the basin. Maintaining the source water temperature allows time for the machine to start producing more product water. Additionally, during this mode the regenerative blower is not functioning and the inlet and outlet The valve is closed.

[0197] Examples of tests that may be performed on source water samples to analyze source water quality include bacteriological tests, mineral tests, and chemical tests. Bacterial tests are used to detect any bacteria that may be present in the sample. It indicates the amount of certain bacteria. The most common type of bacterial test is total coliform bacteria.

[0198] Mineral test results may indicate the amount of mineral impurities in the water. Impurities can pose health hazards and affect the appearance and usefulness of water.

[0199] Another type of water testing that may be performed is chemical testing. Many man-made chemicals are present in water supplies. It may contaminate roads and pose a health hazard to water consumers. This type of testing is not recommended for unspecified chemical contaminants unless a specific substance is suspected to be in the water. It may not be performed routinely due to the high cost of the material. If a substance is suspected to be present in source water, testing may be carried out. An example of a quality check is 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 basic. or alkaline. The higher the pH, the more alkaline it is. In the United States, the pH of natural water is usually between 6.5 and 8.5. Freshwater sources with a pH above 9.5 cannot provide nutrients to plant or animal species. The pH may be measured using any method known in the art for testing. It may be determined.

[0201] pH should be measured immediately, preferably at a source water testing station, as changes in temperature can affect pH values. Preferably, the water sample is taken from the "bank" when using lakes, streams, rivers, puddles, etc. They are collected underwater, away from the surface of the water.

[0202] Nitrate - Nitrogen is used by all living plants and animals to build proteins Nitrogen is an essential element in aquatic ecosystems. It exists in many forms: oxygen and They may combine to form compounds called nitrates. Nitrates are found in fertilizers, sewage, and industrial wastewater. They can cause eutrophication of lakes and ponds. Eutrophication occurs when nutrients (such as nitrates and phosphates) are added to a body of water. These nutrients typically come from agricultural soils, sewage, detergents, animal waste, and leaking septic systems. The presence of nitrates is determined by any known method in the art for testing. This may be determined using known methods.

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

[0204] When water is highly turbid, there are many suspended particles in it. These soil particles are dispersed throughout the water. They block light and prevent aquatic plants from receiving the sunlight they need for photosynthesis. They produce less oxygen, which reduces DO levels. Plants wilt more easily and lose water. The bacteria in the water decomposes the soluble solids, which reduces the DO level even further. The amount of ATP present may be determined using any method known in the art for this purpose.

[0205] E. coli - coliforms are present in water supplies because the water supply is not receiving sewage or other septic waste. Coliform bacteria are usually found on the surface film of the water or in sediments on the bottom. Found in large quantities in piles.

[0206] Fecal coliform bacteria found in the lower intestine of humans and other warm-blooded animals are a type of coliform bacteria The presence of fecal coliform bacteria in water supplies is a clear sign that sewage has contaminated the water. Tests can be performed specifically for fecal coliforms or for total coliforms, including all E. coli strains. The presence of E. coli may be indicative of fecal contamination. It may be determined using any method known in the art.

[0207] During operation, the water machine performs conductivity testing of the source water and / or product water to determine if it is entering the system. The quality of the incoming and outgoing water may be determined. This test may be performed on the inlet and outlet piping of the system. This may be accomplished using a conductivity sensor installed in the water. Conversely, water with a lower amount of conductivity indicates a higher amount of impurities. This type of testing is comprehensive and shows that the water has a lower level of impurities. It only provides a general indication of the purity / quality of the water being used.

[0208] Including but not limited to pH, hardness, chloride, color, turbidity, sulfate, nitrite, nitrate, and E. coli. Other types of tests may be used to analyze specific levels of water impurities / characteristics, including but not limited to: Typically, an operation is performed to analyze the water entering or exiting the machine. The person may first obtain a water sample. After obtaining the desired sample, the water is Obtained from the company (Loveland, Colorado 80539-0389) Other methods for testing water purity include analytical testing. The method may include sending the water to a laboratory for analysis. (a system for distilling water) This specification refers to the May 2007 issue of the IEEE 802.1 ... Systems and Methods for Distributed Systems U.S. Patent Application Publication No. 2007 / 0112530 entitled "Telecommunications Utilities" As described in A1, the previously disclosed apparatus for distilling water is Further, the contents of which are incorporated herein by reference. "Systems and Methods," May 17, 2007, incorporated into Published U.S. patent application entitled "Systems for Distributed Utilities" As described in Patent Publication No. 2007 / 0112530A1, the monitoring / communication system also , may be included within a distribution system. Alternative Embodiments Although exemplary embodiments of the still / steam distillation apparatus have been described, the specific elements of the still (i.e. Alternative embodiments of the distiller, including alternative embodiments of the heat exchanger, evaporator / condenser, compressor, etc. Thus, in some alternative embodiments, one or more of the elements may be: In some embodiments, the distillation The entire device may be replaced with an alternative embodiment, e.g., a system as described in one embodiment may be While the exemplary embodiment utilizes a distiller, in other embodiments, the system may utilize alternative embodiments. Make use of this attitude.

[0209] Referring to Figures 32-32C, an alternative embodiment of a water vapor distillation apparatus having a liquid ring pump 3200 is shown. The ring pump may include a fully rotating housing, which is frictionless. provides the greatest reduction in friction losses, yet maintains the simplicity and Maintaining cost-effective production. As shown in FIG. 32, the stator 3202 is connected to the rotor 3204. The steam is stationary relative to the steam source and has an inlet 3206 and an outlet 3208. The steam is The rotor 3204 is drawn into the rotor chamber 3210. The rotor 3204 has a rotating housing on it. The rotor 3204 is offset from the central axis Z, which is the center of the liquid ring pump. As the bearing 3214 rotates around the central axis 3212, the The effective volume is reduced, causing the vapor to be conveyed along a rotational path into the outlet 3208. As it is refrigerated, it is compressed to a pressure P2 and sent to the evaporator / condenser 104 of FIG. The rotating housing (not shown) is a liquid-sealed type to reduce energy loss due to friction. It rotates with the liquid ring inside the pump.

[0210] Referring to Figures 32A-B, the stator 3202 includes support structures 3 in the input and output regions. 216. The support structure 3216 of the top view of the stator 3202 shown in FIGS. Below, the individual blades 3218 of the rotor 3204, as well as the rotor 3204 around the central axis, This particular embodiment of the liquid ring pump is an axially fed The pump is fed and discharged axially and may have a vertical, horizontal, or other orientation during operation. Figure 32C shows yet another view of this embodiment.

[0211] The 3200 Liquid Ring Pump is typically designed to operate in the range of 5 to 15 psig. The device is designed to operate within a very narrow range of input and output pressures. is regulated using a check valve that releases steam from chamber 3210 in Figures 32-32C. Improved device performance may be achieved by preferably increasing the exhaust port speed at a specific rotation angle around the rotor axis. This is achieved by positioning the outlet 3208 at a specific angle as desired for the distillation operation. Corresponding to the desired pressure increase. One embodiment of a specific port opening angle to regulate the pressure of the device. The outlet 3208 is positioned at approximately a 90 degree rotation around the rotor access. This allows steam from the chamber 3210 to escape. Placing the outlet 3208 at a corner increases the pressure in the system and reduces the pump throughput. while positioning the outlet 3208 at a lower angle around the stator axis provides a more This results in lower system pressure and increased pump throughput. Selecting the placement of the outlet 3208 accordingly may result in improved pump efficiency. Additionally, the placement of outlet 3208 to maintain pressure in the device is achieved by providing an exhaust port to chamber 3210. The complexity of the device may be minimized by eliminating check valves in the port, thereby This provides a simpler and more cost-effective compressor.

[0212] Referring now to FIG. 32D, during operation, the liquid phosphorus in the compressor is adjusted to optimize performance. In the embodiments disclosed herein, it may be desirable to measure the depth of the liquid seal. The pump housing 3232 rotates with the liquid ring in the pump, and the temperature of the fluid is typically The temperature is about 110°C. Methods for measuring the depth of the ring include ultrasonic waves, radar, floats, and currents. Any one of the conventional methods, such as using electrical conductivity and optical sensors. Due to the complexity of the rotating enclosure, the use of a capacitive sensor is the preferred implementation for this measurement. As the depth of the fluid in the capacitor changes, the capacitance of the capacitor also changes. To become.

[0213] Still referring to FIG. 32D, a disc-shaped capacitor sensor plate 3234 is mounted on the rotating housing 323. 2 and the bottom surface 3204A of the rotor 3204, 32. Therefore, the capacitor is attached to the bottom of the housing 3232, the rotor 320 4, and the capacitor sensor 3234. The lead 3240 is From the sensor 3234, through a passage 3236A in the rotating housing shaft 3236, preferably A capacitor is connected to the secondary 3242 (not shown) of the ferrite core transformer. In an embodiment, the secondary 3242 rotates at the same speed as the capacitor plates, and the ferrite It is inductively connected to the primary of the magnetic core transformer. The primary winding 3238 is stationary and has a level The signal going to and from the measuring capacitor is transmitted through a transformer, thus rotating the depth information. Capacitance allows the current to be transmitted from the secondary to the stationary position. It is measured by determining the LC resonance of a capacitor (C) with a capacitance (L). In an exemplary embodiment, an LC oscillator circuit is constructed and the oscillation frequency is used as a measure of capacitance. will be done.

[0214] Referring to FIG. 32E, this diagram illustrates the steam flow to the evaporator / condenser 104 of FIG. Alternative pump 3200 designs to prevent contaminating fluid droplets from being entrained and transported In such an embodiment, the liquid ring pump 3200 is The spray is removed as the rotating housing 3232 rotates, and the rotating housing 3232 rotates. creates a cyclone effect, forcing the atomization and droplets to fly off through centrifugal force, forcing the distillation The rotating housing 3232 and the fixed housing 3232 collide with each other and fall into the water in the pool. 28 to enhance the circulation and rotation of steam in the annular space between the rotating housing 3232. There may be fins 3244 extending from the outside. 104 is provided in the flow path.

[0215] Referring now to Figures 32F-G, an alternative embodiment of a liquid ring pump 3200 is shown having a single An outer rotating housing 3254 that surrounds the channel stator / body 3256 and rotor 3258 The pump may include a ring pump 3252 with a rotating housing 3254 and a stationary stator / body. The sealing surface between the stator / body 3256 and the cylinder is a two channel stator / body 3256. The chamber 3260 of the pump 3252, as well as the rotor 3258 and rotating housing 3254 3262 and outlet 3264. The steam is The rotor rotates around the stationary stator 3256. As the intake 3266 aligns with the intake holes 3268 in the rotor 3258, the steam It passes through intake hole 3268 into rotor chamber 3270. Rotor 3258 spins. As the rotor 3258 rotates, the effective volume of the rotor chamber 3270 decreases. The rotor 3258 is offset from the axis Z. Thus, the steam is directed to the outlet holes 3272 of the rotor 3258. As it is transported along the rotating path, it is compressed to a pressure P2. As the pressure increases, the outlet hole 2 coincides with the outlet 3274 of the stationary outlet 3264, and the steam at pressure P2 , through outlet 3274 into outlet 3264 which sends it to the evaporator / condenser. In such an embodiment, the rotating housing 3254 is configured to mix with the water 3276 present in the chamber 3260. This reduces the friction energy loss due to windage. to exit and / or enter chamber 3260, thereby There is a small hole 3278 in the housing 3254 to control the fluid level in the pump. In addition, the rotor 3258 may be configured as shown in FIG. The rotor chambers 3270, 3280 are easily visible when viewed from above. and individual intake holes 3268 and exit holes 3272 for each rotor chamber 3270. This is also easily seen from this figure.

[0216] Referring to FIG. 32H, an alternative embodiment of a liquid ring pump is shown, which includes a rotating housing 3254 and The interface between the rotor 3256 and the stator 3256 is conical rather than cylindrical. The rotor drive shaft 3282 rotates the rotor housing 3254 together with the rotor 3258. The intake 3262 and the end 3286 are disposed on a bearing 3284, which allows the intake 3262 and the end 3286 to be and outlet 3264, along with corresponding inlets 3266 and outlets 3274, form rotor 32. 58 and the rotor housing 3254 is held stationary relative to the rotor housing 3254.

[0217] Referring now to Figures 32F, H, and I, another further embodiment includes a stationary portion 326 4 and 3262 and the rotor 3258, and the conical or axial seal 32 82. In a conical embodiment, most clearly seen in FIG. The seal 3282 separates the intake 3266 from the outlet 3274 of the rotor 3258. Prevents leakage. Axial supply, axial discharge. Discuss with reference to Figures 32-32C. In contrast to the liquid ring pump embodiment shown in Figs. 32E-I and 7 The liquid ring pump is axially fed and radially discharged.

[0218] In an alternative embodiment, the water vapor distillation apparatus may include a back pressure regulator. It may also help maintain safe and optimal operation of processes that are carried out under pressure. The steam distillation apparatus may include a back pressure regulator to purify brackish or seawater into potable water. , excess equipment generated from volatile components during start-up or from compressors operating off-spec Pressures can be dangerous to operators if such pressures are not safely relieved. Similarly, volatile components present in the feed stream during start-up can contaminate the equipment and prevent proper operation. The back pressure regulator relieves excess pressure and allows the actuator to operate at the desired speed. It may also serve to return the pressure to the operating pressure.

[0219] The steam distillation apparatus embodiments described above generally operate at atmospheric pressure, typically about 10 psig. Such devices advantageously provide higher vapor densities at higher pressures. This allows more steam to be pumped through the positive displacement pump than would be possible at a lower pressure. The resulting higher throughput allows for an overall improved system Additionally, higher throughput and higher system pressures reduce the compressor requirements. This reduces the power required and allows for two additional pumps, one for pumping the concentrated product. Eliminates the need for pumps to pump in and out of the pump. Many configurations require more pressure than external pressure. It has good resistance to internal pressure, simplifying the overall structure. This reduces the impact of minor leaks on overall efficiency and performance. Condensable gases inhibit the condensation process and expand below atmospheric pressure, where a minor leak can cause an air leak. This serves to draw in air, something that does not occur in systems operating at superatmospheric pressure. be.

[0220] Referring now to Figures 33 and 33A, these figures show the operation of the device above atmospheric pressure. 1 shows a diagram of a back pressure regulator that may sometimes be incorporated into the water vapor distillation apparatus 100. 300 has a container 3302 containing an opening 3304. One side of the opening is insulated. Pressurized conduits of equipment that may be constantly exposed to fluctuating high pressures (e.g., in vapor compression distillation equipment) The other side of the opening is connected to the outlet of the compressor. The port 3306 is covered by a spherical movable stop 3308. The stop 3308 , held to arm 3310 by means of retainer 3312 at a fixed distance from pivot pin 3314. The arm 3310 is hinged via a pivot pin 3314 to the opening port 3316. The arm 3310 is attached to a point in fixed relation to the counter mass 331. 6 and pivot pin 3314 may be varied. Possibly, a counter mass 3316 is included suspended from the arm. In this embodiment, the axial direction of the opening 3304 is perpendicular to the direction 3320 of the gravity vector. The pressure regulator also prevents foreign objects from entering the regulator and interfering with the function of the internal components. , may include a housing.

[0221] Still referring to Figures 33 and 33A, in operation, the pressure in the pressurized conduit rises to a given set point. If the arm 3310 is below this value, it will maintain a horizontal position relative to the direction of gravity 3320. The arm position is known as the closed position in this embodiment and stops covering the port 3306. When the pressure in the conduit exceeds a set point, a force acts on stop 3308. , resulting in a torque acting around the pivot pin 3314. The torque acts in a counterclockwise direction It acts to rotate the arm 3310 about the pivot pin 3314, moving the arm to its closed position. 3306. The fluid is then removed from the opening 3304. When the pressure in the conduit is below a set point, the gas force moves the arm 3310 to its It is no longer sufficient to keep the arms 3310 away from the closed position, and therefore the arms 3310 are closed. Returning to the leash position, stop 3308 covers port 3306 .

[0222] Still referring to Figures 33 and 33A, arm 3310 provides an adjustable moment. The counter mass 3316 acts as a lever when generating the stopper 3308. This force multiplication acts to multiply the force applied to port 3306 through the pressure cooker. As in the case of a design in which only the stop 3308 acts vertically on the top of the opening 3304, In contrast, it reduces the weight required to close the opening 3304. The mold port size is relatively light and large to facilitate rapid venting from the pressurized conduit. The counter mass acts to adjust the desired set point, particularly Less design effort is expended in selecting certain port sizes and stop properties. The addition of the shaft 3318 for adjusting the position of the counter mass 3316 is also possible in this embodiment. allows for a change in the multiplier ratio. The counter mass 3316 is closer to the pivot pin 3314. As the counter is moved to a position, the multiplier ratio is reduced, producing a lower closing force. If the base 3316 is moved further from the pivot pin 3314, the multiplier ratio is increased, thus Therefore, the position of the counter mass 3316 is determined by the setting of the back pressure regulator. It effectively acts to adjust the fixed point.

[0223] Adjusting the backpressure regulator set point is useful when the backpressure regulator is utilized at higher altitudes. When atmospheric pressure is lower, the system operating pressure is correspondingly lower. The temperature of the device will be reduced, which may adversely affect the performance of the device. Such adjustments allow identification of the backpressure regulator set point desired by the end user. The use of a counter mass to apply the closing force also reduces the cost of the back pressure regulator. , which may reduce fatigue of the components. In certain embodiments, an adjustable counter mass may Minimum set point substantially below 10 psig and maximum set point substantially above 17 psig Therefore, various embodiments are designed to accommodate a range of set points that may be involved. Unlike devices that act as total relief valves, this allows for precise system pressure regulation.

[0224] Referring now to Figures 33B-C, these figures show the port 3328 facing in the direction of gravity 332 0. A back pressure regulator 330 having an opening 3326 configured to be oriented perpendicular to the 0. Thus, other embodiments may include an adjustable counter mass. Any opening orientation may be accommodated while maintaining use.

[0225] The back pressure regulator acts to isolate the heat exchange and suppress boiling in the system. It is configured to allow a small leak rate below a set point to clear any buildup of volatile gas. However, the regulator must be able to ensure that pressure is not lost despite this slight leakage. In one embodiment, the back pressure regulator is designed to allow for a gradual build-up in the tubing. Below this set point, the release of volatile components from the pressurized conduit also occurs when the back thickness adjuster arm is in the closed position. This may be achieved through a specially designed leak vent while the device is in place. Allowing a certain leak rate from a port or opening while the pressure in the conduit is below a set point Such leakage vents may be designed by various means known to those skilled in the art. Non-limiting examples include stops and closures that allow a small opening while the arms are in the closed position. and specific positioning of ports, so that small openings that cannot be covered by stops are always exposed. a step of designing the port so that the stop and the port are in contact when the arm is in the closed position; specifying a particular stiff, inelastic seal configuration between the valve and the valve, and allowing fluid leakage. The method includes configuring the opening to the port to have a small opening to accommodate the fluid.

[0226] Referring now to Figures 33D-G, these figures show the effect of allowing volatiles to escape below the set point. 3 illustrates an alternative embodiment of back pressure regulator 3300. In one alternative embodiment, port 3 332 has a notch 3334 as shown in FIG. 33D, an enlargement of region C of FIG. 33D. A view is shown in FIG. 33E. Therefore, when the stop is in contact with the port 3332 , the back pressure regulator arm is in a closed position, and the leak vent is a notch that allows fluid to escape. In another alternative embodiment of the backpressure regulator 3300, the opening 333 6 has a small opening 3338 as shown in FIG. 33F, and an enlarged view of area E of FIG. 33G. The opening 3338 allows fluid to escape through the opening 3338. Therefore, when the stop covers the port 3336, a leakage vent is created. can be.

[0227] Various features of the back pressure regulator may be altered or modified. For example, along with the back thickness regulator The stops used may be of any shape, size, or mass consistent with the desired operating conditions. Such stops may be shown in some of the embodiments discussed herein. Similarly, different weights can be used to alter the regulator set point. Similarly, stops of similar size may be utilized with the retainer. and arm configurations accommodate different sizes, shapes, and qualities. A counter mass of a certain amount may be utilized with various embodiments (see 3 in FIGS. 33 and 33A). (Compare 316 with 3330 in Figures 33B and 33C). The can be attached to the arm by any of a variety of techniques that will be apparent to those skilled in the art. The pivot pin arrangement may be arranged as shown in Figures 33-33C. It is not necessary, but it does provide the mechanical advantage required to achieve a particular pressure set point. The device may be located wherever it is advantageous to do so.

[0228] Referring again to FIG. 33, another embodiment of the backpressure regulator 3300 may optionally include the drainage system described above. Additionally, embodiments of the back pressure regulator 3300 may utilize counter mass force adjustment. feature and rely on the specific nature of the stop to provide the backpressure regulator set point. It exists.

[0229] Other embodiments of the water vapor distillation apparatus may not utilize a vessel, but essentially In such cases, the back pressure regulator arm may be configured with an arm, a stop, directly to a portion of the system so that the counter mass is properly oriented for regulator operation. It may be attached.

[0230] 34, the container 3302 includes a drain port 3322. 3400 may operate within a bounded area 3402 of a large system 3400, 22 is swept from pressurized conduit 3404 through opening 3304 into bounded area 3402. The drain 3322 acts as a passageway for the discharge of fluid from the bounded area 3402. , to another area of ​​a larger system, or to the external environment 3406. The accumulation of gases in the boundary region 3402 may result in condensation of such gases. The gas swept through the mouth 3304 dissolves droplets of fluid that may accumulate in the bounded area 3402. Therefore, the drain 3322 also allows the water to accumulate in the bounded area 3402. This may be utilized to clear away any condensation buildup. Condensate may also be removed through separate openings 3408. may be emitted from the bounded region using

[0231] Referring now to FIG. 35, in an alternative embodiment, the device may maintain a constant discharge water flow, Debris and other buildup in the device may be prevented as follows: Head chamber 35 The water level 3502 in the reservoir 04 is maintained at a level A feedback control loop is used to control the flow rate of the feedstock using sensor L1, valve V1, and feedstock pump 3506. The three-way feed pump fill valve 3510 directs water into the water reservoir 3512. The head chamber 3504 is set to fill with water, which raises the water level 3502 in the head chamber 3504. As the fluid level 3502 in the head chamber 3504 rises, the fluid 3514 and into the emission control chamber 3516 containing the emission level sensor L1. If necessary, water flows from the emission control chamber 3516 through a heat exchanger 3518 to The effluent stream 3508 is cooled and passes through a volatile mixer 3520 and out of valve V1. The discharge valve V1 is controlled to allow hot gas from the evaporator section 3524 and The vapor 3522 is allowed to cool and then completes the discharge flow to waste 3526 .

[0232] Still referring to FIG. 35, the system may also maintain proper production flow as follows: The product level 3528 increases in the condenser chamber 3530 and is detected by the product level sensor. The level sensor L2 and the product control chamber 3532 are housed in the product control chamber 3532. A feedback control loop is used with valve V2 to control the flow rate from product control chamber 3532. The product stream 3534 flows through a heat exchanger 3518 to extract heat and cool the product stream 3534, which is then cooled by a valve The product flow is completed by passing through V2 and exiting as the product water outlet 3536. 3534 is controlled.

[0233] The system preferably uses a fluid recovery system to replenish fluid losses. The lower reservoir may be configured to maintain the proper water level in the liquid ring pump 3538. The system is free from leakage into the reservoir 3540, evacuation through the exhaust port 3542, and evaporation. There are several ways in which the ring pump can become starved of fluid during system operation. The leakage and rejection losses depend on the operating parameters, such as the rotational speed and throughput of the liquid ring pump 3538. These leakage and elimination losses can be significant and can occur several times per hour. This may require a complete replacement of the fluid in the tank. Evaporative losses are typically small.

[0234] Referring to FIG. 35, the fluid level in the ring pump 3538 may be increased by adding additional source or product water. or preferably, by adding a liquid ring pump for improved system efficiency. This may be maintained by recirculating liquid water lost from the pump. The fluid level in the ring pump 3538 is primarily determined by the regeneration of fluid accumulated in the lower reservoir 3540. The fluid is maintained by leakage from the liquid ring pump 3538 and by the exhaust It is discharged into pipe 3542, captured by mist eliminator 3544, and sent to lower reservoir 3540. The trapped fluid may accumulate in the lower reservoir 3540. Alternatively, the exhaust pipe 3542 The discharged fluid trapped in the mist eliminator 3544 is discharged through the liquid ring pump exhaust port. The fluid accumulated in the lower reservoir may be pumped into one of several pumping mechanisms. One exemplary method is to use a siphon pump. be.

[0235] Still referring to FIG. 35, the minimum depth of water is preferably determined by the amount of water required for the siphon pump to function properly. In one embodiment, the liquid ring pump is maintained in a lower reservoir to function. The liquid ring pump level sensor L3 is housed in order to control the water level in the lower reservoir 3540. A liquid ring pump control chamber 3546 may be used to house the liquid ring pump control chamber. The reservoir 3546 is fluidly connected to the liquid ring pump 3538 and the lower reservoir 3540. The ring pump 3538 opens when the liquid ring pump 3538 needs more water. and a liquid ring pump 3538. A liquid ring pump drain valve that opens when required to discharge water into the discharge stream 3508 It is also connected to V3.

[0236] Still referring to FIG. 35, to maintain the fluid level in the liquid ring pump 3538, If recirculated water from lower reservoir 3540 is not primarily used, either cold source water or product water may be used. If source water is used, cold water (system The introduction of a refrigerant (which can be approximately 85°C lower than the system temperature) reduces system efficiency or The use of a preheater for such low temperature source water increases the energy balance of the system, as Alternatively, using product water will not adversely affect system temperatures, but will reduce production levels. During start-up, the initial pressure of the liquid ring pump decreases, which can lead to system inefficiencies. The fluid level is preferably supplied from a source of water.

[0237] Referring now to FIG. 35A, in one embodiment, adjacent to the cold side heat exchanger 3518 Using an external connection valve 3550 located between the feed 3548 and discharge 3508 fluid lines Start-up time may be reduced by increasing the temperature of the vaporizer head 3504 during the initial fill. To determine the fluid level in the feedstock, open the connection valve 3550, close the discharge valve BV, and Fluid is pumped into the system through the inlet 3548. The outlet 3508 and the source 3548 Connecting the lines connects the emission level sensor housing 3516 and the evaporator head 350 4, thereby providing an equal fluid level in the evaporator head 3504. This allows for the determination of the minimum required level at start-up. By using the minimum level required, preheat time is reduced and the Also, when the liquid ring pump 3538 starts, the liquid ring pump 35 38 to prevent overflow into the condenser 3552.

[0238] Still referring to FIG. 35A, the precipitation of material from solution and therefore clogging of the system can be prevented. The concentration of solids in the effluent stream 3508 may be monitored and controlled to prevent During startup, the circulation pump 3554 circulates water through the heat exchanger 3518, ensuring normal operation. The heat exchanger may be preheated to the proper temperature for this purpose. A conductivity sensor (not shown) may be used to determine total dissolved solids (TDS) in the water. In certain embodiments, the sensor is an inductive sensor, whereby any conductive The material is also not in contact with the fluid flow. For example, during the distillation of seawater, the TD in the discharge stream 3508 If the S content rises above a predetermined level, the supply rate of the fluid source is increased. As distilled water production varies only slightly as a function of temperature, increasing the feed rate of the fluid source As the flow rate increases, the velocity of the discharge stream 3508 increases, and the increased discharge stream velocity results in a reduced concentration of TDS. degree, thereby maintaining the overall national and productivity of the system.

[0239] An alternative embodiment also uses a level sensor and a variable flow valve in a feedback configuration. This includes the fluid control system. Optimal operation of the distiller is when the total fluid inflow closely matches the total fluid outflow. Maintaining a nearly constant fluid level in the still meets this requirement. In certain embodiments, the sensor is a capacitive level sensor that measures the fluid level. Capacitive level sensors have no moving parts and are highly resistant to contamination. The opening of the variable flow valve is controlled by a capacitive level sensor. The fluid level is controlled by the level of the fluid measured by the level sensor. The rising fluid level causes the valve to open further, releasing fluid from the sensor volume. Conversely, a falling fluid level will cause the valve to close further, increasing the outflow from the sensor volume. Reduce the outflow of

[0240] The flow rate from the input pump through the variable flow control valve is determined using an in-situ calibration technique. A level sensor and associated level sensor may be used to determine the rate at which the sensor volume is filled or emptied. By properly configuring the control valves, the flow rate of each valve can be controlled. The calibration, and also the flow rate calibration of the feed pump may also be determined.

[0241] In one embodiment, all control valves in the system may be integrated into a single fluid flow manifold. A valve block (not shown) may be utilized for integration into the component. Other devices for controlling the height / level of fluid in the tank as well as for total dissolved solids. A control system, including sensors and discharge flows, may also be incorporated.

[0242] Referring again to FIG. 35, in addition, the steam flow line from the head 3504 to the compressor 3538 in 3554, a steam outlet 3542 for bypassing the steam to the evaporator / condenser, From the condenser, the exchanger 3518 also allows for the collection of the hot purified condensate product 3528. hot product line 3534, and diverting the hot product to compressor 3538 to There is a line (not shown) to allow the adjustment of the system to be kept constant. There may be a drain line (not shown) for when the pump is turned off.

[0243] 36-36C, an alternative embodiment also provides a fluid distribution manifold 3600. FIG. 36 illustrates the pump side of one particular embodiment of a fluid distribution manifold 3600. An input in the form of raw material feed flows through port 3602 and a discharge stream (outlet The output (power) flows through port 3604. Additional output in the form of product flow flows through port 3606. Port / chamber 3608 provides a vent for volatiles (output) while flowing through Port 3610 provides the outlet (output) for the liquid ring pump. 3 shows the other side of the pump side of the same particular embodiment of distribution manifold 3600. The port / chamber 3608 for the output of volatiles is clearly visible, as is the drain 3610 for the In this view of this particular embodiment, the mist collector and drainage area 3614 is , the condenser vapor mist eliminator chamber 3612 can be seen.

[0244] Referring specifically to FIG. 36B, this figure illustrates the same particular implementation of a fluid distribution manifold 3600. The evaporator / condenser side of the configuration is shown. The exit port 3604 and the product port 3606 are easily visible in this view. In addition, the evaporator vapor passage port 3616 and the condenser vapor passage port 3618 can be seen. It is possible.

[0245] Referring specifically to FIG. 36B, this figure illustrates the same particular implementation of a fluid distribution manifold 3600. The other side of the evaporator / condenser side of the configuration is shown. Again, the liquid ring pump drain port 3606 , a second condenser vapor mist eliminator 3612, an evaporator vapor mist eliminator 3620, and a The discharge passage port 3604 can be seen, as can the storage collector and drainage area 3614. Also, along with product level control chamber 3622 and liquid ring pump supply 3624 The sump level control chamber can be seen in this view.

[0246] Still referring to Figures 36-36C, a fluid distribution manifold 3600 may be provided to provide a fluid purification system. It is possible to eliminate most of the piping system in the Advantageously combines various functionalities, including pressure regulation, into one unit, thereby simplifying production Simplify and reduce overall component parts. The core plate and manifolds are made of, for example, plastic. , metal, or ceramic plate, or any other material capable of withstanding high temperatures and pressure. The core plate and manifold may be made of non-corrosive materials. Includes outer coating.

[0247] Referring now to Figures 37-37A, these figures illustrate the system in a specific embodiment. 1 illustrates a fitting assembly that allows fluid to contact throughout the entire system. The diverter 3518 (shown in FIG. 35) and the intake / exhaust ports 3220 and 3208 (shown in FIG. 32) 37A shows the heat exchanger ports (not shown) and the floating fluid between them. 37 shows a connector 3702 that may be welded to the fluid interface 37 04, and the fluid interface then communicates with the fluid distribution manifold. 37 shows a cross section through -A (see FIG. 37). Connector 3702 is resistant to temperature or manufacturing variations. Ability to float to compensate for alignment shifts that may be caused by movement The seal is completed by an O-ring 3706. Thus, when the O-ring seal 3706 is rotated 90 degrees around the central axis along the line AA, Connector 3702 and fluid interface 3704 lock together to provide a fluid interface connection.

[0248] Referring now to Figures 38-38A, these figures show another embodiment of an evaporator / condenser 3800. As can be seen in FIG. 38, the evaporator / condenser 3800 is a flat evaporator. / Condenser, typically made of copper-nickel alloy or other heat-conducting material, The core 3802 and 3804 are parallel to each other and have a rib portion 3806 for facilitating vapor and condensate flow. This creates channels 3810 and 3812 for directing fluid flow. 3814 and product outlet 3816 manifolds (as well as contamination intake and and volatiles outlet manifold) may be connected to the liquid ring pump / compressor via a fluid interface. Bolt 3818 attaches the evaporator / condenser core to the bracket on the outer housing of the liquid ring pump / compressor. 3800. In operation, all alternate horizontal (as shown in Figures 38 and 38A) Columns 3802 and 3804 ensure that no two functions overlap on any given layer. , evaporator channels 3810 and condenser channels 3812. , FIG. 38A shows more clearly how the combined evaporator / condenser manifold works. As shown, column 3802 does not interact with column 3804 and is mutually closed. This separates the functions of evaporation and condensation in the horizontal core layer.

[0249] Referring now to Figure 39, this figure shows an alternative embodiment of a heat exchanger for use in a steam distillation apparatus. The embodiment shown in Figure 1 makes full use of available system and heat resources. In one particular embodiment, heat from at least one of the sources is 3904, 3906, 3908 through a multi-line heat exchanger 3902 such as that shown. A series of two-channel heat exchangers such as the 3910 and 3920 are piped to create a multi-line effect. In the particular multi-line heat exchanger embodiment shown in FIG. 2 passes through all heat exchanger units 3904, 3906, 3908, and 3910; One heat source, e.g., hot product 3914, passes through heat exchanger units 3904 and 3908. and another heat source, e.g., hot exhaust stream 3916, flows through heat exchange units 3906 and 3907. Note that the cold intake stream 3912 flows through 910. To achieve this, multiple heat sources may be used.

[0250] Referring now to Figure 39A, this figure illustrates an alternative embodiment of the heat exchanger. In an embodiment, the heat exchanger may be a single multi-channel heat exchanger 3918. In certain embodiments, a heat source, such as a cold intake 3912 and a hot output 3914, and hot bleed stream 3916 flows simultaneously but in opposite directions through exchanger 3918; This allows for the exchange of cold heat from both heat sources 3914 and 3916 in a single heat exchanger 3912. Allows heat exchange with intake 3912.

[0251] Referring now to FIG. 40, one alternative embodiment evaluates overall system performance. and / or to provide data to a control system. The step of measuring the force required to withstand the high temperature of the evaporator / condenser 4002 may be included. To avoid the need for expensive sensors, the pressure sensors PE and Pc are installed on the fluid line between the cold side of the reservoir 4004 and the corresponding control valves VE and VC. This occurs when fluid flows against a pressure sensor located at this location. To avoid measuring a pressure lower than the actual pressure of the During the "no flow" period, pressure is returned from the control valve to the evaporator or condenser. These short "no flow" periods allow accurate measurement of system pressure. These do not have any adverse effect on the performance of the still.

[0252] Referring now to Figures 41-41B, this figure shows the effect of increasing the purity of the final product fluid. 1 illustrates another embodiment of the present disclosure including a filtering mechanism within the intake for at least two filters. A multi-unit filter assembly having a pivot joint 4102 joining filter units 4104 and 4106. The flip-top filter 4100 allows fluid to pass through the filter units 4104 and 4106. and orienting the filter units 4104 and 4106 around the central pivot joint 4102. As shown, the discharge flow 41 is disposed within a filter housing 4108 that facilitates rotation of the filter. 4109 passes through the flip filter unit 4104, while the intake fluid stream 4110 passes through the flip filter unit 4104. At times, the water flows from the intake through the flip filter unit 4106 during purification. After a certain interval, a flip filter switch (not shown) flips the filter pivot joint 410 2, the flip filter 4100 is rotated around the central axis indicated by the dotted line. To do this, the filter unit 410 is contaminated with contaminants filtered from the contaminated intake fluid. 6 is backwashed by the discharge stream 4109 and the filter unit 4104 is backwashed by the intake fluid stream 41 In such an embodiment, the O-ring gasket 4112 and 4114 are connected to the filter units 4104 and 4106, respectively. may be used as a seal between the fluid flow paths of flow 4109 and intake fluid flow 4110. .

[0253] Referring now to Figures 41C-D, the multi-unit flip filter is a multi-section annular flip filter. The filter 4112 may be a filter having multiple flip-flops around it, such as 4116 and 4118. A multi-unit flip filter 4114 having a pivot point 4114 about which the filter units pivot. 112 also directs fluid flow through the individual filter units 4116 and 4118. The filter housing 412 is configured to rotate about a pivot point 4114, facilitating rotation of the filter 4112. As shown, the discharge flow 4109 may be placed in one flip filter unit. While passing through unit 4116, intake fluid stream 4110 simultaneously passes through the intake port. On the way, it flows through a flip filter unit 4118. As shown in Figure 41, A filter switch (not shown) is shown by the dotted line at the flip filter pivot point 4114. The flip filter 4112 is rotated about the central axis shown in FIG. The filter unit 4118, which is contaminated with contaminants filtered from the Thus, the filter unit 4116 is backwashed, filtering the intake fluid stream 4110. The discharge flow 4109 that flows through one filter section is then filtered out by another filter section. individual filter units 4116 to separate from the intake fluid stream 4110 flowing through Between 4118 and 4119, a series of seals such as those shown by 4122 and 4124 It will be used.

[0254] Referring now to Figures 41E-41F, other embodiments may be implemented to modify the reporting of water flow. Manual valves 4122 may be included. Such valves may be, for example, one for each flip filter. Allows use of the discharge stream 4109 to continuously clean the unit, in one operation It effectively switches which units are being filtered and which are being backwashed, This allows the filter unit 4100 to be replaced without actually having to replace the filter 4100 itself. 4 or 4106. In one particular embodiment, when valve 4122 is in position A, The filter unit 4104 filters the intake fluid 4110. 106 is backwashed with discharge flow 4109. Switching valve 4100 to position B The filter unit 4104 is backwashed with the effluent 4108 and the filter unit 4106 is backwashed with the inlet The force fluid 4110 is filtered. (Stirling cycle engine) The various embodiments of the water vapor distillation apparatus described above may, in some embodiments, be Stirling It may also be powered by a Stirling engine (also called a Stirling engine). In an exemplary embodiment, a Stirling cycle machine is incorporated herein by reference in its entirety. Pending patent application bearing attorney docket number 170, filed April 18, 2008, which is incorporated herein by reference. A Stirling engine is described in US patent application Ser. No. 12 / 105,854. However, in other embodiments, the Stirling cycle machines may all be referred to in their entirety. No. 6,381,958, which is incorporated herein by reference. No. 7,310, No. 6,536,207, No. 6,705,081, No. 7,111,46 0, and any of the Stirling cycle machines described in No. 6,694,731. It could be either one.

[0255] Walker, Stirling En, incorporated herein by reference. This is explained in detail in Genes, Oxford University Press (1980). Stirling cycle machines, including engines and refrigerators, have a long technical tradition. The principle underlying the Stirling cycle engine is that equal volumes of gas in a cylinder Heating, isothermal expansion of gas (during which the action is performed by driving a piston), etc. It is a mechanical realization of the Stirling thermodynamic cycle: condensation, cooling, and isothermal compression. For additional background on aspects of Stirling cycle machines and their improvements, see Hargreaves, The Phillips St, incorporated herein by reference. The author discusses the "Swirl Engine" (Elsevier, Amsterdam, 1991). It is being discussed.

[0256] The principle of operation of a Stirling cycle machine is easily explained with reference to Figures 45A-45E, In the drawings, the same numbers are used to identify the same or similar parts. Many mechanical layouts for cyling machines are known in the art and are generally numbered 5110. The particular Stirling cycle machine designated by is shown for illustrative purposes only. In Figures 45A to 45D, the piston 5112 and displacer 5114 are In some embodiments of the cylinder machine, it may be a single cylinder, while in other embodiments it may be a single cylinder. It moves in a stepped reciprocating motion within a cylinder 5116, which may be more than one cylinder. The working fluid contained within cylinder 5116 is guided by seals through piston 5112 and variable The working fluid is restricted from leaking around the positioner 5114. The working fluid is discussed in the following description. The gas chosen for its thermodynamic properties is typically helium at a pressure of several atmospheres. However, any gas may be used, including any inert gas, such as hydrogen, argon, neon, etc. The gases include, but are not limited to, nitrogen, air, and any mixture thereof. The position 114 is the interface where the working fluid receives heat and the interface where the working fluid receives heat. The fluid is contacted with the hot interface 5118 or the cold interface 5120, which corresponds to the interface that is extracted from the fluid. Heat supply and extraction are discussed in more detail below. The volume of working fluid governed by the position of the nozzle 5112 is called the compression space 5122 .

[0257] During the first phase of the Stirling cycle, the starting state of which is shown in FIG. 45A, piston 51 12 compresses the fluid in the compression space 5122. Heat is extracted from the fluid to the surrounding environment. The compression occurs at a substantially constant temperature. The situation is shown in Figure 45B. During the second phase of the cycle, the displacer 5114 direction, displacing the working fluid from the region of the cold interface 5120 to the region of the hot interface 5118. This stage may be called the transfer phase. At the end of the transfer phase, the working fluid is The fluid is heated by the pressure difference and reaches a higher pressure. This is symbolically shown in FIG. 45C by a constant value.

[0258] During the third phase (expansion process) of the Stirling cycle machine, As it receives heat from outside, the volume of the compression space 5122 increases, thereby In practice, the heater head (not shown) is used, which is discussed in more detail below. At the end of the expansion phase, the compression space 5122 is Filled with cryogenic fluid as shown in 5D. 4th stage of Stirling cycle machine 5110 During this time, the fluid is drawn from the region of the hot interface 5118 to the cold interface 5118 by the movement of the displacer 5114 in the opposite direction. At the end of this second transfer phase, the fluid is transferred to the region of the hot interface 5120. As shown, the compression space 5122 and the cold interface 5120 are filled, and the compression phase is repeated. The Stirling cycle is a PV (Pressure-Voltage) cycle, as shown in Figure 45E. This is shown in the volume diagram.

[0259] Furthermore, upon passing from the region of the hot interface 5118 to the region of the cold interface 5120, some In this embodiment, the fluid may be passed through a regenerator (shown as 5408 in FIG. 48). The regenerator absorbs heat from the fluid as it enters from the region of the hot interface 5118 and 5120 area, which has a large surface area to volume ratio that heats the fluid as it passes through. It is a matrix material.

[0260] Stirling cycle machines in general have been hampered by several difficult challenges to their development. These are not used in practical applications due to practical considerations such as efficiency and lifespan. This results in minimal side loads on the piston, increased efficiency and lifespan. There is a need for more Taring cycle machines. (Rocking beam drive) 46-48, an implementation of a Stirling cycle machine according to one embodiment. An embodiment of the engine is generally designated by the numeral 5300. Stirling cycle machines are generally referred to as Stirling engines 5 shown in Figures 46-48. Although described with respect to the 300 embodiment, it also includes a refrigerator and a compressor. Many types of machines and engines are known, including but not limited to external and internal combustion engines. Those skilled in the art will appreciate that the present invention may be practiced with the benefit of the various embodiments and improvements described herein, including but not limited to: Please understand that this is acceptable.

[0261] FIG. 46 shows linearly reciprocating cylinders housed in cylinders 5206 and 5208, respectively. for an engine such as a Stirling engine having moving pistons 5202 and 5204 The rocking beam drive mechanism 5200 (the term "rocking beam drive" is used interchangeably with "rocking beam drive"). 1 shows a cross section of an embodiment of a locking beam drive mechanism (used interchangeably with the "locking beam drive mechanism"). The rocking beam drive 5200 includes a piston 5202 and a linear bearing 5220. The linear motion of 5204 is converted into the rotational motion of the crankshaft 5214. Rocking beam drive unit 5200 includes a rocking beam 5216, a rocker pivot 5218, a first connecting assembly piston 5202 and 5 204 are a first coupling assembly 5210 and a second coupling assembly 521 2, the rocking beam driver 5200 is connected to the rocking beam driver 5200. , and is connected to the crankshaft 5214 via a connecting rod 5222.

[0262] In some embodiments, the first portion of the rocking beam and linkage assembly is The cylinder, piston, and coupling assembly may be located within the engine case. The second portion is located within the workspace.

[0263] In the crankcase 5400 of FIG. 48, most of the rocking beam drive 5200 is The crankcase 5400 is disposed below the cylinder housing 5402. 4, rocking beam 5216, linear bearing 5220, connecting rod 5222, and connecting assembly The rocking beam drive 5200 having bridges 5210 and 5212 is operable. The crankcase 5400 is a space in which the pistons 5202 and 5204 are arranged in a plane parallel to the axis of the pistons 5202 and 5204. The pistons 5202 and 520 intersect the cylinders 5206 and 5208 at right angles. 4 are reciprocated in respective cylinders 5206 and 5208, as also shown in FIG. The cylinders 5206 and 5208 are located above the crankshaft housing 5400. The crankshaft 5214 extends below the cylinders 5206 and 5208. It is installed inside the 5400.

[0264] Figure 46 shows one embodiment of a rocking beam driver 5200. 10 and 5212 extend from the pistons 5202 and 5204, respectively. Pistons 5202 and 5204 connect to rocking beam 5216. Piston 5204 In some embodiments, the coupling assembly 5212 includes a piston rod 5224 and a ring. The coupling assembly 5210 for the piston 5202 may include several In some embodiments, a piston rod 5228 and a link rod 5230 may be included. Ton 5204 moves vertically within cylinder 5208 and is connected by linkage assembly 5212. The cylinder 5208 is connected to the end pivot 5232 of the rocking beam 5216. It provides guidance for the longitudinal movement of piston 5204. The piston rod 5224 of the coupling assembly 5212 is connected to the axis of the cylinder 5208. is driven longitudinally by its link rod 5226 in a substantially linear reciprocating path along The distal end of the piston rod 5224 and the proximal end of the link rod 5226 are connected to several In an embodiment, they are co-hinged via a connecting means 5234. The connecting means 5234 is Flexible joints, roller bearing elements, hinges, journal bearing joints (shown as 5600 in Figure 50) 51A and 51B), and a bend (shown as 5700 in FIGS. 51A and 51B). The link rod 52 may be any connecting means known in the art, but is not limited to these. The distal end of the link rod 5226 is positioned vertically and upright under the proximal end of the link rod 5226. One end of the bearing 5220 may be connected to a pivot 5232 of the bearing beam 5216. further ensures substantially linear longitudinal movement of the piston rod 5224, and therefore Linkage assembly 521 is adapted to ensure substantially linear longitudinal movement of piston 5204. 2. In the exemplary embodiment, the link rod 5226 is connected to the linear bearing 52 20. This means, among other things, that the piston rod 5224 is substantially straight in the longitudinal direction. Ensure that the forward motion is maintained.

[0265] In an exemplary embodiment, the link rod may be made of aluminum, and the piston rod and The link rods, piston rods, connecting rods and The locking beam may be made of 4340 steel. Titanium, aluminum, steel Iron or other materials, including but not limited to cast iron, may be used for the rocking beam drive. In some embodiments, the fatigue strength of the materials used may be improved. is equal to or greater than the actual load experienced by the component during operation.

[0266] Still referring to Figures 46-48, piston 5202 is vertically aligned within cylinder 5206. 5216 by the linkage assembly 5210. 236. Cylinder 5206, among other things, controls the longitudinal movement of piston 5202. The piston rod 5228 of the linkage assembly 5210 serves to provide guidance for Attached to the lower portion of the piston 5202 is a substantially straight line along the axis of the cylinder 5206. The piston rod 52 is driven axially by its link rod 5230 along a reciprocating motion path. The distal end of the link rod 528 and the proximal end of the link rod 5230 may, in some embodiments, be connected to the connecting means 5 238. The connecting means 5238 may, in various embodiments, be flexural. (shown as 5700 in Figures 51A and 51B), roller bearing elements, hinges, A journal bearing coupling (shown as 5600 in FIG. 50), or as known in the art, may be used. The distal end of the link rod 5230 may include, but is not limited to, a connecting means such as In some embodiments, the link rod 5230 is positioned vertically and upright below the proximal end of the link rod 5230. One end of the rocking beam 5216 may be connected to a pivot 5236. The bearing 5220 further ensures substantially linear longitudinal movement of the piston rod 5228, and Therefore, to ensure linear longitudinal movement of the piston 5202, the linkage assembly 52 10. In an exemplary embodiment, the link rod 5230 is Linear bearing 52 is attached to ensure that 5228 maintains substantially linear longitudinal motion. Doesn't go past 20.

[0267] Coupling assemblies 5210 and 5212 couple to respective pistons 5202 and 520 The alternating longitudinal motion of the 4 is transformed into an oscillatory motion of the rocking beam 5216. The vibrational motion is converted into rotational motion of the crankshaft 5214 by the connecting rod 5222, One end of the connecting rod 5222 is connected to the end pivot 5232 of the rocking beam 5216. The connecting pivot 5240 is rotatably connected to the connecting pivot 5240 and is disposed between the connecting pivot 5218 and the connecting pivot 5240. The other end of the connecting rod 5222 is rotatably connected to a crank pin 5246. - pivot 5218 is located substantially at the midpoint between end pivots 5232 and 5236; The rocking beam 5216 is supported as a fulcrum, and therefore each piston The rods 5224 and 5228 may be guided to undergo sufficient linear motion. In this embodiment, the crankshaft 5214 is located above the rocking beam 5216. In other embodiments, the crankshaft 5214 is located below the rocking beam 5216. (as shown in Figures 49B and 49D), or in some embodiments, The crankshaft 5214 is still aligned with the rocking beam 5216 so that it has a parallel axis. 5216.

[0268] Still referring to Figures 46-48, the rocking beam rotates around the rocker pivot 5218. The link rod 5226 and the end pivots 5232 and 5236 follow an arcuate path. The distal ends of the rocking beams 5216 and 5230 are pivoted to the rocking beams 5216 at pivot points 5232 and 5236. , the distal ends of link rods 5226 and 5230 also follow this arcuate path, The angular deviation 5242 of the motion of each piston 5202 and 5204 from the longitudinal axis and and 5244. Coupling means 5234 and 5238 connect piston rod 5224 and Any angular deviation 5242 from the link rods 5226 and 5230 experienced by 5228 and 5244 are configured to be minimized. Essentially, the angular deviations 5244 and and 5242 maintain the piston rods 5224 and 5228 in a substantially linear longitudinal motion. Therefore, the coupling means 5204 and 5202 are arranged to reduce the side load on the pistons 5204 and 5202. 234 and 5238. Any angular deviation 5244 or 5242 is absorbed by further absorbing, and therefore linear movement along the longitudinal axis of, piston 5204 or 5202. to hold the piston push rod 5224 or 5228 and the piston 5204 or 5202 To this end, a stationary linear bearing 5220 is also mounted inside the cylinder 5208 or 5206 or may be disposed along the linkage assembly 5212 or 5210.

[0269] Therefore, taking into account the reciprocating motion of pistons 5202 and 5204, piston 520 The deviations 5242 and 5244 from the longitudinal axis of the reciprocating motion of 2 and 5204 are This leads to reduced pressure, increased friction against the cylinder walls, increased side loads, and reduced component durability. To achieve this, it is important to keep the motion of pistons 5202 and 5204 as close to a straight line as possible. Therefore, the alignment of cylinders 5206 and 5208 and crankshaft 52 14, piston rods 5224 and 5228, link rods 5226 and 5230, and connecting rods The placement of the connecting rods 5222 may affect, among other things, the efficiency and / or volume of the device. As mentioned above, in order to increase the linearity of the piston movement, 5202 and 5204) are preferably mounted in respective cylinders 5206 and as close as possible to the side of 5208.

[0270] In another embodiment for reducing link rod angular deviation, link rods 5226 and 5230 , reciprocating motion substantially linearly along the longitudinal axis of each piston 5204 and 5202. 5202. The angular deviation is the angle from the longitudinal axis of the piston 5204 or 5202. The numbers 5244 and 5242 define the deviation of the link rod 5226 or 5230. This refers to the angular deviation of link bars 5226 and 5230 as shown in FIG. The position of the linkage assembly 5212 is determined by the position of the end pivot 5232 and the rocking beam 5216. The angular displacement of the link rod 5226 is affected by the length of the distance between the link rod 5226 and the pivot 5218. Therefore, the position of the link assembly is such that the angular displacement of the link rod 5226 is reduced. The link rod 5230 may be a link rod that is The length of 0 also corresponds to the length of the end pivot 5236 and the rocker pivot 521 of the rocking beam 5216. 8, the angular displacement of the link rod 5230 is determined based on the length of the distance between the Therefore, the length of the link rods 5226 and 5230, the connecting assembly The lengths of the assemblies 5212 and 5210 and the rocking beam 5216 are shown in FIG. 6, which greatly affects the angular deviation of the link rods 5226 and 5230. and / or determining, are important parameters.

[0271] The exemplary embodiment has end points 5232 and 5236, rocker pivot 5236, along the same axis. 218 and a straight rocking beam 5216 having a connecting pivot 5240. However, in other embodiments, the rocking beam 5216 may be The curved pistons may be arranged at angles to one another, as shown in You may do so.

[0272] Referring now to Figures 46-48 and Figures 51A-51B, some of the linkage assemblies In this embodiment, the linkage assemblies 5212 and 5210 are axially stiff, but , the locomotion between the link rods 5226 and 5230 and the pistons 5204 and 5202 The locking beam 5216 may include a flexible link rod that is flexible within the plane of the locking beam 5216. In an embodiment, the bends (FIG. Flexure 5700 (shown as 5700 in 51A and 51B) is elastic. The bend 5700 acts as a connecting means between the tension rod and the link rod. absorbs the crank-induced side loads of each piston, thus This flexure 570 may allow linear axial movement to be maintained inside the cylinder. 0 are the link rods 5226 and 5230 and the pistons 5204 and 5202, respectively. In this embodiment, the rocking beam 5216 allows for small rotations in the plane between the rings. Although shown as flat, the flexural bars 5226 and 5230 have a flexural profile that increases their resilience. The bend 5700 is not flat in some embodiments. or near the distal ends of link rods 5226 and 5230. The flexure 5700 may be made of #D reinforced 58-62RC in one embodiment. 2. In some embodiments, the link rods may be made of tool steel to increase their elasticity. Therefore, two or more bends (not shown) may be present on link rod 5226 or 5230. good.

[0273] In an alternative embodiment, the axis of the piston in each cylinder housing is In an exemplary embodiment, the pins in each cylinder housing may extend in different directions so as to be The axes of the stones are substantially parallel and preferably as shown in FIGS. 46-48 and 55A and 55B, the vertical axis is substantially perpendicular. Various embodiments of the rocking beam drive mechanism, including like numbers as shown and described Varying the relative position of the connecting pivot 5240 along the rocking beam 5216 It will be understood by those skilled in the art that the stroke of the piston will vary.

[0274] Therefore, the relative position of the connecting pivot 5240 in the rocking beam 5216, and piston rods 5224 and 5228, link rods 5230 and 5226, locking The length of the beam 5216 and the length of the rocker pivot 5218 parameters change The angular deviation of the link rods 5226 and 5230, the phase of the pistons 5204 and 5202, and and the size of device 5300 may be varied in various ways. So, based on modifying one or more of these parameters, a wide range of piston phase angles can be achieved. and variable engine sizes may be selected. In fact, the link in the exemplary embodiment Rods 5224 and 5228 are at -0.5 degrees from the longitudinal axis of pistons 5204 and 5202. In various other embodiments, the link rod has a substantial lateral movement within +0.5 degrees of the Depending on the length, the angle may vary between about 0 and 0.75 degrees. In other embodiments, the angle may be even higher, including between about 0 degrees and about 20 degrees. However, as the link rod length increases, the crankcase / overall engine The height and weight of the engine increases.

[0275] One feature of the exemplary embodiment is that each piston is formed as a linked assembly. In one embodiment, the piston rod has a link rod extending substantially from the piston rod to the associated piston rod. , the coupling assembly 5212 for the piston 5204 is connected to the piston 5204 as shown in FIG. It includes a rod 5224, a link rod 5226, and a connecting means 5234. More specifically, One proximal end of the rod 5224 is attached to the lower portion of the piston 5204. The distal end of rod 5224 is connected to the proximal end of link rod 5226 by a coupling means 5234. The distal end of the link rod 5226 is perpendicular to the end pivot 5232 of the rocking beam 5216. As described above, the connecting means 5234 may be a joint, hinge, link, or flexure. This may be, but is not limited to, a hologram or other means known in the art. In this embodiment, the ratio of the piston rod 5224 to the link rod 5226 is The angular deviation of the link rod 5226 may be determined.

[0276] In one embodiment of the machine, the engine, such as a Stirling engine, has two or more rotors on the crankshaft. The rocking beam drive unit above is adopted. Now, referring to Figure 52, An under rocking beam drive mechanism 5800 is shown. In this embodiment, the rocking The rocking beam drive mechanism is connected to two rocking beam drives 5810 and 5812. The example embodiment has four pistons 5802, 5804, 5806, and 5808. In this embodiment, the rocking beam drive mechanism 5800 includes a pair of rocking beam drives 58 At least four pistons 5 arranged in a quadrilateral arrangement connected to the pistons 10 and 5812 Used in Stirling engines with 802, 5804, 5806, and 5808 , each rocking beam drive is connected to a crankshaft 5814. However, other In an embodiment, the Stirling cycle engine includes between one and four pistons; In yet another embodiment, the Stirling cycle engine includes five or more pistons. In some embodiments, the rocking beam drivers 5810 and 5812 are Rocking beam drive described above with respect to -48 (5210 and 5211 in Figures 46-48) 5212). In this embodiment, the piston is Although shown outside the cylinder, in reality the piston would be inside the cylinder.

[0277] Still referring to FIG. 52, in some embodiments, a rocking beam drive mechanism 58 00 includes a pair of longitudinally spaced, radiating A single crankshaft 581 having concentric and opposing crankpins 5816 and 5818 4 and a pair of rocking beam drivers 5810 and 5812. Beams 5820 and 5822 are connected to rocker pivots 5824 and 5826, respectively, and 5816 and 5818, respectively. In this embodiment, rocking beams 5820 and 5822 are connected to rocking beam axis 5828. It is tied.

[0278] In some embodiments, a motor / generator is connected to the crankshaft in operative relationship. The motor may be located between the rocking beam drives in one embodiment. In this embodiment, the motor may be externally located. , is used to mean either a motor or a generator.

[0279] FIG. 53 shows one embodiment of a crankshaft 5814. On the crankshaft, a permanent magnet (" A motor / generator 5900 such as a PM generator is disposed. The motor / generator 5900 is Rocking beam drives (not shown, shown in FIG. 53 as 5810 and 5812) or may be located between or within the Rocking beam drives 5810 and 5812 are connected at the ends of crankshaft 5814 so that 12 or may be located outside or external to the

[0280] Motor / generator 5900 drives the rocking beam drive (not shown, 5810 and 581 52) the length of the motor / generator 5900 is The distance between the driving beam and the motor / generator 5900 is limited by the square of the diameter of the motor / generator 5900. , limited by the distance between the crankshaft 5814 and the rocking beam axis 5828. Since the capacity of the motor / generator 5900 is proportional to the square of its diameter and its length, these The size limitations are a limited volume with a relatively short length and a relatively large square of the diameter. "Pancake" motor / generator 5900. The use of 900 may reduce the overall size of the engine, but is imposed by the internal configuration The size restrictions result in a motor / generator with a limited capacity.

[0281] By placing the motor / generator 5900 between the rocking beam drives, the motor / Exposing the Generator 5900 to heat generated by mechanical friction in the rocking beam drive Due to the inboard location of the motor / generator 5900, it is difficult to cool the motor / generator 5900. This makes it more difficult to reduce the heat generated by the motor / generator 5900, and the effect of heat absorbed by the motor / generator 5900 from the rocking beam drive. This can lead to overheating and eventual failure of the Motor / Generator 5900. There may be a connection.

[0282] Referring to both Figures 52 and 53, the internal arrangement of the motor / generator 5900 also includes a Stones 5802, 5804, 5806, and 5808 are rocking beam drives, respectively. The pistons 5802, 5804, 5806 are coupled to the rotors 5810 and 5812. , and 5808 may also lead to a non-equilateral configuration, and the increase in distance may also This also results in an increase in the distance between pistons 5802 and 5804 and pistons 5806 and 5808. Non-equidistant piston placement leads to inefficiencies in the thermodynamic operation of the combustor and heater head. This in turn can lead to a decrease in overall engine efficiency. Non-equilateral piston arrangements can lead to larger heater head and combustion chamber dimensions. be.

[0283] An exemplary embodiment of a motor / generator arrangement is shown in Figure 54A. As shown in Figure 54A: The motor / generator 51000 is connected to the rocking beam drives 51010 and 51012 (see Figure 1). 52) and externally from the crankshaft 51006 The external location is the "pancake" motor / generator (see Figure 53) motor / generator with a length and diameter squared greater than 5900 As mentioned above, the capacity of the motor / generator 51000 depends on its length. and the square of the diameter, and the external motor / generator 51000 The configuration of the external motor / generator 51000 shown in FIG. 54A may have a square of the diameter. may allow the use of a higher capacity motor / generator in conjunction with the engine.

[0284] As shown in the embodiment of FIG. 54A, motors are provided externally to the drivers 51010 and 51012. By disposing the motor / generator 51000, the motor / generator 51000 is It is not exposed to heat generated by mechanical friction between 51010 and 51012. The external location of the motor / generator 1000 further facilitates cooling of the motor / generator, This allows for more mechanical engine cycles for a given amount of time, which This in turn allows for higher overall engine performance.

[0285] In addition, the motor / generator 51000 is disposed on the outside, and the driving units 51010 and 5101 2, the rocking beam drives 51010 and 51012 are not located between 51010 and 51012. In some embodiments, the pistons used are arranged in an equilateral arrangement. Depending on the type of combustor being used, particularly in the case of a single combustor embodiment, the pistons may be equilaterally spaced. The design allows for greater efficiency in the thermodynamic operation of the combustor and heater head, which in turn This allows for higher overall engine performance. The equilateral arrangement of the pistons also allows for a smaller load. The dimensions of the heater head and combustion chamber are also advantageously made possible.

[0286] Referring again to Figures 52 and 53, the crankshaft 5814 may, in one embodiment, be a crankshaft. In various other embodiments, the bearing may be, but is not limited to, a bearing. Each of the concentric ends 5902, 5904 may have The crank pins 5816, 5818 may be offset from the central axis of the crankshaft. To counterbalance any instabilities that the crankshaft 581 may experience, At either end of the crank shaft 5814 (shown as 51006 in FIG. 54A) , at least one counterweight 5906 may be installed. This crankshaft configuration, combined with the beam drive, is used to drive the pistons (5802 and 5803 in Figure 52). 5804, 5806, and 5808) rotate in unison with one revolution of the crankshaft 5814. This feature is further described below. In other embodiments, The crankshaft 5814 (shown in FIG. 54A) is rotated to reduce angular velocity fluctuations for a constant speed. 51006), a flywheel (not shown) may be disposed thereon.

[0287] Still referring to FIGS. 52 and 53, in some embodiments, the crankshaft 5814 and a cooler (see FIG. (not shown) also includes crankshaft 5814 (shown as 51006 in FIG. 54A) and Rocking beam drivers 5810 and 5812 (51010 and 5101 in FIG. 54A) 2). In some embodiments, the cooler may be positioned along the It may also be used to cool the working gas in the cryo-chamber of the cylinder, The cooling device may be configured to cool the beam drive. Various embodiments of the cooling device are described in more detail below. Discuss in detail.

[0288] Figures 54A-54G show several embodiments of the various parts of the machine. As shown, the crankshaft 51006 is connected to the motor through a motor / generator linkage assembly. The motor / generator 51000 is connected to the crankcase 510. 08, the crankcase pressure due to the input fluid is This can result in deformation of the motor / generator 51000 and crankshaft 510. This can lead to misalignment between the crankshaft 51006 and the locking mechanism, causing the crankshaft 51006 to deflect. The beam drivers 51010 and 51012 are connected to the crankshaft 51006. , the deflection of the crankshaft 51006 is caused by the rocking beam drive units 51010 and 51012 Therefore, in one embodiment of the machine, the motor / generator coupling The assembly is used to connect the motor / generator 51000 to the crankshaft 51006 The motor / generator linkage assembly is connected to the rocking beam drive 51010 during operation. and 51012 failures, which may contribute to the motor / generator 51000 and crank This accommodates differences in alignment between the axes 51006.

[0289] Still referring to Figures 54A-54G, in one embodiment, the motor / generator combination assembly The sleeve rotor 5100 of the motor / generator 51000 is connected to the spline shaft 51004. 2 and a crankshaft 51006. 51004 connects one end of the crankshaft 51006 to the sleeve rotor 51002. The reeve rotor 51002 is secured by mechanical means such as press fitting, welding, threading, or the like. Attached to the motor / generator 51000. In one embodiment, the splined shaft 51004 The shaft 5100 includes multiple splines on both ends of the shaft. 4 is a diameter smaller than the outer or inner diameter of the splined parts 51016 and 51018. In yet another embodiment, the splined portion 51014 includes an intermediate, non-splined portion 51014 having a diameter One end portion of the splined shaft 51016 has a second end portion which also includes splines thereon. 51018 has splines that extend a longer distance along the axis than 51018.

[0290] In some embodiments, the sleeve rotor 51002 is The spline shaft 51020 includes an opening 51020 extending along the longitudinal axis. 1004. In some embodiments, the opening 51020 is A plurality of internal splines capable of engaging the splines on one end of the splined shaft 51004. The outer diameter 51028 of the internal spline 51022 is so that the fit between the spline 51022 and the spline on the spline shaft 51004 is loose ( 54E), the outer diameter 51030 of the spline of the spline shaft 51004 The inner spline 51022 and the spline shaft 51004 A loose fit between the spring and the crankcase can be caused by crankcase pressurization. During deflection of the line shaft 51004, the spline shaft 51004 and the rotor sleeve 51002 In another embodiment, the splined shaft 51 The longer splined portion 51016 of rotor 51004 is connected to the inner spline of rotor 51002. 51022.

[0291] Still referring to FIGS. 54A-54G, in some embodiments, the crankshaft 5100 6 has an opening 51 on its end capable of receiving one end of the splined shaft 51004. The opening 51024 preferably accommodates the spline on the spline shaft 51004. The inner splines 51026 are arranged to engage with the inner The outer diameter 51032 is connected to the inner spline 51026 and the spline on the spline shaft 51004. 54F) so that the fit between the spline shaft 51004 is loose. As mentioned above, the outer diameter of the internal spline 51034 may be larger than the outer diameter of the internal spline 51034. The loose fit between 1026 and the splines on the splined shaft 51004 may cause the crankcase During deflection of the spline shaft 51004, which may be caused by pressure on the spline shaft Contributes to maintaining spline engagement between the in-shaft 51004 and the crankshaft 51006 The internal splines 510 on the crankshaft 51006 and sleeve rotor 51002 The loose fit between 26 and 51022 and the splines on the splined shaft 51004 This may contribute to maintaining the deflection of the spline shaft 51004. There may be some misalignment between the shaft 51006 and the sleeve rotor 51002. In some embodiments, the shorter splined portion 51018 of the splined shaft 51004 , engages the opening 51024 in the crankshaft 51006, thus preventing these potential imperfections. This may prevent the occurrence of such a problem.

[0292] In some embodiments, the opening 51020 in the sleeve rotor 51002 is 1020. This arrangement allows the splines to be aligned during assembly. This helps ensure that the line shaft 51004 is properly inserted into the opening 51020. , spline on the spline shaft 51004 and inner spline on the sleeve rotor 51002 This will contribute to maintaining proper alignment between the

[0293] Referring now to Figure 48, one embodiment of the engine is shown. Pistons 5202 and 5204 of 5300 are inserted into cylinders 5206 and 5208, respectively. The system operates between a high temperature chamber 5404 and a low temperature chamber 5406. Between the two, there may be a regenerator 5408. The regenerator 5408 may have a variable density or a variable area. In some embodiments, the regenerator may have a variable density and and area so that the working gas has a substantially uniform flow throughout the regenerator 5408. Various embodiments of the regenerator 5408 are described below, as well as their full July 2003 to Kamen et al., the entire disclosure of which is incorporated herein by reference. U.S. Patent No. 6,591,609 issued on the 17th, and U.S. Patent No. 20 to Kamen et al. This is discussed in detail in U.S. Patent No. 6,862,883, issued March 8, 2005. As the working gas passes through the high temperature chamber 5404, the heater head 5410 heats the gas. This expands the gas and pushes pistons 5202 and 5204 towards cold chamber 5406. As the gas compresses in the cryo-chamber 5406, Thus, pistons 5202 and 5204 are driven at high speeds to undergo the Stirling cycle again. The heater head 5410 may be a pin head, a fin head, or a , folded fin heads, heater tubes as shown in FIG. 48, or as described below. Any other known heater head embodiment, including but not limited to Various embodiments of the heater head 5410 are described below and in their entirety. No. 6,200,000, filed on May 7, 2002, to Kamen et al., which is incorporated herein by reference. Issued U.S. Patent No. 6,381,958 to Langenfeld et al., 2003 U.S. Patent No. 6,543,215, issued April 8, 2004 to Kamen et al. U.S. Patent No. 6,966,182, issued November 22, 2005, and LaRocqu No. 7,308,787, issued December 18, 2007 to Chris et al. is being discussed in detail.

[0294] In some embodiments, the cooler 5412 cools the gas passing through the cryo-chamber 5406. It may be positioned next to cylinders 5206 and 5208 for further cooling. Various embodiments of the device 5412 are described in the following sections and are incorporated herein by reference in their entirety. No. 6,299,299, issued Feb. 5, 2008 to Strimling et al., which is incorporated herein. This is discussed in detail in US Pat. No. 7,325,399.

[0295] In some embodiments, at least one refrigerant may be used to seal the hot section 5404 from the cold section 5406. At least one piston seal 5414 is disposed on pistons 5202 and 5204. In addition, a piston may be provided to help guide the movement of the piston within each cylinder. At least one piston guide ring 5416 guides the pistons 5202 and 520 4. Various types of piston seals 5414 and guide rings 5416 may be arranged on the piston. The embodiments are described below and are incorporated herein by reference in their entirety. , U.S. Patent filed July 19, 2002, issued February 6, 2003 (now abandoned) This is described in detail in application Ser. No. 10 / 175,502.

[0296] In some embodiments, the working gas is pumped into the crankcase 5400, or alternatively At least one piston is provided to prevent leakage into the airlock volume 5420. A piston rod seal 5418 may be disposed against the piston rods 5224 and 5228. The piston rod seal 5418 may be an elastomeric seal or a spring-loaded seal. Various embodiments of the piston rod seal 5418 are discussed in detail below.

[0297] In some embodiments, for example, a rolling diaphragm, as described in more detail below, may be used. In the case of the drum and / or bellows embodiment, the airlock space may be eliminated. In this case, the piston rod seals 5224 and 5228 separate the working space from the crankcase. Seal.

[0298] In some embodiments, airlock gas may leak into the crankcase 5400. At least one rolling diaphragm / bellows 5422 is provided in the piston to prevent The rolling diaphragm 5422 may be located along the tonneau 5224 and 5228. Various embodiments are discussed in detail below.

[0299] Figure 48 shows only two pistons and one rocking beam drive. 5300, the principles of operation described herein are generally as shown in FIG. 58 and number 58. Applying a four-cylinder double rocking beam drive engine, as indicated by 00 Please understand that this is also acceptable. (piston movement) 52 and 55, piston 58 during one revolution of crankshaft 5814. The operation of crankshaft 5814 is shown. By rotating a quarter of a revolution, the piston 5802 reaches the lowest point of the cylinder, also known as top dead center. At the top, piston 5806 is at its mid-stroke upwards, and piston 5804 is also known as At the bottom of the cylinder, known as the bottom dead center, the piston 5808 is As the crankshaft 5814 rotates halfway, the piston 5802 moves downward to the middle The piston 5806 is at the top dead center, and the piston 5804 is at the upper intermediate position. The piston 5808 is at bottom dead center. , piston 5802 is at bottom dead center and piston 5806 is at mid-stroke downwards; Piston 5804 is at top dead center and piston 5808 is at mid-stroke upward. Later, a full revolution of the crankshaft 5814 causes the piston 5802 to move upward. , piston 5806 is at bottom dead center and piston 5804 is at mid-stroke downwards; Piston 5808 is at top dead center. During each quarter revolution, pistons 5802 and 5806 a 90 degree phase difference between pistons 5802 and 5804, a 180 degree phase difference between pistons 5802 and 5804, and There is a 270 degree phase difference between stones 5802 and 5808. 55 illustrates the relationship of the piston to the piston, which is approximately 90 degrees out of phase with the following piston. , the mechanical means of the exemplary embodiment of the transmission of action is shown. A full rotation moves all pistons from the top to the bottom of their respective cylinders. The piston 5802 is connected to the piston 5806 so as to exert an action by the piston 5802. 5804 and then to piston 5808.

[0300] Referring now to FIG. 55 in conjunction with FIGS. 56A-56C, the piston in an exemplary embodiment Referring now to Figure 56A, the cylinder is shown in a linear path. An example of a four-cylinder Stirling cycle machine is shown below, but this is for illustrative purposes only. In an embodiment, the flow path of the working gas contained within the cylinder working space follows a figure eight pattern. Therefore, the production of cylinders 51200, 51202, 51204, and 51206 The space for the cylinder 51200 is, for example, from cylinder 51202 to cylinder 51204. The cylinders are connected in a figure-eight pattern to the cylinder 51208, so that the fluid flow pattern is a figure-eight pattern. Still referring to FIG. 56A, the line BB (shown in FIG. 56C) is , uncoated views of cylinders 51200, 51202, 51204, and 51206 are shown. The 90 degree phase difference between the pistons is The working gas in 1212 can be delivered to the cold portion 51222 of the cylinder 51206. When the pistons 5802 and 5808 are 90 degrees out of phase, the cylinder 5120 The working gas in the warm section 51214 of the cylinder 51200 is delivered to the cold section 51216 of the cylinder 51200. Pistons 5802 and 5806 are also 90 degrees out of phase with each other. The working gas in the warm part 51208 of cylinder 51200 flows into the cold part 51218 of cylinder 51202. Pistons 5804 and 5806 are also 90 degrees out of phase. The working gas in the warm portion 51210 of the cylinder 51202 flows into the cold portion 51204 of the cylinder 51204. Once the working gas in the warm part of the first cylinder is delivered to the second cylinder, Upon entering the cold section, the working gas begins to compress and then enters the second cylinder on its downward stroke. The piston of the compressor pumps the working gas through the regenerator 51224 and the heater head 51226 (FIG. 5 6B) and back into the warm part of the first cylinder. Once inside the warm part of the first cylinder, the gas expands and drives a piston inside that cylinder. The first cylinder moves through the previous regenerator and heater head and into the cylinder. As shown in Figure 56A, the working gas in the cold part of each piston is driven by the Piston 5802 in such a way that the annulus travels approximately 90 degrees prior to the travel of the previous piston. , 5804, 5806, and 5808 are connected in common via drivers 5810 and 5812. This cylinder 51200 is connected to the crankshaft 5814 (shown in FIG. 55). The periodic transfer characteristics of the working gas between 51202, 51204, and 51206 are possible. do. (Rolling diaphragms, metal bellows, airlocks, and pressure regulators) In some embodiments of the Stirling cycle machine, a lubricating fluid is used. Seals are used to prevent leakage from the crankcase.

[0301] Referring now to Figures 57A-59, some embodiments of Stirling cycle machines are The lubricating fluid is pumped through the crankcase (not shown, but components housed in the crankcase are 51304) to prevent leakage from the piston rod 51302 A hydrodynamically lubricated rocking bead utilizing a rolling diaphragm 51300 positioned along the This includes the engine drive and the ingress area of ​​the engine, which may be damaged by the lubricating fluid. The fluid flows into the working space (not shown, but the components contained in the working space are represented as 51306). If the water enters the regenerator 513, it will contaminate the working fluid, come into contact with the regenerator 513, and It is beneficial to contain the lubricating fluid as it can clog the 08. Afram 51300 is reinforced with rubber or woven or nonwoven fabric to provide rigidity. The rolling diaphragm 51300 may be made of an elastomeric material such as rubber. Alternatively, other materials such as fluorosilicone or nitrile with woven or nonwoven fabrics. The rolling diaphragm 51300 may also be made of carbon nanotubes, Alternatively, for example, polyester or KEVLAR® dispersed in an elastomer. In some embodiments, the rolled fabric may be made of shredded cloth, which is a nonwoven fabric with fibers of The moving diaphragm 51300 is connected to the top sealing piston 51328 and the bottom sealing piston In another embodiment, a rolling die as shown in FIG. The ear fram 51300 is supported via a notch in the top sealing piston 51328 .

[0302] In some embodiments, the pressure above the seal 51300 is applied to the crankcase 5130 4, a pressure differential is placed across the rolling diaphragm 51300. The pressure differential ensures that the rolling diaphragm maintains its shape throughout operation. This pressure difference causes the seal 51300 to expand, causing the seal 51300 to act as a dynamic seal. Figure 57A and Figures 57C-57H show how the pressure difference The figure shows how the pressure difference affects the rolling diaphragm. As it moves with the piston 513, the rolling diaphragm 51300 is pushed against the bottom sealing piston 513. 10 and prevents the seal 51300 from the surface of the piston 51310 during operation. Such separation can cause seal failure. The pressure difference As it moves with the ton rod 51302, the rolling diaphragm 51300 This maintains constant contact with the closed piston 51310. The surface always has pressure exerted on it, thereby This occurs to expand the seal 51300 to conform to the surface. In this case, the top sealing piston 51328 contacts the bottom sealing piston 51310 to form a seal. 51300 further maintains the bottom sealing piston 51310 in contact with the rolling type diaphragm. "rolls over" the corner of the earphram 51300. In an exemplary embodiment, the pressure differential is 10 ~15 PSI range. Rolling diaphragm 51300 is crankcase 51304 The smaller pressure in the pressure difference is preferably the pressure at the bottom so that the pressure may be expanded into the In other embodiments, however, the pressure difference is greater than It may have a larger or smaller range of values.

[0303] The pressure difference can be generated by pressurized lubrication systems, pneumatic pumps, sensors, electric pumps, and crankcase 51304 by vibrating a rocking beam to generate a pressure rise in By generating static electricity on a rolling diaphragm 51300 or other similar method The compounds may be produced by a variety of methods, including but not limited to, the use of methods. In some embodiments, the pressure differential is increased to a pressure that is less than or equal to the average pressure in the working space 51306. It is generated by pressurizing the crankcase 51304. In some embodiments, The crankcase 51304 is 10 to 15 PSI below the average pressure of the working space 51306. In various other embodiments, the pressure differential may be less or Further details regarding rolling diaphragms are included below.

[0304] However, referring now to Figures 57C, 57G, and 57H, the Stirling machine 51306. Another embodiment of the present invention is shown in which the airlock volume 51312 is closed to the working volume 51306. The airlock space 51312 is located between the crankcase 51304 and the A certain volume is required to generate the pressure difference required for the function of the rolling diaphragm 51300. In one embodiment, the airlock 51312 maintains the volume and pressure of the workspace 51306. Because the airlock 51312 is completely sealed from the outside, the pressure in the airlock 51312 is equal to the average pressure in the working space 51306. Therefore, in some embodiments, the pressure between the working space and the crankcase is The lack of an effective seal contributes to the need for an airlock. The lock space is eliminated in some embodiments by providing a more efficient and effective seal. Good too.

[0305] During operation, the average pressure in working space 51306 is equal to the average pressure in airlock 51312. One reason the pressure may fluctuate is that during operation, The working space may become hotter, which in turn may cause the airlock and working space to become in fluid communication. This can increase the pressure in the working space and consequently in the airlock. In such a case, the pressure difference between the airlock 51312 and the crankcase 51304 also changes. Rolling diaphragm 51300 may move and cause seal failure Therefore, in some embodiments of the machine, to maintain a constant desired pressure differential between the lock 51312 and the crankcase 51304. The average pressure in the airlock 51312 is adjusted, and the rolling diaphragm 51300 expands. In some embodiments, the flexures remain tensioned and maintain their shape. monitors and manages the pressure difference between the airlock and the crankcase and adjusts the airflow accordingly. To regulate the pressure to maintain a constant pressure difference between the lock and the crankcase. A pressure transducer is used. Various embodiments of pressure regulators that may be used are described below. and Gurski et al., 2002, which is incorporated herein by reference in its entirety. Further details are provided in U.S. Patent No. 7,310,945, issued December 25, 2007. It has been done.

[0306] A constant pressure difference between the airlock 51312 and the crankcase 51304 prevents the pump or by adding or removing working fluid from airlock 51312 via the valve or release valve. Alternatively, the airlock 51312 and crankcase 51304 may be used. A constant pressure difference between the crankcase 51304 and the This may be achieved by adding or removing fluid. The working fluid may be supplied from a separate source, such as a working fluid reservoir. may be added to the airlock 51312 (or crankcase 51304), or The working fluid may be transferred from the crankcase 51304. If this were to be transmitted from the source to Airlock 51312, it could result in engine failure. , lubricant flows from the crankcase 51304 into the airlock 51312 and finally Before entering airlock 51312, to prevent passage into workspace 51306. It may be desirable to filter the working fluid.

[0307] In some embodiments of the machine, the crankcase 51304 is a thermally isolated fluid different from the working fluid. For example, the working gas may be helium or hydrogen. In this case, the crankcase may be filled with argon. In some embodiments, helium is used, while in other embodiments, Any inert gas may be used as described herein. In the exemplary embodiment, the crankcase is a wet pressurized crankcase. In this embodiment, the crankcase is not wet.

[0308] In the exemplary embodiment, the rolling diaphragm 51300 is configured to allow gas or liquid to pass through it. This ensures that the working space 51306 remains dry and the crank The case 51304 is able to retain lubricating fluid and remain wet. Allowing the base 51304 reduces friction in the rocking beam drive 51316 This increases the efficiency and lifespan of the engine. The use of roller or ball bearings in the This further reduces engine noise and The life and efficiency of the engine may be increased.

[0309] Figures 58A-58E show the top and bottom sealing pistons (Figures 57A and 57H between the top mounting surface and the bottom mounting surface (shown here as 51328 and 51310) (shown as 51320 and 51318 in Figure 57A) Rolling diaphragm (51400, 51410, 51412, 51 422, and 51, 424). In an embodiment, the top mounting surface may be a surface of an airlock or workspace, and the bottom The mounting surface may be a surface of a crankcase.

[0310] FIG. 58A shows one embodiment of a rolling diaphragm 51400. 51400 is configured to form a seal between the top sealing piston and the bottom sealing piston. A flat inner end 5140 may be disposed between the top and bottom sealing pistons. 2. The rolling diaphragm 51400 also includes a top mounting surface and a bottom mounting surface. a flat mounting surface that may be disposed between the top mounting surface and the bottom mounting surface to form a seal therebetween. It also includes a flat outer edge 51404. Figure 58B shows another embodiment of a rolling diaphragm. The moving diaphragm 51410 provides additional pressure between the top and bottom sealing pistons. The flat inner end 51406 has a plurality of bends 51408 leading to it to provide adequate support and sealing contact. 1408. FIG. 58C shows another embodiment of a rolling diaphragm. Diaphragm 51412 provides additional support and The flat outer end 51414 has a plurality of bends 51416 that provide a tight seal. include.

[0311] FIG. 58D shows another embodiment of a rolling diaphragm, rolling diaphragm 5142 2 provides an "O-ring" type seal between the top and bottom sealing pistons 51420 and the bead along its inner edge 51420 between the bottom and top mounting surfaces. and a bead along its outer edge 51418 to provide an "O-ring" type seal. FIG. 58E shows another embodiment of a rolling diaphragm, rolling diaphragm 51424 provides additional support and sealing contact between the top and bottom sealing pistons The beaded inner end 51426 includes a plurality of bends 51428 connected to the beaded inner end 51426 so as to Diaphragm 51424 also provides additional insulation between the top and bottom sealing pistons. Multiple flexures leading to the beaded outer end 51432 provide adequate support and sealing contact. It may contain 51430 songs.

[0312] 58A to 58E show various embodiments of the rolling diaphragm. The ram may be held in place by any other mechanical means known in the art. I would like you to understand this.

[0313] Referring now to FIG. 59A, a cross section shows one embodiment of a rolling diaphragm embodiment. Metal bellows 51500 are used to secure the working space or airlock (51306 and 51306 in Figure 57G). and 51312) to the crankcase (shown in Figure 57G as 51304) The metal bellows 515 is arranged along the piston rod 51502 so as to seal the piston rod 515. 00 is attached to the top sealing piston 51504 and stationary mounting surface 51506. Alternatively, the metal bellows 51500 may be connected to a bottom sealing piston (not shown) and In one embodiment, the bottom stationary mounting surface may be attached to a top stationary mounting surface. The top surface may be the surface of the rank case, or the surface of the inner airloc...

Claims

1. A feed fluid inlet; 1. An evaporator-condenser apparatus comprising: a substantially cylindrical housing; a plurality of tubes in the housing, an evaporator portion disposed inside the plurality of tubes and a condenser portion disposed between the tubes and the housing, the feed fluid inlet fluidly connected to the evaporator portion where the feed fluid is converted to vapor and sent to a compressor; a condenser section for converting compressed vapor received from the compressor into a product fluid; an evaporator-condenser apparatus comprising: a heat exchanger fluidly connecting the feed fluid inlet to the evaporator section and the condenser section to a product outlet; a vent valve fluidly connected to the condenser portion; a temperature sensor disposed in the evaporator portion; 11. A control system for controlling a fluid vapor distillation apparatus comprising a vent control configured to open and close the vent valve and receiving a temperature signal from the temperature sensor, the control system comprising: an idle state in which at least one controller is not operating; an injection state in which the raw material valve is opened and the raw material fluid enters the water reservoir of the fluid vapor distillation apparatus; a heating state in which a heater in the water reservoir is operated at maximum output until the fluid in the water reservoir reaches a predetermined temperature; a heat exchanger peak condition in which the feed valve is opened to a predetermined duty cycle; a start pump state in which the compressor starts and the vent valve operates; an operating state in which the fluid vapor distillation apparatus produces product water; a flow metering state for measuring the time it takes to fill the product to a given value after emptying the product collection vessel to a certain level; a control system for controlling the fluid vapor distillation apparatus, the control system further comprising an operating state including: A fluid vapor distillation apparatus comprising:

2. 2. The apparatus of claim 1, wherein the heat exchanger is disposed about the periphery of the housing of the evaporator-condenser unit.

3. 3. The apparatus of claim 1 or claim 2, wherein the heat exchanger further comprises an outer tube for a feed fluid flow path and at least one inner tube for a product fluid flow path.

4. 4. The apparatus of claim 3, wherein the heat exchanger further comprises at least three inner tubes.

5. 5. The apparatus of claim 4, wherein said at least three inner tubes are intertwined to define a substantially helical configuration.

6. 6. Apparatus according to any one of claims 1 to 5, characterized in that the heat exchanger includes two ends, each end being fitted with a connector, said connector forming a coupling with an evaporator-condenser arrangement.

7. 7. The apparatus of any one of claims 1 to 6, wherein the evaporator-condenser arrangement further comprises evaporator-condenser tubes having a packing on the inside of the tubes.

8. 8. The apparatus of claim 7, wherein the packing is a rod.

9. 9. The apparatus of any one of claims 1 to 8, wherein the evaporator-condenser arrangement further comprises a vapor chest fluidly connected to a plurality of tubes.

10. The apparatus of claim 1, wherein the compressor further comprises an impeller assembly driven by a magnetic drive coupling.

11. 11. The apparatus of any one of claims 1 to 10, wherein the fluid steam distillation apparatus further comprises a conductivity meter and a conductivity cell for measuring the conductivity of the product fluid.

12. 2. The apparatus of claim 1, wherein the vent control varies a duty cycle of the vent valve based on the temperature signal and the operating state of a control system for controlling the fluid vapor distillation apparatus.

Images