Gas supercharging device and supercharging cooling method

Abstract

The invention discloses a gas supercharging device and a supercharging cooling method, the device simultaneously has a cooling function, the device at least comprises a first-stage cavity, a second-stage cavity, a third-stage cavity, a fourth-stage cavity, a fourth-stage cavity, a fifth-stage cavity, a fifth-stage cavity, a sixth-stage cavity, a fifth-stage cavity, a sixth-stage cavity and a sixth-stage cavity, the two first rotors rotate relatively and are engaged, hot gas is divided into two strands, and the two strands of hot gas are preliminarily compressed; the compression air chamber is of a double-piston air chamber structure and is used for compressing the two strands of hot air at intervals; the cooling chamber is filled with a cooling medium, a cooling coil pipe is arranged in the cooling medium, and the cooling coil pipe is used for receiving two strands of compressed gas obtained from the compressed gas chamber at an interval and carrying out interval cooling. By means of the first-stage double-rotor structure in the first-stage cavity, entering hot gas can be preliminarily compressed, the hot gas can be divided into two strands, the two strands are subjected to main compression at intervals, and efficient gas pressurization is achieved; the two streams of gas can integrate the pressurizing and cooling functions of the gas into one device while ensuring the cooling effect.

Description

Technical Field

[0001] This invention relates to the field of gas boosting equipment technology, and in particular to a gas boosting device with cooling function and a boosting and cooling method. Background Technology

[0002] In fields such as gas adsorption, separation, and gas storage and transportation, gas pressurization is often involved. However, in some operating conditions, when hot gas is transported to the next stage of equipment, it is necessary not only to maintain a certain pressure but also to reduce the gas temperature. Currently, the commonly used technique is to cool the gas and then further pressurize it. However, this method requires multiple devices, and the gas temperature will rise again during the pressurization process, making it impossible to maintain stable pressure and temperature.

[0003] Chinese patent application CN115076105A discloses a process booster pump and boosting method for a cooling system, including a pump casing, a main shaft horizontally mounted within the pump casing, an eccentric differential mechanism fitted in the middle of the main shaft, and a rotor disposed within the rotor cavity of the pump casing. The eccentric differential mechanism is connected to the inner rotor via an outer sleeve and to the outer rotor via an inner sleeve. This prior art also discloses a boosting method based on a process booster pump for a cooling system, including the following steps: the inlet and outlet ports on the pump casing are connected to the cooling system via pipelines; a booster motor is connected externally to the main shaft; the booster motor connected externally to the main shaft actuates, causing the main shaft of the process booster pump to rotate, driving the eccentric differential mechanism inside the pump casing to move; the internal eccentric differential mechanism outputs the rotational motion as two rotors with different motion patterns; the relative positions of the pistons of the two rotors change, causing a change in the space within the rotor cavity, thus achieving boosting. This prior art is applicable to process boosting in cooling systems.

[0004] This type of solution belongs to traditional gas boosting technology. It uses an external motor to drive an eccentric differential mechanism, which outputs the rotational motion as two rotors with different motion patterns. This causes a change in the size of the piston within the rotor chamber, thus achieving pressurization. However, when cooling the pressurized gas is required, the inlet and outlet ports need to be connected to a cooling system via pipelines, meaning additional cooling equipment is required.

[0005] Therefore, there is an urgent need for a gas pressurization device and pressurization and cooling method with cooling function to achieve rapid cooling and pressure maintenance or increase in the process flow, so as to meet the process technology requirements of cooling hot gas while maintaining high pressure in a single device.

[0006] The information disclosed in this background section is intended only to enhance the understanding of the overall background of the invention and should not be construed as an admission or in any way implying that the information constitutes prior art known to those skilled in the art. Summary of the Invention

[0007] The purpose of this invention is to provide a gas boosting device with cooling function and a boosting and cooling method. Through the primary dual-rotor structure in the primary chamber, not only can the incoming hot gas be initially compressed, but the hot gas can also be divided into two streams and subjected to main compression separately and at intervals, thereby achieving efficient gas boosting.

[0008] Another objective of this invention is to provide a gas boosting device and a boosting and cooling method with a cooling function, in which two streams of gas, after being compressed at intervals, are introduced at intervals into a cooling coil located in the same device, thereby ensuring the cooling effect while integrating the gas boosting and cooling functions into one device.

[0009] To achieve the above objectives, according to a first aspect of the present invention, a gas booster device is provided, which also has a cooling function, comprising at least: a primary chamber communicating with a hot gas inlet and having a primary dual rotor inside, wherein the outer edges of the blades of the primary dual rotor are dynamically sealed to the inner wall of the chamber; two primary rotors rotating relative to each other and meshing, dividing the hot gas into two streams and performing preliminary compression on the two streams of hot gas; a compression chamber having a dual-piston chamber structure for intermittently compressing the two streams of hot gas; and a cooling chamber filled with a cooling medium and having a cooling coil disposed within the cooling medium, the cooling coil being used to receive the two intermittently compressed gas streams from the compression chamber and perform intermittent cooling.

[0010] Furthermore, in the above technical solution, the outlet end of the cooling coil can be provided with a secondary cavity. The secondary cavity is connected to the gas outlet and has a secondary dual rotor inside. The outer edge of the blades of the secondary dual rotor is dynamically sealed to the inner wall of the cavity. The volume of the secondary cavity is smaller than that of the primary cavity. The two secondary rotors rotate relative to each other and mesh, dividing the cooled gas into two streams and compressing the two streams of gas again.

[0011] Furthermore, in the above technical solution, the secondary cavity is preferably located in the cooling chamber.

[0012] Furthermore, in the above technical solution, both the first rotor and the second rotor can be three-lobe rotors.

[0013] Furthermore, in the above technical solution, both the primary cavity and the secondary cavity can be constructed from two arc-shaped cavities, each adapted to the corresponding rotor diameter.

[0014] Furthermore, in the above technical solution, the compressed air chamber is divided into a first compressed air chamber and a second compressed air chamber. Correspondingly, the dual piston includes a first piston and a second piston. When the first piston generates negative pressure to drive air intake, the first compressed air chamber is under negative pressure and the second compressed air chamber is compressed and vented. Conversely, when the second piston generates negative pressure to drive air intake, the second compressed air chamber is under negative pressure and the first compressed air chamber is compressed and vented.

[0015] Furthermore, in the above technical solution, the first compressed gas chamber and the second compressed gas chamber are selectively connected to the corresponding hot gas channel and compressed gas channel, respectively; the hot gas channel and the compressed gas channel can be separated by a partition.

[0016] Furthermore, in the above technical solution, an inlet valve is provided between the compressed air chamber and the hot gas passage, and an outlet valve is provided between the compressed air chamber and the compressed gas passage. The inlet valve and the outlet valve preferably adopt the same structure and are set in opposite directions. The valve is I-shaped as a whole, with a perforated baffle at one end and a non-perforated baffle at the other end.

[0017] Furthermore, in the above technical solution, the dual pistons and the first-stage dual rotors can be driven by a combined drive unit connected to an external motor, which is located between the first piston and the second piston.

[0018] Furthermore, in the above technical solution, the combined drive unit may include: a gear chassis, which can be driven by an external motor and is connected to the shaft of the first-stage dual rotor via a conveyor belt to drive the two first rotors to rotate relative to each other; a limiter, which has a circular locking component fixedly connected to the gear chassis, the circular locking component being eccentrically arranged relative to the gear chassis; the limiter is a hollow racetrack-shaped structure, and the circular locking component can move horizontally within the limiter while rotating eccentrically.

[0019] Furthermore, in the above technical solution, the end of the fixing rod of the dual pistons can be fixed at the center of the long side of the racetrack-shaped limiter; the eccentric rotation of the circular locking component can drive the dual pistons to perform up-and-down reciprocating motion.

[0020] Furthermore, in the above technical solution, the cooling coil can be configured as a double helix structure; a one-way valve is provided at the end of the compressed gas channel to selectively introduce two streams of compressed gas from different directions into different inlets of the cooling coil.

[0021] Furthermore, in the above technical solution, the space at the end of the compressed gas channel is set as a double expansion section, and a constriction platform is provided between the two expansion sections; correspondingly, the one-way valve can be a dumbbell-shaped structure, and the two large ends of the dumbbell selectively contact and press against the constriction platform to achieve selective (i.e. intermittent) flow of two streams of compressed gas into the cooling coil.

[0022] Furthermore, in the above technical solution, the secondary dual rotor can be driven by an independent external motor or by sharing a motor with the primary dual rotor.

[0023] According to a second aspect of the present invention, the present invention provides a gas pressurization and cooling method, using the apparatus described in any one of the foregoing claims, comprising the following steps: A. By means of a dynamic sealing connection between a primary dual rotor and a primary cavity, hot gas is split into two streams, and the two streams of hot gas are transported to corresponding hot gas channels during initial compression; B. The two streams of hot gas are compressed intermittently in corresponding compression chambers by means of dual pistons; C. The two streams of hot gas after compression are selectively introduced into cooling coils provided in the cooling chamber for gas cooling.

[0024] Furthermore, in the above technical solution, the method may also include the following steps: D. The two compressed and cooled gases enter the secondary cavity in the cooling chamber, and are connected to the secondary cavity by a dynamic seal through a secondary dual rotor, and are then output after being compressed again.

[0025] Furthermore, in the above technical solution, the volume ratio of the primary cavity to the secondary cavity can be set to 2 to 4:1; the speed ratio of the primary dual rotor to the secondary dual rotor can be set to 1:2 to 5.

[0026] Furthermore, in the above technical solution, the ratio of the gas flow velocity at the hot gas inlet to the rotational speed of the first-stage dual rotor can be 1.5 to 3 times the volume of the first-stage cavity.

[0027] Compared with the prior art, the present invention has the following beneficial effects:

[0028] 1) The gas booster device of the present invention, through the primary dual-rotor structure in the primary chamber, can not only perform preliminary compression on the incoming hot gas, but also divide the hot gas into two streams and perform main compression separately and at intervals, so as to achieve efficient gas boosting; the two streams of gas after being compressed at intervals enter the cooling coil in the same device at intervals, so as to ensure the cooling effect while integrating the gas boosting and cooling functions into one device.

[0029] 2) The two-stage chamber design of this invention enables the gas, after initial compression and main compression, to be compressed again after cooling, while maintaining the gas's cooling state during this recompression. Through the cooling chamber within the device, the split gas is cooled in the cooling coil, and then, after converging, is further compressed and transported in the two-stage chamber using two second rotors, achieving simultaneous transport and compression. The volume of the two-stage chamber is designed to be smaller than that of the first-stage chamber. On the one hand, the volume of the preceding gas is reduced after compression and cooling; the smaller second rotors utilize the limited space and the squeezing force of the two meshing blades to compress the gas. The smaller space allows for recompression of the gas in a shorter time, thereby maintaining or enhancing the pressurization effect of the preceding gas. On the other hand, the two-stage chamber, located within the cooling chamber, maintains the gas in a cooled state while simultaneously recompressing the gas and providing transport power.

[0030] 3) The first rotor in the first chamber and the second rotor in the second chamber of the present invention both adopt a three-blade design. While the incoming gas is "divided into two streams", each stream of gas can be further divided into three relatively independent parts, ensuring the "preliminary compression" effect of each part of the gas in the first chamber and the "re-compression" and "cooling" effects in the second chamber.

[0031] 4) This invention, through the cooperation of a gear chassis, a limiter, and a circular locking component, enables the combined drive unit to drive the two first rotors in the first-stage chamber to rotate while simultaneously driving the double pistons to reciprocate up and down. This achieves the intermittent compression of hot gas in the first and second compression chambers, with the two streams of gas being compressed separately and at intervals, effectively improving compression efficiency. The second-stage double rotor can also be driven by sharing a motor with the first-stage double rotor. Considering that the speed of the second-stage double rotor differs from that of the first-stage double rotor, a gearbox can be added to the design. In this case, the first-stage double rotor, the second-stage double rotor, and the double pistons are all driven by the same motor, which simplifies the drive equipment and is energy-efficient.

[0032] 5) The cooling coil of the present invention adopts a double helix structure, and through the one-way valve at the end of the compressed gas channel, two streams of compressed gas from different directions can be selectively introduced into the cooling coil. Through the interval between the two streams of gas, each hot gas can be cooled "through the whole process", and the cooling efficiency and effect can be well guaranteed.

[0033] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it according to the contents of the specification, and to make the above and other objects, technical features and advantages of the present invention easier to understand, one or more preferred embodiments are listed below and described in detail with reference to the accompanying drawings. Attached Figure Description

[0034] Figure 1 This is a schematic diagram of the internal structure of the gas booster device of the present invention.

[0035] Figure 2 This is a partial enlarged view of the compression chamber in the gas booster device of the present invention.

[0036] Figure 3 This is a schematic diagram of the combined drive unit in the gas booster device of the present invention.

[0037] Figure 4 This is a schematic diagram of the one-way movable valve structure at the end of the compressed gas channel in the gas booster device of the present invention.

[0038] Explanation of key figure labels:

[0039] 1-First stage chamber, 11-First stage dual rotor, 11A, 11B-First rotor, 110A, 110B-First rotor shaft, 2-Hot gas passage, 3-Compressed gas chamber, 30-Baffle, 31-Inlet valve, 311, 321-Perforated baffle, 312, 322-Non-perforated baffle, 32-Outlet valve, 33-Dual piston, 33A-First piston, 33B-Second piston, 4-Compressed gas passage, 40-Extension section, 41-One-way valve, 411-Sealing head, 412-Sealing piston, 42-Necked platform, 5-Cooling chamber, 51-Cooling coil, 511-First inlet of coil, 512-Second inlet of coil, 6-Second stage chamber, 61-Second stage dual rotor, 61A, 61B-Second rotor, 7-Gear chassis, 71-Drive belt, 8-Limiter, 81-Circular locking component, 810-Eccentric shaft;

[0040] 100 - Gas booster device, 101 - Hot gas inlet, 102 - Gas outlet, 103 - Cooling medium outlet, 104 - Cooling medium inlet, 105 - Support leg, 106 - Base. Detailed Implementation

[0041] The specific embodiments of the present invention will now be described in detail with reference to the accompanying drawings, but it should be understood that the scope of protection of the present invention is not limited to the specific embodiments.

[0042] Unless otherwise expressly stated, throughout the specification and claims, the term "comprising" or its variations such as "including" or "comprises" shall be understood to include the stated elements or components without excluding other elements or other components.

[0043] In this document, for ease of description, spatial relative terms such as “below,” “under,” “down,” “above,” “above,” “upper,” etc., are used to describe the relationship of one element or feature to another element or feature in the accompanying drawings. It should be understood that spatial relative terms are intended to encompass different orientations of an object in use or operation, in addition to those depicted in the figures. For example, if an object in the figure is flipped, an element described as “below” or “under” another element or feature would be oriented “above” that element or feature. Thus, the exemplary term “below” can encompass both the downward and upward orientations. An object may also have other orientations (rotated 90 degrees or other orientations), and the spatial relative terms used herein should be interpreted accordingly.

[0044] In this document, the terms "first," "second," etc., are used to distinguish two different elements or parts, and are not used to define specific positions or relative relationships. In other words, in some embodiments, the terms "first," "second," etc., can also be used interchangeably.

[0045] Example 1

[0046] This invention addresses the problem in existing technologies where gas pressurization and cooling cannot be performed in the same device. It develops a gas pressurization device 100 that also has a cooling function, comprising at least a primary chamber 1, a compression chamber 3, and a cooling chamber 5. The primary chamber 1 is connected to a hot gas inlet 101 and houses a primary dual rotor 11 (including two first rotors 11A and 11B). The outer edges of the blades of the primary dual rotor 11 are dynamically sealed to the inner wall of the chamber (the figure only shows the blades in contact with the inner wall of the primary chamber 1, not the dynamic seal structure). The two first rotors 11A and 11B can rotate relative to each other around their respective axes and engage, dividing the incoming hot gas into two streams and performing preliminary compression on both streams. This preliminary compression refers to the fact that, under the rotation of the blades and the aforementioned dynamic seal, the incoming hot gas sequentially enters the sealed space between adjacent blades. The high gas velocity instantly fills this sealed space, causing the gas density to increase instantaneously, thus achieving the effect of "preliminary compression." The compression chamber 3 is a dual-piston chamber structure used to compress two streams of hot gas alternately. This alternate compression means that while the first piston 33A compresses the gas in its corresponding chamber, the corresponding chamber of the second piston 33B is in a suction state; conversely, while the second piston 33B compresses the gas in its corresponding chamber, the corresponding chamber of the first piston 33A is in a suction state. The cooling chamber 5 is filled with a cooling medium and a cooling coil 51 is installed within the cooling medium. The cooling coil 51 receives the two streams of compressed gas from the compression chamber alternately and performs intermittent cooling.

[0047] The gas booster device in this embodiment, through a primary dual-rotor structure within the primary chamber, can not only perform preliminary compression on the incoming hot gas, but also divide the hot gas into two streams and perform primary compression separately and at intervals, achieving efficient gas boosting. The two streams of gas, after being compressed at intervals, enter the cooling coil located in the same device at intervals, ensuring the cooling effect while integrating the gas boosting and cooling functions into one device.

[0048] Further as Figure 1As shown, the outlet end of the cooling coil 51 is provided with a secondary cavity 6. The secondary cavity 6 is connected to the gas outlet 102 and contains a secondary dual rotor 61 (including two second rotors 61A and 61B). The outer edge of the blades of the secondary dual rotor 6 is dynamically sealed to the inner wall of the cavity. Preferably, but not limitingly, the volume of the secondary cavity 6 is smaller than that of the primary cavity 1. The two second rotors 61A and 61B can rotate relative to each other and mesh, dividing the gas after main compression and cooling into two streams and recompressing the two streams of gas. The secondary cavity 6 is located in the cooling chamber 5, so that the gas is kept cooled while being recompressed. The gas is cooled in the cooling coil within the cooling chamber of the device, and then further compressed and transported in the secondary chamber by two second rotors after converging, achieving simultaneous transport and compression. The volume of the secondary chamber is smaller than that of the primary chamber, meaning the diameter of the second rotor is smaller than that of the first rotor. On the one hand, the volume of the preceding gas is reduced after compression and cooling. The smaller second rotor uses the squeezing force of the two blades after meshing and separating to compress the gas. The smaller space allows for the gas to be recompressed in a shorter time, thereby maintaining or enhancing the pressurization effect of the preceding gas. On the other hand, the secondary chamber and the second rotor within it are also arranged in the cooling chamber. While recompressing the gas and providing transport power, they can also be further mixed and then diverted to achieve more effective cooling.

[0049] Further as Figure 1 As shown, the two first rotors 11A and 11B arranged in the primary cavity 1 and the two second rotors 61A and 61B arranged in the secondary cavity 6 are preferably three-lobe rotors. Both the primary cavity 1 and the secondary cavity 6 are constructed from two arc-shaped cavities, each adapted to the corresponding rotor diameter. Through this structural design, while the incoming gas is "divided into two streams," each stream of gas can be further divided into three relatively independent parts, ensuring the "preliminary compression" effect of each part of the gas in the primary cavity 1 and the "re-compression" and "cooling" effects in the secondary cavity 6. The inventors have verified through experiments that both the gas pressurization effect and the gas cooling effect can be effectively guaranteed and are highly efficient.

[0050] Further as Figure 1 , 2 As shown, the compressed air chamber is divided into the first compressed air chamber (i.e., Figure 1 The air chamber above the first piston 33A) and the second compression air chamber (i.e. Figure 1The air chamber below the second piston 33B is located in the middle. Correspondingly, the dual pistons 33 include a first piston 33A and a second piston 33B. When the first piston 33A generates negative pressure to drive air intake (at which time the dual pistons 33 move downward as a whole), the first compression chamber receives air under negative pressure, and the second compression chamber compresses and exhausts air; conversely, when the second piston 33B generates negative pressure to drive air intake, the second compression chamber receives air under negative pressure, and the first compression chamber compresses and exhausts air. Further, the first and second compression chambers are selectively connected to the corresponding hot gas channel 2 and compressed gas channel 4, respectively, that is... Figure 1 The first compressed gas chamber can be selectively connected to the upper hot gas passage 2 and compressed gas passage 4. Figure 1 The second compressed gas chamber can selectively communicate with the lower hot gas passage 2 and compressed gas passage 4; the hot gas passage 2 and compressed gas passage 4 are separated by a partition 30. This selective communication can be achieved by the cooperation of an inlet valve and an outlet valve. Specifically, an inlet valve 31 is provided between the compressed gas chamber 3 and the hot gas passage 2, and an outlet valve 32 is provided between the compressed gas chamber 3 and the compressed gas passage 4. The inlet valve 31 and the outlet valve 32 preferably have the same structure and are arranged in opposite directions (see reference). Figure 2 The valve is H-shaped, with perforated baffles 311 and 321 at one end and non-perforated baffles 312 and 322 at the other end. Figure 2 As shown, when piston 33 moves downward, compression chamber 3 is in the intake state. At this time, both the I-shaped inlet valve 31 and outlet valve 32 are in the "downward" state. The non-perforated baffle 312 at the lower end of inlet valve 31 is open, and the perforated baffle 311 at the upper end can freely ventilate. The non-perforated baffle 322 at the upper end of outlet valve 32 is closed, and hot gas from hot gas passage 2 enters compression chamber 3. When piston 33 moves upward, compression chamber 3 is in the compression state. At this time, both the I-shaped inlet valve 31 and outlet valve 32 are in the "backward" state. The non-perforated baffle 312 at the lower end of inlet valve 31 is closed, and the non-perforated baffle 322 at the upper end of outlet valve 32 is open. The perforated baffle 321 at the lower end of outlet valve 32 can freely ventilate. The hot gas in compression chamber 3 is compressed and enters compression gas passage 4 through outlet valve 32. The relative arrangement of the two pistons and two gas chambers allows the first piston 33A to compress the gas while the second piston 33B moves upward to drive the intake of gas; conversely, the second piston 33B compresses the gas while the first piston 33A moves downward to drive the intake of gas.

[0051] Further as Figure 1 , 3 As shown, the dual pistons 33 and the first-stage dual rotors 11 are preferably driven by a combined drive unit connected to an external motor (not shown in the figure). This combined drive unit is located between the first piston 33A and the second piston 33B, and specifically includes a gear chassis 7 and a limiter 8. The gear chassis 7 is driven by the external motor and connected to the shaft of the first-stage dual rotors (see reference 8) via a conveyor belt 71. Figure 3 The first rotor shafts 110A and 110B are connected in a transmission, driving the two first rotors 11 to rotate relative to each other. A circular locking component 81, fixedly connected to the gear chassis 7, is provided inside the limiter 8. This circular locking component 81 is eccentrically positioned relative to the gear chassis 7 (similar to a cam design fixed to the gear chassis). The limiter 8 has a hollow racetrack-shaped structure, allowing the circular locking component 81 to move horizontally within the limiter 8 while rotating eccentrically. The fixed rod end of the double piston 33 is fixed to the center of the long side of the racetrack-shaped limiter 8. The eccentric rotation of the circular locking component 81 drives the double piston 33 to reciprocate up and down. Through the cooperation of the gear chassis 7, the limiter 8, and the circular locking component 81, the combined drive unit can drive the double piston 33 to reciprocate up and down while simultaneously driving the two first rotors 11 to rotate in the primary cavity 1 (the movement directions of each component can be referenced). Figure 3 This allows for the intermittent compression of hot gas in the first and second compression chambers, achieving main gas compression within the device. The two streams of gas are compressed separately and at intervals, effectively improving compression efficiency.

[0052] Further as Figure 1 , 4 As shown, the cooling coil 51 preferably has a double-helix structure; a one-way valve 41 is provided at the end of the compressed gas passage 4 to selectively introduce two streams of compressed gas from different directions (i.e., the compressed gas passage at the upper end and the compressed gas passage at the lower end) into different inlets of the cooling coil 51. Specifically, the space at the end of the compressed gas passage 4 is provided with a double extension section (see...). Figure 4 The expansion section 40 is provided between the two expansion sections 40, and a constricted platform 42 is provided between them. Correspondingly, the one-way valve 41 has a dumbbell-shaped structure. By selectively contacting and pressing the two large ends of the dumbbell (i.e., the sealing heads 411) with the constricted platform 42, two streams of compressed gas are selectively introduced into the cooling coil 51. Specifically, when the hot gas from the upper end, which has been compressed by the main compression, runs to the one-way valve 41, the valve falls down, and the sealing piston 412 at the upper end is stuck at the constricted platform 42. At this time, the sealing head at the upper end disengages from the straight section of the compressed gas passage, so that the upper end of the one-way valve 41 opens (at this time, the sealing head 411 at the lower end seals with the compressed gas passage), allowing the hot gas after the main compression to enter the cooling coil 51 through the first inlet 511. Conversely, when the hot gas from the lower end, after being compressed by the main compressor, reaches the one-way valve 41, the valve is lifted, and the sealing piston 412 at the lower end is locked at the constriction platform 42. At this time, the sealing head 411 at the lower end disengages from the straight section of the compressed gas passage, causing the lower end of the one-way valve 41 to open (at this time, the sealing head 411 at the upper end seals with the compressed gas passage), allowing the hot gas after the main compressor to enter the cooling coil through the second inlet 512 of the cooling coil 51.

[0053] Furthermore, preferably but not limitingly, the secondary dual rotor 61 can be driven by an independent external motor. Alternatively, it can be driven by sharing a motor with the primary dual rotor 11. Considering that the secondary dual rotor and its speed may differ from the primary dual rotor 11, a gearbox can be added to the design. In this case, the primary dual rotor, the secondary dual rotor, and the dual pistons are all driven by the same motor, which simplifies the drive equipment and is energy-efficient.

[0054] Example 2

[0055] This embodiment provides a gas pressurization and cooling method, using the apparatus in Embodiment 1, including the following steps:

[0056] In step S101, the hot gas is split into two streams through a dynamic sealing connection between the primary dual rotor 11 (preferably a three-bladed rotor) and the primary cavity 1, and the two streams of hot gas are transported to the corresponding hot gas channels 2 (i.e., ...) during initial compression. Figure 1 (The upper and lower hot gas channels in the middle). In this step, as the first rotor 11A and the second rotor 11B rotate relative to each other, each hot gas enters the space between adjacent blades in sequence. Each space is relatively independent and can compress the hot gas with a certain gas velocity instantaneously, realizing the compression of each gas in three parts, which can effectively improve the compression efficiency of the initial compression in the first-stage cavity 1.

[0057] In step S102, the two streams of hot gas from step S101 are compressed intermittently in their respective compression chambers using a dual piston. The pre-compressed hot gas from the primary chamber 1 enters the upper and lower compression chambers at intervals through the hot gas channel 2. During the reciprocating motion of the dual piston as a whole, the intake of gas in the first compression chamber and the compression in the second compression chamber occur simultaneously, as do the compression in the first compression chamber and the intake in the second compression chamber, thereby completing one pressurization cycle and achieving the main compression of the hot gas in the compression chamber 3.

[0058] In step S103, the two streams of hot gas after main compression are selectively (i.e., intermittently) introduced into the cooling coil 51 located in the cooling chamber 5 for gas cooling. In this step, the time difference between the entry of the two streams of hot gas after main compression and the one-way valve 41 at the end of the compressed gas channel 4 are used to allow the two streams of gas to enter the double-helix structure cooling coil intermittently. In this way, each stream of hot gas can be cooled "throughout" the process, ensuring both cooling efficiency and effect. The two streams of gas merge at the outlets of the two cooling coils after cooling, thus obtaining the gas after preliminary compression, main compression, and cooling.

[0059] Step S104, this is the preferred step, where the two compressed and cooled gases enter the secondary chamber 6 within the cooling chamber. The secondary dual rotor 61 is dynamically sealed to the secondary chamber 6, allowing for further gas compression before output. This preferred step has several advantages. First, the volume of the preceding gas after compression (i.e., preliminary compression + main compression) and cooling is reduced, resulting in a slight decrease in pressure. Utilizing a smaller secondary chamber space allows for faster gas recompression, thus maintaining or enhancing the pressurization effect of the preceding gas. Second, since the secondary chamber is also located within the cooling chamber, it further mixes the gas before splitting it, maintaining the gas's cooling state throughout the process, while simultaneously recompressing the gas and providing delivery power.

[0060] Through experimentation, the inventors verified that the overall compression and cooling effect is optimal when the volume ratio of the primary and secondary chambers is 2–4:1 and the rotational speed ratio of the primary dual rotors to the secondary dual rotors is 1:2–5. Further experimentation by the inventors showed that, for the three-bladed primary rotor, the overall gas pressurization effect is even better when the ratio of the gas flow velocity at the hot gas inlet to the rotational speed of the primary dual rotors is 1.5–3 times the volume of the primary chamber.

[0061] The foregoing description of specific exemplary embodiments of the present invention is for illustrative and explanatory purposes. These descriptions are not intended to limit the invention to the precise forms disclosed, and it will be apparent that many changes and variations can be made in accordance with the foregoing teachings. The exemplary embodiments were chosen and described in order to explain the specific principles of the invention and its practical application, thereby enabling those skilled in the art to implement and utilize various different exemplary embodiments of the invention, as well as various different choices and variations. Any simple modifications, equivalent changes, and alterations made to the foregoing exemplary embodiments should fall within the scope of protection of the present invention.

Claims

1. A gas booster device, characterized in that, It also has a cooling function, including: The first-stage cavity is connected to the hot gas inlet and is equipped with a first-stage dual rotor. The outer edge of the blades of the first-stage dual rotor is dynamically sealed to the inner wall of the cavity. The two first rotors rotate relative to each other and mesh, dividing the hot gas into two streams and performing preliminary compression on the two streams of hot gas. The compression chamber, which has a double-piston chamber structure, is used to compress the two streams of hot gas at intervals. The cooling chamber is filled with a cooling medium and a cooling coil is installed within the cooling medium. The cooling coil is used to receive two streams of compressed gas from the compression chamber at intervals and to cool them at intervals.

2. The gas booster device according to claim 1, characterized in that, The cooling coil outlet end is provided with a secondary cavity, which is connected to the gas outlet and contains a secondary dual rotor. The outer edge of the blades of the secondary dual rotor is dynamically sealed to the inner wall of the cavity. The volume of the secondary cavity is smaller than that of the primary cavity. The two second rotors rotate relative to each other and mesh, dividing the cooled gas into two streams and recompressing the two streams of gas.

3. The gas booster device according to claim 2, characterized in that, The secondary cavity is located within the cooling cavity.

4. The gas booster device according to claim 2, characterized in that, Both the first rotor and the second rotor are three-lobe rotors.

5. The gas booster device according to claim 2, characterized in that, Both the primary cavity and the secondary cavity are constructed from two arc-shaped cavities, each adapted to the corresponding rotor diameter.

6. The gas booster device according to claim 1, characterized in that, The compressed air chamber is divided into a first compressed air chamber and a second compressed air chamber. Correspondingly, the dual piston includes a first piston and a second piston. When the first piston generates negative pressure to drive the intake, the first compressed air chamber is under negative pressure to intake, and the second compressed air chamber is compressed to exhaust. Conversely, when the second piston generates negative pressure to drive the intake, the second compression chamber receives negative pressure and the first compression chamber compresses and exhausts air.

7. The gas booster device according to claim 6, characterized in that, The first and second compressed gas chambers are selectively connected to corresponding hot gas channels and compressed gas channels, respectively; the hot gas channels and compressed gas channels are separated by partitions.

8. The gas booster device according to claim 7, characterized in that, An inlet valve is provided between the compressed air chamber and the hot gas passage, and an outlet valve is provided between the compressed air chamber and the compressed gas passage. The inlet valve and the outlet valve have the same structure and are set in opposite directions. The valve is I-shaped, with a perforated baffle at one end and a non-perforated baffle at the other end.

9. The gas booster device according to claim 6, characterized in that, The dual pistons and the first-stage dual rotors are driven by a combined drive unit connected to an external motor, which is located between the first piston and the second piston.

10. The gas booster device according to claim 9, characterized in that, The combined drive unit includes: The gear chassis is driven by the external motor and is connected to the shaft of the first-stage dual rotor via a conveyor belt, driving the two first rotors to rotate relative to each other. The limiter has a circular locking component that is fixedly connected to the gear chassis. The circular locking component is eccentrically positioned relative to the gear chassis. The limiter has a hollow racetrack-shaped structure. The circular locking component can move horizontally within the limiter while rotating eccentrically.

11. The gas booster device according to claim 10, characterized in that, The fixed rod end of the dual piston is fixed to the center of the long side of the racetrack-shaped limiter; the eccentric rotation of the circular locking component drives the dual piston to reciprocate up and down.

12. The gas booster device according to claim 7, characterized in that, The cooling coil has a double-helix structure; the end of the compressed gas channel is equipped with a one-way valve for selectively introducing two streams of compressed gas from different directions into different inlets of the cooling coil.

13. The gas booster device according to claim 12, characterized in that, The space at the end of the compressed gas channel is configured with two expansion sections, and a constricted platform is provided between the two expansion sections; correspondingly, the one-way valve has a dumbbell-shaped structure, and the two large ends of the dumbbell selectively contact and press against the constricted platform to achieve selective introduction of two streams of compressed gas into the cooling coil.

14. The gas booster device according to claim 2, characterized in that, The secondary dual rotor is driven by an independent external motor or by sharing a motor with the primary dual rotor.

15. A gas pressurization and cooling method, characterized in that, Using the apparatus according to any one of claims 1 to 14, the steps include: A. Through the dynamic sealing connection between the first-stage dual rotor and the first-stage cavity, the hot gas is split into two streams, and the two streams of hot gas are transported to the corresponding hot gas channels during the initial compression. B. The two streams of hot gas are compressed intermittently in their respective compression chambers using a dual piston; C. The two compressed hot gases are selectively introduced into the cooling coils located in the cooling chamber for gas cooling.

16. The gas pressurization and cooling method according to claim 15, characterized in that, The method further includes the following steps: D. The two compressed and cooled gases enter the secondary chamber within the cooling chamber. They are connected to the secondary chamber via a dynamic seal through a secondary dual rotor, and then the gases are compressed again before being output.

17. The gas pressurization and cooling method according to claim 16, characterized in that, The volume ratio of the primary cavity to the secondary cavity is 2 to 4:1; the speed ratio of the primary dual rotor to the secondary dual rotor is 1:2 to 5.

18. The gas pressurization and cooling method according to claim 17, characterized in that, The ratio of the gas flow velocity at the hot gas inlet to the rotational speed of the first-stage dual rotor is 1.5 to 3 times the volume of the first-stage cavity.

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