Twin-screw compressor, refrigeration unit, gas compression unit

Abstract

This application provides a twin-screw compressor, a refrigeration device, and a gas compression device. The twin-screw compressor includes: a housing with a compressor exhaust port at one end, the housing enclosing a cylinder; an exhaust chamber located at the end of the cylinder near the compressor exhaust port; a screw rotor located inside the cylinder, including a pair of meshing female and male rotors; a slide valve located axially parallel to and adjacent to the screw rotor and movably located inside the cylinder, the slide valve and the screw rotor enclosing a compression chamber; an exhaust chamber pressure detection port communicating with the exhaust chamber and opening into the housing; a compression chamber end pressure detection port communicating with the end of the compression chamber near the exhaust chamber and opening into the housing; a differential pressure sensor communicating with both the exhaust chamber pressure detection port and the compression chamber end pressure detection port; and a controller connected to the differential pressure sensor at one end, controlling the movement of the slide valve based on the exhaust pressure and the compression chamber end pressure detected by the differential pressure sensor.

Description

Technical Field

[0001] This application relates to refrigeration / cooling equipment technology and gas compression technology, specifically to a twin-screw compressor and a refrigeration device or gas compression device having the twin-screw compressor. Background Technology

[0002] Variable compression ratio twin-screw compressors maintain high efficiency in both heating and cooling applications, making them increasingly popular. However, if the slide valve in a variable compression ratio twin-screw compressor is not in the correct position, it can lead to undercompression or overcompression. Utility Model Content

[0003] This application aims to provide a twin-screw compressor in order to at least solve or alleviate some of the problems existing in the prior art.

[0004] This application provides a twin-screw compressor, comprising: a housing with a compressor exhaust port at one end, the housing enclosing a cylinder; an exhaust chamber located at the end of the cylinder near the compressor exhaust port; a screw rotor located inside the cylinder, comprising a pair of meshing female and male rotors; a slide valve movably located inside the cylinder, parallel and adjacent to the screw rotor axis, the slide valve and the screw rotor enclosing a compression chamber; an exhaust chamber pressure detection port located on the housing, communicating with the exhaust chamber; a compression chamber end pressure detection port located on the housing, communicating with the end of the compression chamber near the exhaust chamber; a differential pressure sensor, one end of which is connected to the exhaust chamber pressure detection port and the other end of which is connected to the compression chamber end pressure detection port; and a controller connected to the differential pressure sensor, controlling the movement of the slide valve based on the pressure difference between the exhaust pressure detected by the differential pressure sensor and the compression chamber end pressure.

[0005] In one or more embodiments, the twin-screw compressor further includes: a hydraulic cylinder formed by a housing, one end of which is provided with a through hole and communicates with a cylinder through the through hole; and a piston rod disposed inside the hydraulic cylinder and fixedly connected to a slide valve through the through hole.

[0006] In one or more embodiments, the twin-screw compressor further includes: an oil solenoid valve connected to the hydraulic cylinder via an oil line; the controller controls the opening and closing of the oil solenoid valve based on the exhaust pressure and the end pressure of the compression chamber detected by the differential pressure sensor, so as to discharge oil from the hydraulic cylinder or fill the hydraulic cylinder with oil.

[0007] In one or more embodiments, the twin-screw compressor further includes: a slide valve detection groove that is slotted into the slide valve and extends along the moving direction of the slide valve in a manner communicating with a pressure detection port at the end of the compression chamber, wherein the length of the slide valve detection groove in the moving direction of the slide valve is greater than or equal to the movable distance of the slide valve.

[0008] In one or more embodiments, the twin-screw compressor further includes: a slide valve air passage formed in the slide valve in a direction perpendicular to the slide valve's movement direction, connecting the slide valve detection groove and the compression chamber.

[0009] In one or more embodiments, the pressure detection port at the end of the compression chamber is positioned so that it can still maintain communication with the valve detection groove when the slide valve is at the end of its stroke closest to the exhaust chamber.

[0010] In one or more embodiments, the twin-screw compressor further includes: a first maintenance valve disposed on a pipeline connected to a differential pressure sensor corresponding to the pressure detection port of the exhaust chamber; and a second maintenance valve disposed on a pipeline connected to a differential pressure sensor corresponding to the pressure detection port at the end of the compression chamber.

[0011] In one or more embodiments, the first maintenance valve and the second maintenance valve are shut-off valves.

[0012] This application also provides a refrigeration device, including a compressor, a condenser, an expansion valve and an evaporator connected in sequence via refrigerant pipes, wherein the compressor is a twin-screw compressor provided in one or more embodiments of this application.

[0013] This application also provides a gas compression device including a compressor, wherein the compressor is a twin-screw compressor provided in one or more embodiments of this application. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the structure of a twin-screw compressor provided in one or more embodiments of this application.

[0015] Figure 2 This is a partial structural diagram of a twin-screw compressor provided in one or more embodiments of this application.

[0016] Figure 3 This is a partial structural diagram of a twin-screw compressor provided in one or more embodiments of this application.

[0017] Figure 4 This is a schematic diagram showing the slide valve of a twin-screw compressor in one or more embodiments of this application moving to the first position.

[0018] Reference numerals: twin-screw compressor 100, housing 101, compression chamber housing 101a, exhaust chamber housing 101b, hydraulic cylinder housing 101c, compressor exhaust port 102, cylinder 103, exhaust chamber 104, screw rotor 105, female rotor 106, male rotor 107, slide valve 108, compression chamber 109, exhaust chamber pressure detection port 110, compression chamber end pressure detection port 111, differential pressure sensor 112, hydraulic cylinder 113, piston rod 114, slide valve detection groove 115, slide valve air passage 116, first maintenance valve 117, second maintenance valve 118. Detailed Implementation

[0019] It should be noted that the following will use examples to illustrate the working principle, features and advantages of the refrigeration equipment according to this application. However, it should be understood that all descriptions are given for illustrative purposes only and should not be construed as limiting the application in any way.

[0020] Furthermore, for any single technical feature described or implied in the embodiments mentioned herein, or any single technical feature shown or implied in the various figures, this application still allows for any combination or deletion of these technical features (or their equivalents) without any technical obstacle, thereby obtaining more other embodiments of this application that may not be directly mentioned herein.

[0021] Figure 1 This is a schematic diagram of the structure of a twin-screw compressor provided in one or more embodiments of this application. Figure 2 This is a partial structural schematic diagram of a twin-screw compressor provided in one or more embodiments of this application. Figure 3 This is a partial structural schematic diagram of a twin-screw compressor provided in one or more embodiments of this application, see reference. Figure 1 , Figure 2 and Figure 3 As shown, the twin-screw compressor 100 provided in one or more embodiments of this application includes: a housing 101, an exhaust chamber 104 enclosed within the housing 101, a screw rotor 105, a slide valve 108, an exhaust chamber pressure detection port 110 and a compression chamber end pressure detection port 111 opened into the housing 101, a differential pressure sensor 112 disposed outside the housing 101, and a controller. Further, the housing 101 includes a compression chamber housing 101a and an exhaust chamber housing 101b.

[0022] Specifically, the housing 101 encloses a cylinder 103, with a compressor exhaust port 102 at one end. An exhaust chamber 104 is located inside the cylinder 103 near the compressor exhaust port 102. A screw rotor 105 is disposed inside the cylinder 103 and includes a pair of meshing female rotors 106 and male rotors 107. When the female rotors 106 and 107 rotate, they can achieve gas intake, compression, and exhaust. A slide valve 108 is movably disposed inside the cylinder 103, parallel and adjacent to the screw rotor 105. The slide valve 108 and the screw rotor 105 together enclose a compression chamber 109, and the end position of the compression chamber 109 along the gas flow direction communicates with the exhaust chamber 104. Furthermore, the compression chamber 109 is correspondingly disposed with the compression chamber housing 101a, and the exhaust chamber 104 is correspondingly disposed with the exhaust chamber housing 101b.

[0023] Furthermore, it should be noted that although the housing 101 has been described in one or more embodiments as including a compression chamber housing 101a and an exhaust chamber housing 101b, this is not intended to limit this application. Depending on the operating conditions and manufacturing process of the twin-screw compressor, the housing 101 may be integrally formed, or the compression chamber housing 101a and the exhaust chamber housing 101b may be separately processed as required. All such arrangements should be included within the scope of protection of this application.

[0024] When the male rotor 107 rotates, it drives the female rotor 106 to rotate synchronously. The gas is drawn in and compressed as it moves along the inter-tooth space between the female rotor 106 and the male rotor 107 until the compressed gas flows to the end of the compression chamber 109, that is, the position where the screw rotor 105 does not correspond to the slide valve 108. At this time, the inter-tooth space between the female rotor 106 and the male rotor 107 that does not correspond to the slide valve 108 is connected to the exhaust chamber 104. After the compressed gas passes through the inter-tooth space of the part of the screw rotor 105 that does not correspond to the slide valve 108, the compressed gas flows into the exhaust chamber 104 and is further discharged from the twin-screw compressor 100 through the compressor exhaust port 102.

[0025] The exhaust chamber 104 of the twin-screw compressor 100 is connected to the outside through the compressor exhaust port 102. That is, the pressure inside the exhaust chamber 104 is equal to the exhaust pressure of the twin-screw compressor 100. Through the exhaust chamber pressure detection port 110, which is provided in the exhaust chamber housing 101b and communicates with the exhaust chamber 104, the gas pressure inside the exhaust chamber 104 can be transmitted to the differential pressure sensor 112, which is provided outside the exhaust chamber housing 101b. Through the compression chamber end pressure detection port 111, which is provided in the compression chamber housing 101a and communicates with the end of the compression chamber 109 near the exhaust chamber 104, the gas pressure at the end of the compression chamber 109 (i.e., the space between the teeth of the female rotor 106 and the male rotor 107 that does not correspond to the slide valve 108) can be transmitted to the differential pressure sensor 112. Thus, the differential pressure sensor 112 outputs the pressure difference between the pressure inside the exhaust chamber 104 and the pressure at the end of the compression chamber 109, which is the difference between the exhaust pressure of the twin-screw compressor 100 and the pressure at the end of the compression chamber 109.

[0026] If the pressure difference between the exhaust chamber 104 and the end pressure of the compression chamber 109 of the twin-screw compressor 100 is less than the specified allowable pressure difference value, for example, less than 0, it indicates that the end pressure of the compression chamber 109 is greater than the pressure of the exhaust chamber 104 of the twin-screw compressor 100, and the twin-screw compressor 100 is in an overcompression state. At this time, the controller controls the slide valve 108 to move away from the compressor exhaust port 102. That is, as the slide valve 108 moves, the exhaust is advanced and the internal volume ratio becomes smaller, thereby reducing the end pressure of the compression chamber 109 of the twin-screw compressor 100 until it approaches the pressure of the exhaust chamber 104. This allows the twin-screw compressor 100 to escape the overcompression state and avoids pressure fluctuations, efficiency reduction, and exhaust temperature rise caused by the sudden expansion of high-pressure gas in the compression chamber 109 to the exhaust chamber 104.

[0027] Figure 4 This is a schematic diagram showing the slide valve of a twin-screw compressor in one or more embodiments of this application moving to the first position. Figure 4 For example, when the slide valve 108 moves to the first position (that is, the position furthest from the compressor exhaust port 102 in the movable position), the internal volume ratio of the twin-screw compressor 100 (that is, the ratio between the suction volume and the exhaust volume) reaches the minimum value under the variable operating conditions of the twin-screw compressor 100.

[0028] If the pressure difference between the exhaust chamber 104 and the end pressure of the compression chamber 109 of the twin-screw compressor 100 exceeds the specified allowable pressure difference value (e.g., greater than 0), it indicates that the pressure in the exhaust chamber 104 of the twin-screw compressor 100 is greater than the end pressure of the compression chamber 109, and the twin-screw compressor 100 is in an undercompression state. At this time, the controller controls the slide valve 108 to move towards the compressor exhaust port 102. That is, as the slide valve 108 moves, the exhaust is delayed, and the internal volume ratio increases, thereby increasing the end pressure of the compression chamber 109 of the twin-screw compressor 100 until it approaches the pressure of the exhaust chamber 104. This allows the twin-screw compressor 100 to escape the undercompression state, thus avoiding the low-frequency impact sound or airflow whistling caused by the backflow of gas from the exhaust chamber 104 in the undercompression state, as well as the problem of high-pressure exhaust backflow mixing with low-temperature gas in the compression chamber, leading to a drop in average temperature.

[0029] Continue reading Figure 2 As shown, Figure 2 When the slide valve 108 of the twin-screw compressor 100 provided in the middle moves to the second position (that is, the position closest to the compressor discharge port 102 in the movable position), the internal volume ratio of the twin-screw compressor 100 (that is, the ratio between the suction volume and the discharge volume) reaches the maximum value of the twin-screw compressor 100 under variable operating conditions.

[0030] The pressure of the exhaust chamber 104 of the twin-screw compressor 100 described above is based on the example of the twin-screw compressor 100 reaching its design exhaust pressure during normal operation. However, it does not limit the exhaust pressure of the twin-screw compressor 100 to a point value; it can also be a range value.

[0031] Through the above implementation method, a differential pressure sensor 112 is set to detect the difference between the exhaust pressure of the exhaust chamber 104 of the twin-screw compressor 100 and the end pressure of the compression chamber 109, and the slide valve 108 is controlled to move according to the detection result, thereby changing the end pressure of the compression chamber 109, so that the end pressure of the compression chamber 109 is equal to the exhaust pressure of the exhaust chamber 104 of the twin-screw compressor 100, thereby improving the working efficiency of the twin-screw compressor 100.

[0032] Meanwhile, by setting differential pressure sensor 112, the difference between the output pressure of the exhaust chamber 104 of the twin-screw compressor 100 and the end pressure of the compression chamber 109 can be directly output. The position of slide valve 108 can be adjusted in real time according to this difference. There is no need to use multiple pressure sensors and slide valve 108 displacement sensors to detect and further calculate and analyze before controlling the movement of slide valve 108 assembly. This reduces the number of parts and lowers the cost while improving the response speed.

[0033] More specifically, during the compression process of the twin-screw compressor 100, its internal pressure often fluctuates significantly. If multiple individual pressure sensors are used and algorithms are applied to control the movement of the slide valve 108, the slide valve 108 may move frequently due to pressure fluctuations. In one or more embodiments of this application, a differential pressure sensor 112 is used to directly acquire and output the pressure difference between the exhaust pressure of the exhaust chamber 104 and the pressure at the end of the compression chamber 109 of the twin-screw compressor 100. Compared with using multiple individual pressure sensors to measure the pressure at the end of the compression chamber 109 or the exhaust chamber 104, this reduces the measurement errors caused by pressure fluctuations in the end of the compression chamber 109 or the exhaust chamber 104, thereby improving the accuracy of the slide valve 108 movement control.

[0034] In one or more embodiments, the twin-screw compressor 100 further includes a hydraulic cylinder 113, which is formed by a hydraulic cylinder housing 101c and is disposed adjacent to the cylinder 103. A through hole is provided at the end of the hydraulic cylinder 113 adjacent to the cylinder 103, through which it communicates with the cylinder 103. Simultaneously, a piston rod 114 is also disposed inside the hydraulic cylinder 113, which passes through the through hole and is fixedly connected to a slide valve 108. The piston rod 114 drives the slide valve 108 to move in a direction closer to or further away from the compressor exhaust port 102.

[0035] In an optional embodiment, the twin-screw compressor 100 further includes an oil solenoid valve connected to the hydraulic cylinder 113 via an oil passage.

[0036] When the differential pressure sensor 112 detects that the difference between the discharge pressure of the exhaust chamber 104 and the end pressure of the compression chamber 109 of the twin-screw compressor 100 is less than a specified differential pressure value, the controller controls the opening and closing of the oil solenoid valve to discharge oil from the hydraulic cylinder 113. The decrease in oil pressure in the hydraulic cylinder 113 causes the piston rod 114 to drive the slide valve 108 to move towards the direction closer to the compressor exhaust port 102. That is, the internal volume ratio of the screw compressor 100 increases with the movement of the slide valve 108, thereby increasing the end pressure of the compression chamber 109 of the twin-screw compressor 100 until it approaches the pressure of the exhaust chamber 104, so that the operating condition of the twin-screw compressor 100 is removed from the undercompression state.

[0037] When the differential pressure sensor 112 detects that the pressure difference between the exhaust chamber 104 and the end pressure of the compression chamber 109 of the twin-screw compressor 100 is greater than 0, the controller controls the opening and closing of the oil solenoid valve to fill the hydraulic cylinder 113 with oil. The increase in oil pressure in the hydraulic cylinder 113 causes the piston rod 114 to drive the slide valve 108 to move away from the compressor exhaust port 102. That is, the internal volume ratio of the screw compressor 100 decreases as the slide valve 108 moves, thereby reducing the end pressure of the compression chamber 109 of the twin-screw compressor 100 until it approaches the pressure of the exhaust chamber 104, so that the operating condition of the twin-screw compressor 100 is removed from the over-compression state.

[0038] Through the above implementation method, the controller directly controls the opening and closing of the oil solenoid valve based on the pressure difference between the exhaust chamber 104 and the end pressure of the compression chamber 109 detected by the differential pressure sensor 112. This allows for faster and more stable control of the slide valve 108 to move to a suitable position, ensuring that the pressure in the exhaust chamber 104 of the twin-screw compressor 100 is equal to the end pressure of the compression chamber 109. This avoids over-compression or under-compression, improves the working efficiency of the twin-screw compressor 100, and reduces the complexity of using multiple pressure sensors and slide valve 108 displacement sensors to control the movement of the slide valve 108.

[0039] In one or more embodiments, the twin-screw compressor 100 further includes a slide valve detection groove 115.

[0040] Specifically, the slide valve detection groove 115 is provided on the slide valve 108 in a slotted manner that extends along the moving direction of the slide valve 108 in a manner that communicates with the pressure detection port 111 at the end of the compression chamber, and the length of the slide valve detection groove 115 in the moving direction of the slide valve 108 is greater than or equal to the movable distance of the slide valve 108.

[0041] Through the above implementation, a slide valve detection groove 115 is provided at the slide valve 108, communicating with the pressure detection port 111 at the end of the compression chamber. This allows the gas at the end of the compression chamber 109 to flow through the slide valve detection groove 115 to the pressure detection port 111 at the end of the compression chamber, thereby transmitting the gas pressure at the end of the compression chamber 109 to the differential pressure sensor 112 for differential pressure detection. Simultaneously, by ensuring that the length of the slide valve detection groove 115 in the moving direction of the slide valve 108 is greater than or equal to the movable distance of the slide valve 108, even if the slide valve 108 moves to any movable position in the direction approaching / away from the compressor exhaust port 102 under the control of the controller, it can be guaranteed that the pressure detection port 111 at the end of the compression chamber 109 can always be connected through the slide valve detection groove 115. This avoids the problem that the movement of the slide valve 108 might prevent the gas at the end of the compression chamber 109 from flowing to the differential pressure sensor 112, ensuring the stability of the twin-screw compressor 100 in controlling the movement of the slide valve 108 based on the difference between the pressure in the exhaust chamber 104 and the pressure at the end of the compression chamber 109.

[0042] In one or more embodiments, the twin-screw compressor 100 further includes a slide valve air passage 116 provided in the slide valve 108 in a direction perpendicular to the moving direction of the slide valve 108, and the slide valve detection groove 115 is connected to the compression chamber 109 through the slide valve air passage 116. Specifically, the slide valve air passage 116 is provided at the end of the slide valve 108 near the compressor exhaust port 102.

[0043] In the above-described embodiment, the slide valve detection groove 115 is connected to the compression chamber 109 through the slide valve air passage 116. Part of the gas in the compression chamber 109 can flow through the slide valve air passage 116 to the slide valve detection groove 115, and further flow through the compression chamber end pressure detection port 111 connected to the slide valve detection groove 115 to the differential pressure sensor 112, which detects and outputs the difference between the pressure of the exhaust chamber 104 of the twin-screw compressor 100 and the pressure at the end of the compression chamber 109, and then controls the slide valve 108 to move according to the difference.

[0044] Because the slide valve air passage 106 is located at the end of the slide valve 108 near the compressor exhaust port 102, the end pressure of the compression chamber 109 can be detected through the slide valve air passage 116 regardless of the position of the slide valve 108, thereby improving the accuracy of the differential pressure sensor 112.

[0045] In one or more embodiments, the position of the pressure detection port 111 at the end of the compression chamber is set such that when the slide valve 108 is at the end of its stroke closest to the exhaust chamber 104, it can still maintain communication with the slide valve detection groove 115.

[0046] Through the above implementation, even when the slide valve 108 moves to the end of its stroke closest to the exhaust chamber 104 in the direction close to the compressor exhaust port 102 under the control of the controller, it can be ensured that the pressure detection port 111 at the end of the compression chamber can always be connected to the end of the compression chamber 109 through the slide valve detection groove 115. This avoids the problem that the movement of the slide valve 108 may prevent the gas at the end of the compression chamber 109 from flowing to the differential pressure sensor 112. It ensures the stability of the twin-screw compressor 100 in controlling the movement of the slide valve 108 according to the difference between the exhaust pressure and the pressure at the end of the compression chamber 109.

[0047] In one or more embodiments, the twin-screw compressor 100 further includes a first maintenance valve 117 disposed on the pipeline connected to the differential pressure sensor 112 corresponding to the exhaust chamber pressure detection port 110, and a second maintenance valve 118 disposed on the pipeline connected to the differential pressure sensor 112 corresponding to the compression chamber end pressure detection port 111.

[0048] When the differential pressure sensor 112 needs to be repaired or replaced, the first maintenance valve 117 and the second maintenance valve 118 are closed, preventing the gas inside the twin-screw compressor 100 from flowing to the outside of the exhaust chamber housing 101b of the twin-screw compressor 100 through the exhaust chamber pressure detection port 110, or to the outside of the compression chamber housing 101a of the twin-screw compressor 100 through the compression chamber end pressure detection port 111. This allows the differential pressure sensor 112 to be disassembled, repaired, or replaced without the need to recover the gas inside the twin-screw compressor 100.

[0049] In one or more embodiments, the first maintenance valve 117 and the second maintenance valve 118 may be configured as shut-off valves.

[0050] Through the above implementation, using shut-off valves as the first maintenance valve 117 and the second maintenance valve 118, when the differential pressure sensor 112 is connected to the first maintenance valve 117 and the second maintenance valve 118 via a pipeline, the shut-off valve is internally connected, allowing gas in the exhaust chamber 104 or gas at the end of the compression chamber 109 to flow into the differential pressure sensor 112 through the exhaust chamber pressure detection port 110 or the compression chamber end pressure detection port 111. When the pipeline connecting the differential pressure sensor 112 to the first maintenance valve 117 and the second maintenance valve 118 is disconnected, the first maintenance valve 117 and the second maintenance valve 118 are automatically shut off, preventing gas in the exhaust chamber 104 or gas at the end of the compression chamber 109 from flowing to the outside of the exhaust chamber housing 101b through the exhaust chamber pressure detection port 110 or to the outside of the compression chamber housing 101a through the compression chamber end pressure detection port 111. This more conveniently avoids the problem of gas leakage inside the twin-screw compressor 100 that may occur when repairing or replacing the differential pressure sensor 112.

[0051] In one or more embodiments of this application, a refrigeration device is also provided, which includes a compressor, a condenser, an expansion valve and an evaporator connected in sequence through refrigerant pipes, wherein the compressor is a twin-screw compressor 100 provided in one or more embodiments of this application.

[0052] In one or more embodiments of this application, a gas compression device is also provided, specifically an air compression device, wherein the compressor in the gas compression device is the twin-screw compressor 100 provided in one or more embodiments of this application.

[0053] The above are merely optional embodiments of this application and are not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A twin screw compressor, characterized in that, include: A housing with a compressor exhaust port at one end, the housing enclosing and forming a cylinder; An exhaust chamber is located at one end of the cylinder near the compressor exhaust port; The screw rotor, disposed inside the cylinder, includes a pair of meshing female rotors and male rotors; A slide valve is movably disposed inside the cylinder in a form that is parallel to and adjacent to the screw rotor axis, and the slide valve and the screw rotor enclose a compression chamber. An exhaust chamber pressure detection port is provided in the housing in a manner that communicates with the exhaust chamber; The pressure detection port at the end of the compression chamber is provided in the housing in a manner that communicates with the end of the compression chamber near the exhaust chamber; A differential pressure sensor, one end of which is connected to the pressure detection port of the exhaust chamber, and the other end of which is connected to the pressure detection port at the end of the compression chamber; The controller can receive the output of the differential pressure sensor and control the movement of the slide valve based on the pressure difference between the exhaust chamber pressure and the end pressure of the compression chamber detected by the differential pressure sensor.

2. Twin screw compressor according to claim 1, characterized in that Also includes: A hydraulic cylinder is formed by the housing, and one end of the cylinder is provided with a through hole, which communicates with the cylinder. The piston rod is located inside the hydraulic cylinder and is fixedly connected to the slide valve through the through hole.

3. Double screw compressor according to claim 2, characterized in that Also includes: The oil solenoid valve is connected to the hydraulic cylinder via an oil pipeline.

4. Twin screw compressor according to claim 3, characterized in that Also includes: A valve detection groove is provided on the valve in a way that connects to the pressure detection port at the end of the compression chamber. The groove extends along the moving direction of the valve and is greater than or equal to the movable distance of the valve.

5. Double screw compressor according to claim 4, characterized in that Also includes: The slide valve air passage is opened in the slide valve in a direction perpendicular to the movement direction of the slide valve, connecting the slide valve detection groove and the compression chamber.

6. The twin-screw compressor according to claim 5, characterized in that, The position of the pressure detection port at the end of the compression chamber is configured such that when the slide valve is at the end of its stroke closest to the exhaust chamber, it can still maintain communication with the slide valve detection slot.

7. Double screw compressor according to claim 6, characterized in that Also includes: The first maintenance valve is installed on the pipeline connected to the differential pressure sensor, corresponding to the pressure detection port of the exhaust chamber; The second maintenance valve is installed on the pipeline connected to the differential pressure sensor, corresponding to the pressure detection port at the end of the compression chamber.

8. The twin-screw compressor according to claim 7, characterized in that, The first maintenance valve and the second maintenance valve are shut-off valves.

9. A refrigeration device, comprising a compressor, a condenser, an expansion valve, and an evaporator connected in sequence via refrigerant pipes, characterized in that, The compressor is a twin-screw compressor as described in any one of claims 1-8.

10. A gas compression device comprising a compressor, characterized in that The compressor is a twin-screw compressor as described in any one of claims 1-8.

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