A compressor cooling system suitable for multi-stage compression

Abstract

The application discloses a compressor cooling system suitable for multistage compression, which comprises a cooling water unit and oil cooling branches, front cooling branches, intermediate cooling branches and exhaust cooling branches arranged between the water outlet and the backwater outlet of the cooling water unit; the front cooling branches comprise a front cooler, a first cooling cylinder jacket and a second cooling cylinder jacket connected in series, the front cooler is used to cool the gas before entering the first-stage compression cylinder, and the first cooling cylinder jacket and the second cooling cylinder jacket are respectively used to cool the first-stage compression cylinder and the second-stage compression cylinder; an auxiliary cooling branch is arranged between the first cooling cylinder jacket and the second cooling cylinder jacket; the auxiliary cooling branch comprises an auxiliary cooler used to assist the cooling of the cooling liquid entering the second cooling cylinder jacket from the first cooling cylinder jacket. The application can improve the utilization rate of the cooling liquid of the compressor cooling system and efficiently exert the cooling efficiency of the cooling system.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors. More particularly, the present application relates to a compressor cooling system suitable for multi-stage compression. BACKGROUND

[0002] The cooling system is an important component of a liquid-driven hydrogen compressor sled body. The existing compressor sled body generally uses liquid cooling for cooling. Each cooler is connected to the liquid outlet and the liquid return of the cooling water unit or is separately connected to a cooling tower to form a cooling liquid circulation loop. Due to the different corresponding cooling positions, the cooling liquid requirements of each cooler are different, and the utilization rates of the cooling liquid circulation loops corresponding to the coolers are quite different, resulting in waste of the cooling capacity of the cooling system. For a multi-stage compression compressor, it generally includes two booster cylinders, and cooling cylinder sleeves are arranged on the two booster cylinders. Compared with the pre-cooler, the inter-stage cooler and the exhaust cooler, the cooling energy required by the cooling cylinder sleeves is less, and therefore a cooling system is needed to combine the cooling cylinder sleeves with the cooling liquid requirements of each cooler to improve the cooling efficiency of the cooling system. SUMMARY

[0003] An object of the present application is to solve at least the above problems and to provide at least the advantages described later.

[0004] In order to achieve these objects and other advantages according to the present application, a compressor cooling system suitable for multi-stage compression is provided. The compressor includes a driving oil cylinder, a first-stage booster cylinder and a second-stage booster cylinder. The cooling system includes a cooling water unit and an oil cooling branch, a pre-cooling branch, an intermediate cooling branch and an exhaust cooling branch arranged between the water outlet and the water return of the cooling water unit. The oil cooling branch, the intermediate cooling branch and the exhaust cooling branch each include an oil cooler for cooling hydraulic oil, an intermediate cooler arranged between the first-stage booster cylinder and the second-stage booster cylinder, and an exhaust cooler for cooling gas pressurized by the second-stage booster cylinder.

[0005] The pre-cooling branch comprises a pre-cooler, a first cooling cylinder jacket and a second cooling cylinder jacket connected in series, the pre-cooler is used to cool the gas before entering the first-stage supercharged cylinder, the first cooling cylinder jacket and the second cooling cylinder jacket are used to cool the first-stage supercharged cylinder and the second-stage supercharged cylinder respectively, an auxiliary cooling branch is arranged between the first cooling cylinder jacket and the second cooling cylinder jacket, control valves are arranged between the first cooling cylinder jacket and the second cooling cylinder jacket and at one end of the auxiliary cooling branch close to the first cooling cylinder jacket, the auxiliary cooling branch comprises an auxiliary cooler used to assist cooling the cooling liquid entering the second cooling cylinder jacket from the first cooling cylinder jacket, and the cooling medium in the auxiliary cooler is hydraulic oil cooled by the oil cooler, and temperature sensors are arranged at the liquid outlet of the first cooling cylinder jacket and the liquid inlet of the second cooling cylinder jacket.

[0006] Preferably, the hydraulic oil tank and the oil pump are further included, the hydraulic oil cooled by the oil cooler is returned to the hydraulic oil tank, the oil pump pumps the hydraulic oil from the hydraulic oil tank into two paths, one path enters the driving oil cylinder, and the other path enters the liquid inlet of the auxiliary cooler, and the hydraulic oil flowing out of the liquid outlet of the auxiliary cooler enters the oil cooler again for cooling.

[0007] Preferably, flow regulating valves are arranged at one end of the oil cooling branch, the pre-cooling branch, the intermediate cooling branch and the exhaust gas cooling branch close to the cooling water unit.

[0008] Preferably, the first cooling cylinder jacket and the second cooling cylinder jacket are the same in structure and each comprise a cylinder body and a spiral rib plate arranged in the cylinder body, the cylinder body is in a hollow cylindrical shape, a sealing sleeve of the cylinder body is arranged on the first-stage supercharged cylinder or the second-stage supercharged cylinder, the spiral rib plate divides the cylinder body and the outer wall of the first-stage supercharged cylinder or the second-stage supercharged cylinder into continuous spiral flow channels, and liquid inlets and liquid outlets are arranged on the cylinder body and communicate with both ends of the spiral flow channels respectively.

[0009] Preferably, a plurality of rib plate groups are arranged on the spiral flow channel at intervals along the direction of the cooling liquid flow, and each rib plate group comprises two rib plates arranged in a spreader shape along the direction of the cooling liquid flow.

[0010] Preferably, the bottom surface of the rib plate is fixedly connected with the spiral rib plate, the side of the rib plate facing the cooling liquid is an inclined surface, and the inclined surface is inclined upward along the direction of the cooling liquid flow.

[0011] Preferably, grooves are arranged at intervals on the spiral rib plate, and the length direction of the grooves intersects the direction of the cooling liquid flow.

[0012] Preferably, a plurality of heat pipe groups are embedded in the side wall of the primary and secondary supercharging cylinders along the length direction thereof, and the heat pipe groups comprise a plurality of heat pipes arranged in the circumferential direction of the first or second supercharging cylinder.

[0013] Preferably, the heat pipe is a hollow rectangular flat pipe, and a capillary structure is arranged on the inner wall of the heat pipe, and the capillary structure is filled with a cooling medium.

[0014] The present application at least has the following advantages:

[0015] 1. The compressor cooling system suitable for multi-stage compression provided by the present application connects a pre-cooler, a first cooling cylinder and a second cooling cylinder in sequence through pipelines to form a pre-cooling branch, so that the cooling liquid demand of an oil cooling branch, the pre-cooling branch, an intermediate cooling branch and an exhaust cooling branch tends to be close to each other, thereby improving the utilization rate of the cooling liquid of the entire cooling system. An auxiliary cooling branch is arranged between the first cooling cylinder and the second cooling cylinder to ensure the cooling efficiency of the second cooling cylinder after being connected in series, and the cooling medium of the auxiliary cooler is the hydraulic oil cooled by the oil cooler, so as to maximize the cooling efficiency of the cooling system.

[0016] 2. The compressor cooling system suitable for multi-stage compression provided by the present application establishes a spiral flow channel in the first cooling cylinder and the second cooling cylinder, and generates vortex when the cooling liquid flows through the spiral flow channel through a rib group or a groove, so that the cooling liquid can quickly and comprehensively cover the outer wall of the primary and secondary supercharging cylinders, thereby ensuring the cooling efficiency of the primary and secondary supercharging cylinders in the pre-cooling branch formed in series.

[0017] Other advantages, objects, and features of the present application will be apparent to those skilled in the art from the following description, and will be understood by those skilled in the art upon reading and understanding the present application. BRIEF DESCRIPTION OF DRAWINGS

[0018] Figure 1 A schematic diagram of the working principle of the compressor of the present application;

[0019] Figure 2 A schematic diagram of the structure of the pre-cooling branch of the present application;

[0020] Figure 3 A schematic diagram of one distribution mode of the heat pipe group of the present application;

[0021] Figure 4 A schematic diagram of the A-A cross-sectional structure of the present application; Figure 3

[0022] Figure 5 A schematic diagram of the structure of the rib of the present application; ​

[0023] Figure 6 Structure diagram of the groove according to the present application;

[0024] Figure 7 Structure diagram of the internal structure of the heat pipe according to the present application;

[0025] Figure 8 Structure diagram of another distribution mode of the heat pipe group according to the present application; DETAILED DESCRIPTION

[0026] The present application will be further described below in conjunction with the drawings, so that those skilled in the art can implement the present application according to the description and drawings.

[0027] It should be noted that the experimental methods described in the following embodiments are all conventional methods unless otherwise specified, and the reagents and materials can be obtained from commercial channels unless otherwise specified; in the description of the present application, the terms "lateral", "longitudinal", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like indicate the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0028] As shown in Figure 1 and Figure 2 The present application provides a compressor cooling system suitable for multi-stage compression, the compressor comprising a driving oil cylinder 3, a first-stage booster cylinder 2 and a second-stage booster cylinder 4, the cooling system comprising: a cooling water unit and an oil cooling branch, a front cooling branch, an intermediate cooling branch and an exhaust cooling branch arranged between the water outlet 7 and the return water inlet 12 of the cooling water unit; the oil cooling branch, the intermediate cooling branch and the exhaust cooling branch each comprising an oil cooler for cooling hydraulic oil, an intermediate cooler 7 arranged between the first-stage booster cylinder 2 and the second-stage booster cylinder 4, and an exhaust cooler 5 for cooling the gas pressurized by the second-stage booster cylinder;

[0029] The pre-cooling branch includes a pre-cooler 1, a first cooling cylinder liner 8, and a second cooling cylinder liner 11 connected in series. The pre-cooler 1 is used to cool the gas before it enters the first-stage booster cylinder 2. The first cooling cylinder liner 8 and the second cooling cylinder liner 11 are used to cool the first-stage booster cylinder 2 and the second-stage booster cylinder 4, respectively. An auxiliary cooling branch is provided between the first cooling cylinder liner 8 and the second cooling cylinder liner 11. A control valve 9 is provided between the first cooling cylinder liner 8 and the second cooling cylinder liner 11, as well as at the end of the auxiliary cooling branch near the first cooling cylinder liner 8. The auxiliary cooling branch includes an auxiliary cooler 10, which is used to assist in cooling the coolant entering the second cooling cylinder liner 11 from the first cooling cylinder liner 8. The cooling medium in the auxiliary cooler 10 is hydraulic oil cooled by the oil cooler. Temperature sensors are provided at the outlet of the first cooling cylinder liner 8 and the inlet of the second cooling cylinder liner 11.

[0030] In this technical solution, refer to Figure 1 , Figure 1 The arrows in the dashed lines indicate the direction of airflow. Under the action of hydraulic oil, the drive cylinder 3 compresses the gas by means of a piston in the first-stage booster cylinder 2 and the second-stage booster cylinder 4. The compressed gas is pre-cooled by the pre-cooler 1 and then enters the first-stage booster cylinder 2 for first-stage compression. During this process, the first-stage booster cylinder 2 is cooled by the first cooling cylinder liner 8. The gas after the first compression enters the intercooler 7 for cooling. Then it enters the second-stage booster cylinder 4 for second-stage compression. During this process, the second cooling cylinder liner 11 cools the second-stage booster cylinder 4. The gas after the second-stage compression enters the exhaust cooler 5, and after cooling, it enters the gas storage tank 6 for storage. During the compression process described above, the inlet and outlet of the intercooler 7 are connected to the outlet 7 and return port 12 of the cooling water unit via pipelines, forming the intermediate cooling branch; the inlet and outlet of the exhaust cooler 6 are connected to the outlet 7 and return port 12 of the cooling water unit via pipelines, forming the exhaust cooling branch; the oil cooler cools the hydraulic oil passing through the drive cylinder 3, and its inlet and outlet are connected to the outlet 7 and return port 12 of the cooling water unit via pipelines, forming the oil cooling branch. Compared to the oil cooler, the intercooler 7, and the exhaust cooler 6, the heat exchange requirements of the precooler 1, the first cooling cylinder liner 8, and the second cooling cylinder liner 11 are all lower. Therefore, to ensure that the heat exchange of each cooling branch is similar and to maximize the utilization rate of the cooling system, refer to... Figure 2 , Figure 2The arrows in the middle solid line are the flow directions of the cooling liquid. The pre-cooling cooler 1, the first cooling cylinder jacket 8 and the second cooling cylinder jacket 11 are connected in series through pipelines and communicated with the outlet 7 and the return port 12 of the cooling water unit to form the pre-cooling branch. An auxiliary cooling branch is arranged between the first cooling cylinder jacket 8 and the second cooling cylinder jacket 11 to ensure the cooling efficiency of the second cooling cylinder jacket 11 after being connected in series. In order to maximize the cooling capacity utilization rate of the cooling system, the cooling medium of the auxiliary cooler is the hydraulic oil cooled by the oil cooler. The temperature sensors arranged at the outlet of the first cooling cylinder jacket 8 and the inlet of the second cooling cylinder jacket 11 are used to determine whether the auxiliary cooling branch needs to be used. When the temperature of the cooling liquid measured by any temperature sensor exceeds the predetermined temperature, the control valve 9 on the auxiliary cooling branch is opened and the control valve between the first cooling cylinder jacket 8 and the second cooling cylinder jacket 11 is closed, so that the cooling liquid flowing out of the first cooling cylinder jacket 8 is further cooled by the auxiliary cooler 10 and then enters the second cooling cylinder jacket 11. When the temperature of the cooling liquid measured by any temperature sensor is lower than the predetermined temperature, the control valve 9 on the auxiliary cooling branch is closed and the control valve between the first cooling cylinder jacket 8 and the second cooling cylinder jacket 11 is opened, so that the cooling liquid flowing out of the first cooling cylinder jacket 8 directly enters the second cooling cylinder jacket 11.

[0031] Specifically, the hydraulic oil tank and the oil pump are further included. The hydraulic oil cooled by the oil cooler returns to the hydraulic oil tank. The oil pump pumps the hydraulic oil from the hydraulic oil tank into two paths. One path enters the driving oil cylinder 3 and the other path enters the inlet of the auxiliary cooler 19. The hydraulic oil flowing out of the outlet of the auxiliary cooler 10 reenters the oil cooler for cooling. The hydraulic oil in the hydraulic oil tank enters the driving oil cylinder 3 through the hydraulic oil pipe under the action of the oil pump. The hydraulic oil flowing out of the driving oil cylinder 3 returns to the hydraulic oil tank after being cooled by the oil cooler, forming a hydraulic oil circulation loop. The hydraulic oil entering the inlet of the auxiliary cooler 10 serves as the cooling medium to assist the cooling of the cooling liquid flowing out of the outlet of the first cooling cylinder jacket 8. The hydraulic oil after heat exchange in the auxiliary cooler 10 flows out of the outlet of the auxiliary cooler 10 and is cooled by the oil cooler again to return to the hydraulic oil circulation loop.

[0032] In another embodiment, the oil cooling branch, the pre-cooling branch, the intermediate cooling branch and the exhaust cooling branch are each provided with a flow regulating valve near one end of the cooling water unit. The flow regulating valve can be used to adjust the flow of the cooling liquid in each cooling branch according to different cooling requirements.

[0033] In another embodiment, with reference to Figure 3 andFigure 4 The first cooling cylinder sleeve 8 and the second cooling cylinder sleeve 11 are identical in structure, and each comprises a cylinder body 13 and a spiral rib plate 131 arranged in the cylinder body 13; the cylinder body 13 is in a hollow cylindrical shape, and is sealingly sleeved on the first-stage supercharging cylinder 2 or the second-stage supercharging cylinder 4; the spiral rib plate 131 divides the cylinder body 13 and the outer wall of the first-stage supercharging cylinder 2 or the second-stage supercharging cylinder 4 into a continuous spiral flow channel, and the cylinder body 13 is provided with a liquid inlet 133 and a liquid outlet 134, which are respectively communicated with two ends of the spiral flow channel.

[0034] In this technical scheme, the spiral rib plate 131 spirally extends along the axial direction of the first cooling cylinder sleeve 8 or the second cooling cylinder sleeve 11, and the spiral flow channel extends along the axial direction of the first cooling cylinder sleeve 8 or the second cooling cylinder sleeve 11; the cooling liquid enters the cylinder body 13 from the liquid inlet 133, quickly flows through the spiral flow channel, cools the outer wall of the first-stage supercharging cylinder 2 or the second-stage supercharging cylinder 4, and then flows out from the liquid outlet. The spiral rib plate 131 can make the cooling liquid quickly and comprehensively cover the outer wall of the supercharging cylinder, and improve the cooling efficiency.

[0035] In another embodiment, referring to Figure 4 and Figure 5 a plurality of rib plate groups are arranged on the spiral flow channel and spaced apart along the direction in which the cooling liquid flows, and each rib plate group comprises two rib plates 132 arranged in a spreader shape along the direction in which the cooling liquid flows.

[0036] The bottom surface of the rib plate 132 is fixedly connected with the spiral rib plate 131, one side of the rib plate 132 facing the cooling liquid is an inclined surface, and the inclined surface is inclined upward along the direction in which the cooling liquid flows.

[0037] One end between the two ends of the two rib plates 132 with a larger spacing is located at the lower flow end of the cooling liquid, and one end with a smaller spacing is located at the upper flow end of the cooling liquid, that is, the cooling liquid first passes through one end with a smaller spacing of the two rib plates 132, and then passes through one end with a larger spacing. When the cooling liquid passes through the rib plate group, a vortex effect is generated, thereby increasing the cooling and heat exchange efficiency of the cooling liquid on the first-stage supercharging cylinder 2 or the second-stage supercharging cylinder 4. In combination with the spiral flow channel, the cooling liquid is ensured to have a heat exchange efficiency under the vortex effect when quickly passing through the spiral flow channel, and high-efficiency cooling of the supercharging cylinder is achieved.

[0038] In another embodiment, grooves 135 are arranged on the spiral rib plate 131 and spaced apart, and the length direction of the grooves intersects the direction in which the cooling liquid flows. Referring to Figure 6The helical rib plate 131 is provided with grooves 135 intersecting the direction of the cooling liquid flow perpendicularly. The length direction of the grooves 135 can also be obliquely intersected with the direction of the cooling liquid flow. When the cooling liquid flows along the helical flow channel, it forms vortexes when encountering the grooves 135 intersecting the direction of the cooling liquid flow perpendicularly, so as to improve the heat exchange efficiency of the cooling liquid in the cylinder body 13.

[0039] In another embodiment, a plurality of heat pipe groups are embedded in the side wall of the primary supercharging cylinder 2 and the secondary supercharging cylinder 4 along the length direction thereof, and each heat pipe group comprises a plurality of heat pipes 14 arranged circumferentially along the primary supercharging cylinder 2 or the secondary supercharging cylinder 4.

[0040] The heat pipe 14 is a hollow rectangular flat tube, and the inner wall of the heat pipe is provided with a capillary structure filled with a cooling medium.

[0041] The heat pipe 14 increases the heat transfer efficiency of the side wall of the primary supercharging cylinder 2 and the secondary supercharging cylinder 4, so that the heat generated by the gas compression in the supercharging cylinder can be quickly transferred to the first cooling cylinder liner 8 and the second cooling cylinder liner 11 through the side wall, and then taken away by the cooling liquid in the cooling cylinder liner, thereby achieving efficient cooling of the supercharging cylinder. Figure 3 The heat pipes 14 in the heat pipe group can be arc-shaped and match the diameter of the supercharging cylinder, and the heat pipes 14 in one heat pipe group are embedded along the circumferential direction of the supercharging cylinder. Figure 8 The heat pipes 14 can also be arranged along the axis of the supercharging cylinder, and the heat pipes 14 in one heat pipe group are embedded along the circumferential direction of the supercharging cylinder. The heat pipe 14 is a phase change heat pipe, one side close to the inner wall of the supercharging cylinder is an evaporation zone, and the opposite side is a condensation zone. The cooling medium absorbs heat to evaporate into gas in the evaporation zone, releases heat to condense into liquid in the condensation zone, and returns to the evaporation zone through the capillary structure, while transferring the heat released during condensation to the outer wall of the supercharging cylinder. The capillary structure and the cooling medium can use the materials used in conventional heat pipes. Further, Figure 7 The capillary structure comprises a first capillary structure 141 arranged in the evaporation zone and a second capillary structure 143 arranged in the condensation zone, and a gap is left between the first capillary structure 141 and the second capillary structure 143. The pore size of the first capillary structure 141 is smaller than that of the second capillary structure 143, so that the capillary force of the first capillary structure 141 is greater than that of the second capillary structure 143, thereby enabling the condensed cooling medium to quickly return to the evaporation zone. A plurality of support columns 142 are arranged in the heat pipe 14 along the length direction thereof to ensure the strength of the heat pipe 14.

[0042] While embodiments of the application have been disclosed in connection with the above specification and drawings this description is not intended to limit the scope of the application and many modifications, enhancements, alternatives, and variations will become apparent to those skilled in the art from this disclosure. Accordingly, it is intended that the application not be limited to the described embodiments, but that it include all variations falling within the scope of the claims, and their equivalents.

Claims

1. A compressor cooling system suitable for multi-stage compression, the compressor comprising a drive cylinder, a first-stage booster cylinder, and a second-stage booster cylinder, characterized in that, The cooling system includes: a cooling water unit and an oil cooling branch, a pre-cooling branch, an intermediate cooling branch, and an exhaust cooling branch disposed between the outlet and return outlet of the cooling water unit; the oil cooling branch, the intermediate cooling branch, and the exhaust cooling branch each include an oil cooler for cooling hydraulic oil, an intermediate cooler disposed between the first-stage booster cylinder and the second-stage booster cylinder, and an exhaust cooler for cooling the gas pressurized by the second-stage booster cylinder; The pre-cooling branch includes a pre-cooler, a first cooling cylinder liner, and a second cooling cylinder liner connected in series. The pre-cooler is used to cool the gas before it enters the first-stage booster cylinder. The first and second cooling cylinder liners are used to cool the first-stage booster cylinder and the second-stage booster cylinder, respectively. An auxiliary cooling branch is provided between the first and second cooling cylinder liners. Control valves are provided between the first and second cooling cylinder liners and at the end of the auxiliary cooling branch near the first cooling cylinder liner. The auxiliary cooling branch includes an auxiliary cooler for auxiliary cooling of the coolant entering the second cooling cylinder liner from the first cooling cylinder liner. The cooling medium in the auxiliary cooler is hydraulic oil cooled by the oil cooler. Temperature sensors are provided at the outlet of the first cooling cylinder liner and the inlet of the second cooling cylinder liner. The first cooling cylinder liner and the second cooling cylinder liner have the same structure, both including a cylinder body and a spiral rib plate disposed in the cylinder body; the cylinder body is a hollow cylinder, and its sealing sleeve is disposed on the first-stage booster cylinder or the second-stage booster cylinder; the spiral rib plate separates the cylinder body from the outer wall of the first-stage booster cylinder or the second-stage booster cylinder into a continuous spiral flow channel, and the cylinder body is provided with a liquid inlet and a liquid outlet, which are respectively connected to the two ends of the spiral flow channel.

2. The compressor cooling system suitable for multi-stage compression as described in claim 1, characterized in that, It also includes a hydraulic oil tank and an oil pump. The hydraulic oil cooled by the oil cooler returns to the hydraulic oil tank. The oil pump pumps the hydraulic oil out of the hydraulic oil tank and divides it into two paths. One path enters the drive cylinder, and the other path enters the inlet of the auxiliary cooler. The hydraulic oil flowing out of the outlet of the auxiliary cooler then enters the oil cooler for cooling.

3. The compressor cooling system suitable for multi-stage compression as described in claim 1, characterized in that, The oil cooling branch, the pre-cooling branch, the intermediate cooling branch, and the exhaust cooling branch are all equipped with flow regulating valves at the ends near the cooling water unit.

4. The compressor cooling system suitable for multi-stage compression as described in claim 1, characterized in that, The spiral flow channel is provided with multiple rib groups at intervals along the direction of coolant flow, and each rib group includes two ribs arranged in a figure-eight shape along the direction of coolant flow.

5. The compressor cooling system suitable for multi-stage compression as described in claim 4, characterized in that, The bottom surface of the rib is fixedly connected to the spiral rib. The side of the rib facing the coolant is an inclined surface, and the inclined surface is inclined upward along the direction of coolant flow.

6. The compressor cooling system for multi-stage compression as described in claim 1, characterized in that, The spiral rib is provided with grooves at intervals, and the length direction of the grooves intersects the direction of coolant flow.

7. The compressor cooling system suitable for multi-stage compression as described in claim 1, characterized in that, Multiple heat pipe groups are embedded at intervals along the length of the sidewalls of the primary booster cylinder and the secondary booster cylinder, and each heat pipe group includes multiple heat pipes arranged at intervals along the circumference of the primary booster cylinder or the secondary booster cylinder.

8. The compressor cooling system for multi-stage compression as described in claim 7, characterized in that, The heat pipe is a hollow rectangular flat tube, and a capillary structure is provided on the inner wall of the heat pipe, which is filled with a cooling medium.

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