High-pressure heavy-load piston compressor for supercritical carbon dioxide

Abstract

The utility model relates to a high-pressure heavy-load piston compressor for supercritical carbon dioxide. The high-pressure heavy-load piston compressor comprises a compressor body, a driving motor and a compressor shell, the compressor body comprises a plurality of air cylinders, each air cylinder comprises an air cylinder body and an air cylinder cover which are sequentially arranged from bottom to top, a compression chamber is arranged in each air cylinder body, a piston is arranged in each compression chamber, and an exhaust cavity located at the top of each compression chamber is formed in each air cylinder cover; the upper end of the main piston is provided with an auxiliary piston which protrudes upwards and can stretch into the exhaust cavity when the piston moves to the upper dead center, and the auxiliary piston is of a smooth curved surface structure. By optimizing the auxiliary piston, the motion resistance of the piston is reduced, the efficiency of the compressor is improved, and the failure risk of the auxiliary piston is reduced; the larger width of the bearing bush can stably transmit larger piston force, and abrasion of a connecting pair can be reduced, so that the service life of the bearing bush is prolonged, the capacity of the connecting rod for resisting toppling moment is improved, and an air cylinder operates more stably.

Description

Technical Field

[0001] This utility model relates to the field of gas compressors, and in particular to a high-pressure heavy-duty piston compressor for supercritical carbon dioxide. Background Technology

[0002] Supercritical carbon dioxide is the state of carbon dioxide gas after it has been compressed under high pressure to a temperature and pressure exceeding critical values. Due to its significantly higher density and lower viscosity compared to conventional fluids, supercritical carbon dioxide has become an ideal heat exchange medium for advanced refrigeration, heat pump, and hot water systems. To compress carbon dioxide to its supercritical state, the compressor faces the challenges of high pressure, high temperature, and heavy load; therefore, a high-efficiency, high-reliability, high-pressure, heavy-duty piston compressor is indispensable.

[0003] In piston compressors, the exhaust valve and cylinder top surface contain an exhaust cavity, which reduces the compressor's compression ratio. For high-pressure, heavy-duty compressors, this exhaust cavity causes significant efficiency loss. Current improvement methods involve adding a protrusion structure to the piston top to reduce compression efficiency loss; however, under high pressure and high temperature conditions, this results in significant flow resistance and concentration of temperature and stress fields, negatively impacting compressor efficiency and lifespan.

[0004] In high-pressure, heavy-duty compressors, the piston experiences large and complex forces. To ensure stable piston operation, a reliable connection between the connecting rod and crankshaft is crucial. The rotating joint between the connecting rod and crankshaft not only bears enormous piston forces but also needs to resist the tilting torque caused by unbalanced piston forces. Traditional low-journey rotating joints struggle to suppress the oscillation of the connecting rod and piston under high pressure and heavy loads, easily leading to compressor vibration and affecting compressor efficiency and lifespan.

[0005] High-pressure, heavy-duty compressor cylinders experience extremely high pressure, subjecting the inner walls to immense pressure and friction, leading to severe wear. In traditional piston compressors, the cylinder wall and cylinder body are a single unit; when wear occurs, the entire cylinder structure needs replacement, increasing maintenance complexity and cost. Furthermore, reducing cylinder wall wear requires more wear-resistant materials, further increasing the manufacturing cost of traditional one-piece cylinder structures. Therefore, ensuring cylinder durability while controlling costs is a critical challenge in the design and manufacture of high-pressure, heavy-duty compressors. Utility Model Content

[0006] In view of this, the purpose of this utility model is to provide a high-pressure heavy-duty piston compressor for supercritical carbon dioxide, which reduces piston movement resistance, improves compressor efficiency, and achieves high-pressure, high-temperature, high-efficiency, and stable gas compression.

[0007] This utility model is achieved using the following scheme: a high-pressure heavy-duty piston compressor for supercritical carbon dioxide, comprising a compressor body, a drive motor, and a compressor housing; the compressor body includes several cylinders, each cylinder including a cylinder body and a cylinder head arranged sequentially from bottom to top, a compression chamber provided in the cylinder body, a piston provided in the compression chamber, and an exhaust cavity located at the top of the compression chamber on the cylinder head, the piston including a main piston that works in conjunction with the compression chamber, and an auxiliary piston with an upward protrusion at the upper end of the main piston that can extend into the exhaust cavity when the piston reaches the top dead center, the auxiliary piston having a smooth curved surface structure.

[0008] Furthermore, the upper end of the auxiliary piston is provided with an upwardly raised curved top, and the lower periphery of the auxiliary piston has a constricted neck. The curved top and the constricted neck are connected by an arc-shaped drum.

[0009] Furthermore, the vertical cross-sectional profile of the attached piston is a curve, including a top windward section, two side necking sections, and two side transition sections, which are connected sequentially from top to bottom.

[0010] Furthermore, the upper end of the vertical cross-sectional profile of the main piston has a top surface gentle section located on both sides of the vertical cross-sectional profile of the auxiliary piston. The inner end point of the top surface gentle section is connected to the lower end point of the side transition section, and the outer end point of the top surface gentle section is connected to the upper edge line of the side of the main piston.

[0011] Furthermore, a cylinder liner is detachably fitted inside the compression chamber, and the main piston of the piston slides in conjunction with the cylinder liner. An annular groove is provided around the main piston, and a sealing ring is provided in the annular groove.

[0012] Furthermore, the cylinder liner has a flange on its upper outer periphery, and the compression chamber has an annular mounting groove on its upper periphery that mates with the flange.

[0013] Furthermore, the main shaft of the drive motor is coaxially connected to the crankshaft via a coupling; a connecting rod assembly is provided below the piston, the connecting rod assembly includes a connecting rod body whose small end is hinged to the main piston of the piston via a piston pin, and a seat fixedly connected to the large end of the connecting rod body, the seat housing containing a bearing bush that rotatably engages with the connecting rod journal on the crankshaft.

[0014] Furthermore, the axial width of the seat sleeve is consistent with the axial width of the bearing bush, the axial width of the bearing bush is 2 to 8 times the thickness of the connecting rod body, and the axial width of the bearing bush is greater than the diameter of the bearing bush.

[0015] Furthermore, the cylinder head is provided with an air inlet located at the top of the compression chamber, an air inlet valve is provided at the air inlet, and an air inlet pipe communicating with the air inlet is provided above the cylinder.

[0016] Furthermore, an exhaust pipe communicating with the exhaust cavity is provided above the cylinder, and an exhaust valve is provided at the opening of the exhaust cavity.

[0017] Compared with the prior art, the present invention has the following beneficial effects:

[0018] (1) By optimizing the auxiliary piston and designing it as a smooth curved surface structure, the piston movement resistance is reduced and the compressor efficiency is improved. On the other hand, the temperature concentration and stress concentration at the top of the piston under high temperature and high pressure conditions are reduced, thus reducing the risk of failure of the auxiliary piston.

[0019] (2) The larger bearing width increases the contact area between the connecting rod and the crankshaft, and reduces the contact pressure between the connecting rod and the crankshaft. This not only enables the stable transmission of greater piston force, but also reduces the wear of the connecting parts, thereby improving the bearing life, improving the connecting rod's ability to resist tilting torque, making the cylinder run more smoothly, thereby reducing compressor operating vibration and improving the compressor's dynamic performance.

[0020] (3) The cylinder liner is removable and replaceable, which improves the wear resistance of the cylinder inner surface and reduces maintenance costs.

[0021] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below through specific embodiments and related drawings. Attached Figure Description

[0022] Figure 1 This is a cross-sectional view of the compressor according to an embodiment of the present invention;

[0023] Figure 2 This is a schematic diagram of the connecting rod assembly according to an embodiment of the present utility model;

[0024] Figure 3 This is a schematic diagram of a cylinder liner according to an embodiment of the present invention;

[0025] Figure 4 This is a perspective view of the piston with the piston located at the center, according to an embodiment of the present invention;

[0026] Figure 5 This is a contour curve of the piston with the piston located at the center in an embodiment of this utility model;

[0027] Figure 6 This is a piston profile curve diagram showing the piston offset from the center in an embodiment of this utility model;

[0028] Figure 7 This is a piston profile curve diagram of an embodiment of the present invention, where the piston cross-section is non-circular; Detailed Implementation

[0029] It should be noted that the following detailed descriptions are exemplary and intended to provide further explanation of this application. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0030] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0031] like Figures 1-7 As shown, a high-pressure heavy-duty piston compressor for supercritical carbon dioxide includes a compressor body 10, a drive motor 20, and a compressor housing 30. The compressor body 10 includes several cylinders, each cylinder comprising a cylinder body 104 and a cylinder head 106 arranged sequentially from bottom to top. The cylinder body 104 is the main structure of the cylinder and is integrally formed with the compressor housing. A compression chamber is provided inside the cylinder body 104, and a piston 110 is provided inside the compression chamber. An exhaust cavity 121 located at the top of the compression chamber is provided on the cylinder head 106. The piston 104 includes a main piston 111 that works in conjunction with the compression chamber. An auxiliary piston 112 protrudes upward at the upper end of the main piston and extends into the exhaust cavity when the piston reaches top dead center. The auxiliary piston 112 has a smooth curved surface structure. The centerline of the auxiliary piston may be consistent with or inconsistent with the centerline of the main piston, i.e., it may deviate from the center position. When the piston reaches top dead center, the auxiliary piston extends into the exhaust cavity formed by the bottom surface of the cylinder head and the exhaust valve, thereby improving the compression efficiency of the compressor. The auxiliary piston 112 has a complete smooth curved surface. On the one hand, the smooth air-facing surface structure reduces piston movement resistance and improves compressor efficiency; on the other hand, the smooth curved surface alleviates temperature and stress concentration at the piston top under high temperature and high pressure conditions, reducing the failure risk of the auxiliary piston 112 and extending piston life, thereby achieving high-pressure, high-temperature, high-efficiency, and stable gas compression. This compressor can be applied to gas compression of different displacements and can be used in high-efficiency refrigeration, heat pump, and hot water systems. The compressor body contains an integer number of cylinders greater than or equal to one; in this embodiment, the number of cylinders is three.

[0032] The cross-sectional shape (i.e., the cross-section) of the piston in the direction orthogonal to its centerline can be circular (e.g.) Figure 4 (as shown) or other closed figures, such as ellipses or parallelograms (e.g. Figure 7(As shown). The crank-connecting rod-piston mechanism and intake-exhaust mechanism of a piston compressor are often asymmetrical structures. When facing the stringent requirements of structural stress and exhaust airflow, the curved surface of the attached piston 112 can be designed as a closed surface with a non-circular cross-section. The aerodynamic force generated by the curved surface of the attached piston 112 during movement can improve the dynamic characteristics of the piston and reduce compressor vibration. The curved surface of the attached piston 112 can also improve the flow state of the exhaust airflow.

[0033] In this embodiment, the vertical cross-sectional profile of the attached piston 112 is a curve, including a top windward section 14, side necking sections 15, and side transition sections 16. The top windward section 14, side necking sections 15, and side transition sections 16 are connected sequentially from top to bottom; that is, the upper end point of the side transition section 16 is connected to the lower end point of the side necking section 15, and the lower ends of the top windward section 14 are connected to the upper ends of the side necking sections 15. The curves of the attached piston 112 are interconnected to form a complete curved profile.

[0034] The cross-sectional area of ​​the top windward section 14, which is orthogonal to the top centerline 13, decreases upward along the direction of the top centerline to near zero; the cross-sectional area of ​​the side necking section 15, which is orthogonal to the top centerline 13 (the centerline of the main piston 111 is defined as the top centerline 13), decreases slowly downward along the direction of the top centerline, forming a curved surface with a small cross-sectional area and a smooth transition along the direction of the top centerline; the cross-sectional area of ​​the side transition section 16, which is orthogonal to the top centerline, decreases from the cross-sectional area at the upper end of the top flat section to the cross-sectional area at the lower end of the side necking section.

[0035] The top windward section 14 is located at the top of the auxiliary piston 112. The curved surface formed by the top windward section 14 directly faces the gas during the compression process. As the compression process proceeds, the gas pressure, temperature, and density increase, and the gas resistance faced by the curved surface of the top windward section 14 increases sharply. To reduce the piston running resistance, the cross-sectional area of ​​the auxiliary piston 112 corresponding to the top windward section 14 (i.e., the top of the curved surface) is reduced to a near-zero value along the height of the cross-section to prevent high-pressure, high-temperature gas from accumulating above the top windward section 14 and reduce the aerodynamic resistance during piston movement. Preventing the accumulation of high-pressure, high-temperature gas above the top windward section 14 also reduces the maximum temperature of the auxiliary piston 112. The side constriction section 15 is a smoothly transitioning curve. The curved surface formed here allows the auxiliary piston 112 to extend into the exhaust cavity, allowing the gas in the exhaust cavity to participate in compression, thereby reducing compression ratio loss. The lower edge of the curved surface of the top air-facing section 14 is smoothly connected to the upper edge of the curved surface of the side necking section 15, allowing the high-pressure airflow to flow smoothly and reducing gas resistance during piston movement. The top gentle section 17 is connected to the upper edge of the side of the main piston 111, making the auxiliary piston 112 the upper end face of the main piston 111. The top gentle section 17 is a curved surface that coincides with or gently rises from the top horizontal surface 12, and the top gentle section 17 is the main compression surface of the main piston 111. The side transition section 16 is the transition surface between the side necking section 15 and the top flat section 17. The upper edge of the curved surface of the side transition section 16 is connected to the lower edge of the curved surface of the side necking section 15, and the lower edge of the curved surface of the side transition section 16 is connected to the inner edge of the curved surface of the top flat section. The side transition section 16 prevents high temperature and high pressure gas from accumulating between the side necking section 15 and the top flat section 17, further reducing the piston movement resistance, and at the same time reducing the concentration of temperature field and stress field.

[0036] In this embodiment, the top windward section 14 is semi-elliptical, the side necking section 15 is S-shaped, and the side transition section 16 is circular.

[0037] In this embodiment, the upper end of the vertical cross-sectional profile of the main piston 111 has a top surface smooth section 17 located on both sides of the vertical cross-sectional profile of the auxiliary piston. The inner end point of the top surface smooth section 17 is connected to the lower end point of the side transition section, and the outer end point of the top surface smooth section 17 is connected to the upper edge of the side of the main piston 21.

[0038] In this embodiment, the top surface flat section 17 may coincide with the top surface horizontal plane 12 (the plane enclosed by the upper edge of the side of the main piston 111 is defined as the top surface horizontal plane 12), or it may be a flat curve that is higher than the top surface horizontal plane 12.

[0039] In this embodiment, a cylinder liner 105 is detachably fitted inside the compression chamber. The main piston 111 of the piston 110 slides in conjunction with the cylinder liner 105. An annular groove is provided around the main piston, and a sealing ring is provided in the annular groove. Each cylinder is equipped with a replaceable cylinder liner 105, which is independently installed in the cylinder body. The piston is installed inside the replaceable cylinder liner 105 and can perform reciprocating linear motion within the cylinder liner 105. When the cylinder liner 105 is severely worn, each cylinder liner can be replaced individually, avoiding the problem of having to replace multiple cylinders in the traditional integrated cylinder structure, thus reducing maintenance costs. In addition, the cylinder liner 105 can be made of wear-resistant materials such as ductile iron to improve the wear resistance of the inner surface of the cylinder and improve the operational reliability of the compressor.

[0040] In this embodiment, the cylinder liner 24 has a flange on its upper outer periphery, and the compression chamber has an annular mounting groove that mates with the flange on its upper periphery. The flange is connected to the annular mounting groove by screws.

[0041] In this embodiment, the main shaft of the drive motor 20 is coaxially connected to the crankshaft 101 via a coupling 21; a connecting rod assembly 102 is provided below the piston 110, the connecting rod assembly 102 includes a connecting rod body 124 whose small end 125 is hinged to the main piston 111 of the piston 110 via a piston pin 103, and a seat 123 fixedly connected to the large end 126 of the connecting rod body 124, and a bearing bush 127 that rotates with the connecting rod journal on the crankshaft 101 is nested inside the seat 123.

[0042] In this embodiment, the axial width of the seat sleeve 123 is consistent with the axial width W of the bearing bush 127, and the axial width W of the bearing bush 127 is 2 to 8 times the thickness of the connecting rod body 124, and the axial width W of the bearing bush 127 is greater than the bearing bush diameter D. The connecting rod assembly adopts a wide bearing bush structure. The larger bearing bush width increases the contact area between the connecting rod and the crankshaft, reduces the contact pressure between the connecting rod and the crankshaft, which not only can stably transmit a larger piston force, but also reduces the wear of the connecting pair, thereby improving the bearing bush life. In addition, the wider bearing bush improves the connecting rod's ability to resist the tilting moment caused by the unbalanced piston force, making the crank-connecting rod-piston mechanism run more smoothly, reducing the tilting piston vibration caused by uneven piston force, thereby reducing compressor operating vibration and improving the compressor's dynamic performance.

[0043] In this embodiment, the cylinder head 106 is provided with an air inlet located at the top of the compression chamber, an air inlet valve 109 is provided at the air inlet, and an air inlet pipe 107 communicating with the air inlet is provided above the cylinder.

[0044] In this embodiment, an exhaust pipe 108 communicating with the exhaust cavity is provided above the cylinder, and an exhaust valve 120 is provided at the opening of the exhaust cavity.

[0045] The cylinder block, cylinder liner, master piston, and cylinder head together form a cylinder. Driven by the connecting rod, the master piston reciprocates along the straight line between top dead center and bottom dead center, continuously completing the intake-compression-exhaust process to compress carbon dioxide gas. The compression chamber volume is smallest when the master piston is at top dead center and largest when it is at bottom dead center.

[0046] The intake-compression-exhaust process of the cylinder is as follows: First, when the main piston is at top dead center, the exhaust valve 29 is closed and the intake valve is open. Then, as the main piston moves from top dead center to bottom dead center, the volume of the compression chamber gradually increases, and carbon dioxide gas enters the compression chamber from the intake port. When the main piston reaches the bottom dead center position, the intake valve closes, completing the intake process. Next, the main piston moves from bottom dead center to top dead center, and the volume of the compression chamber decreases, completing the compression process. The carbon dioxide gas is compressed in the compression chamber, and once a certain pressure is reached, the exhaust valve opens, and the compressed carbon dioxide gas is discharged from the compression chamber into the exhaust pipe. Then, the exhaust valve closes, completing the exhaust process.

[0047] like Figure 1 As shown, the exhaust cavity is located on the cylinder head. In traditional compressors, because the auxiliary piston is flat, the volume of the exhaust cavity does not change during compression and exhaust, which reduces the compression ratio of the cylinder to some extent. For high-pressure, heavy-duty compressors, the compression ratio loss caused by the exhaust cavity will significantly affect the compressor performance. Therefore, it is necessary to change the volume of the exhaust cavity during compression. The conventional method to change the volume of the exhaust cavity is to set a protrusion with a flat top surface on the auxiliary piston. During compression, the protrusion enters the exhaust cavity, thereby reducing the impact of the exhaust cavity on the compression ratio. However, the geometric discontinuities of the traditional flat protrusion are prone to airflow accumulation, resulting in high resistance, temperature concentration, and stress concentration. These problems will greatly affect the efficiency and lifespan of the compressor when compressing high-temperature, high-pressure gases. Therefore, this invention changes the auxiliary piston 112 to a continuous curved surface structure. The auxiliary piston 112 extends into the exhaust cavity through the curved surface formed by the top necking section 15. Meanwhile, the top cross-sectional area of ​​the top air-facing section 14 is a near-zero minimum, thus preventing the accumulation of high-pressure, high-temperature airflow above the top air-facing section 14 during the high-speed upward movement of the main piston 111. This reduces piston movement resistance, minimizes stress and temperature concentration, and ultimately improves compressor efficiency and lifespan. Furthermore, by optimizing the curved surface design, the aerodynamic force generated by the auxiliary piston 112 during the movement of the main piston 111 can be used to stabilize the movement of the main piston 111, thereby reducing vibration during compressor operation.

[0048] Unless otherwise stated, if any of the technical solutions disclosed in this utility model discloses a numerical range, then the disclosed numerical range is a preferred numerical range. Any person skilled in the art should understand that the preferred numerical range is merely one among many feasible numerical values ​​that has a more obvious or representative technical effect. Because there are many numerical values, it is impossible to list them all. Therefore, this utility model discloses only some numerical values ​​to illustrate the technical solutions of this utility model. Furthermore, the numerical values ​​listed above should not constitute a limitation on the scope of protection of this utility model.

[0049] If this utility model discloses or relates to mutually fixedly connected parts or structural components, then unless otherwise stated, a fixed connection can be understood as: a detachable fixed connection (e.g., using bolts or screws), or a non-detachable fixed connection (e.g., riveting, welding). Of course, mutually fixed connections can also be replaced by an integral structure (e.g., manufactured by integral molding using a casting process) (except where it is obviously impossible to use an integral molding process).

[0050] In addition, unless otherwise stated, the terms used to indicate positional relationships or shapes in any of the technical solutions disclosed in this utility model above include states or shapes that are similar to, close to, or approximate with them.

[0051] Any component provided by this utility model can be assembled from multiple individual components, or it can be a single component manufactured by a one-piece molding process.

[0052] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model in any other way. Any person skilled in the art may make changes or modifications to the disclosed technical content to create equivalent embodiments. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of this utility model without departing from its technical solution shall still fall within the protection scope of this utility model.

Claims

1. A high-pressure heavy-duty piston compressor for supercritical carbon dioxide, characterized by: The compressor comprises a compressor body, a driving motor and a compressor shell; the compressor body comprises a plurality of cylinders, each of which comprises a cylinder body and a cylinder cover arranged in sequence from bottom to top, a compression chamber is arranged in the cylinder body, a piston is arranged in the compression chamber, an exhaust cavity is arranged on the cylinder cover at the top of the compression chamber, the piston comprises a main piston which cooperates with the compression chamber, an auxiliary piston is arranged on the upper end of the main piston and protrudes upward and can extend into the exhaust cavity when the piston runs to the top dead center, and the auxiliary piston is a smooth curved surface structure.

2. High-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1, characterized in that The upper end of the auxiliary piston is provided with a curved top which protrudes upward, the lower part of the auxiliary piston is provided with a necked part on the periphery, and the curved top and the necked part are connected by an arc-shaped drum part.

3. High-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1 or 2, characterized in that The vertical cross-sectional profile of the auxiliary piston is a curve, comprising a top surface windward section of the top, a side surface necked section on both sides and a side surface transition section on both sides, which are connected in sequence from top to bottom.

4. High-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 3, characterized in that The vertical cross-sectional profile of the main piston has a top surface gentle section on both sides of the vertical cross-sectional profile of the auxiliary piston at the upper end, the inner end point of the top surface gentle section is connected with the lower end point of the side surface transition section, and the outer end point of the top surface gentle section is connected with the upper edge line of the side surface of the main piston.

5. The high-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1, characterized in that: A cylinder liner is detachably arranged in the compression chamber, the main piston of the piston is in sliding cooperation with the cylinder liner, the peripheral part of the main piston is provided with an annular groove, and a sealing ring is arranged in the annular groove.

6. High-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 5, characterized in that A flange part is arranged on the outer periphery of the upper end of the cylinder liner, and an annular mounting groove matched with the flange part is arranged on the periphery of the upper end of the compression chamber.

7. The high-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1, characterized in that: The main shaft of the driving motor is coaxially connected with a crankshaft through a shaft coupling; a connecting rod assembly is arranged below the piston, the connecting rod assembly comprises a connecting rod body which is hingedly connected with the main piston of the piston through a piston pin at the small end, and a seat sleeve which is fixedly connected to the large end of the connecting rod body, and a bearing bush which is rotatably matched with the connecting rod journal on the crankshaft is nested in the seat sleeve.

8. High-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 7, characterized in that The axial width of the seat sleeve is consistent with the axial width of the bearing bush, the axial width of the bearing bush is 2-8 times the thickness of the connecting rod body, and the axial width of the bearing bush is greater than the diameter of the bearing bush.

9. The high-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1, characterized in that: An air inlet is arranged on the cylinder cover at the top of the compression chamber, an air inlet valve is arranged at the air inlet, and an air inlet pipe is arranged above the cylinder and is in communication with the air inlet.

10. The high-pressure heavy-duty piston compressor for supercritical carbon dioxide according to claim 1, characterized in that: An exhaust pipe is arranged above the cylinder and is in communication with the exhaust cavity, and an exhaust valve is arranged at the opening of the exhaust cavity.

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