Pump body assembly for a compressor and compressor

Abstract

The application relates to the technical field of compressors and discloses a pump body assembly for a compressor. The pump body assembly comprises a cylinder, a flange and a sliding vane, the cylinder is provided with a first channel, a sliding vane groove and a working cavity, the flange is arranged on the axial end face of the cylinder, and the sliding vane is arranged in the sliding vane groove and can reciprocate in the direction towards or away from the working cavity. The sliding vane groove comprises a first end and a second end opposite in the radial direction of the cylinder, the first end of the sliding vane groove is communicated with the working cavity, the inlet of the first channel is communicated with an external gas source, the outlet of the first channel is communicated with the second end of the sliding vane groove, so that the airflow can push the sliding vane to move towards the working cavity, the sliding vane is provided with a second channel, the second channel is communicated with the first channel through the sliding vane groove, the end face of the sliding vane in the axial direction of the cylinder is provided with a groove, a movable sealing element is arranged in the groove, and the second channel is communicated with the groove, so that the airflow can drive the sealing element to float along the axial direction of the cylinder towards the flange. The application further discloses a compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, specifically to a pump body assembly for a compressor and a compressor. Background Technology

[0002] Currently, in roller compressors, the cylinder end face typically mates with a flange to form a sealed working chamber. The crankshaft drives the rollers to roll within the working chamber, and a vane is slidably positioned within a groove communicating with the working chamber. Through the dynamic contact between the vane head and the outer wall of the roller, the working chamber is divided into an intake chamber and an exhaust chamber. Poor contact between the vane and the roller, or failure of contact between the vane and the flange end face, will reduce the sealing performance of the working chamber, thereby affecting the compressor's performance.

[0003] The related technology features a sliding vane groove on the cylinder, with a sliding vane disposed within the groove. A force application channel communicating with the sliding vane groove is also provided on the cylinder. The first end of the sliding vane groove is connected to the cylinder, and the force application channel is located at the second end of the groove. Applying pressure to the sliding vane through the force application channel causes the vane to abut against the roller.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, although applying pressure to the slide plate through the force channel can improve the fit between the slide plate and the roller, wear will still occur between the slide plate and the flange end face due to friction during the reciprocating motion. This wear will compromise the sealing between the slide plate and the flange end face, resulting in a reduction in the sealing performance of the working cavity.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a pump body assembly for a compressor and a compressor to improve the sealing of the working chamber.

[0009] According to a first aspect of the present invention, a pump body assembly for a compressor is provided, including a cylinder, a flange, and a vane. The cylinder has a first channel, a vane groove, and a working chamber. The flange is disposed on the axial end face of the cylinder. The vane is disposed in the vane groove and is capable of reciprocating in a direction toward or away from the working chamber. The vane groove includes a first end and a second end that are radially opposite to each other along the cylinder. The first end of the vane groove is connected to the working chamber. The inlet of the first channel is connected to an external gas source, and the outlet of the first channel is connected to the second end of the vane groove, so that the airflow can push the vane toward the working chamber. The vane has a second channel that is connected to the first channel through the vane groove. The vane has a groove on its axial end face along the cylinder, and a movable seal is disposed in the groove. The second channel is connected to the groove, so that the airflow can drive the seal to float toward the flange along the cylinder axial direction.

[0010] Optionally, the end face includes a first end face and a second end face at opposite ends of the slide along the cylinder axis; the number of grooves is multiple, including a first groove and a second groove, the first groove being disposed on the first end face and the second groove being disposed on the second end face; the number of seals is multiple, including a first seal and a second seal, the first seal being disposed on the first groove and the second seal being disposed on the second groove.

[0011] Optionally, the second channel includes: a flow diversion channel connected to the slide groove, and the flow diversion channel extends radially along the cylinder; a first pressure-inducing channel, one end of which is connected to the flow diversion channel and the other end of which is connected to the first groove, and the first pressure-inducing channel extends axially toward the first groove along the cylinder; and a second pressure-inducing channel, one end of which is connected to the flow diversion channel and the other end of which is connected to the second groove, and the second pressure-inducing channel extends axially toward the second groove along the cylinder.

[0012] Optionally, there are multiple first pressure channels, which are evenly distributed along the radial direction of the cylinder; and / or, there are multiple second pressure channels, which are evenly distributed along the radial direction of the cylinder.

[0013] Optionally, the pump body assembly for the compressor also includes rollers disposed in the working chamber, with the sliding vane abutting against the outer wall surface of the rollers to divide the working chamber into an intake chamber and an exhaust chamber. The gas pressure of the external gas source is dynamically adjusted according to the gas pressure changes in the intake and exhaust chambers at different working stages of the compressor, and the gas pressure of the external gas source is greater than the gas pressure difference between the exhaust chamber and the intake chamber at the corresponding working stage.

[0014] Optionally, the flange is provided with a third channel, one end of which is an inlet for an external gas source, and the other end of which is connected to the first channel.

[0015] Optionally, the axial end face of the cylinder is provided with a first sealing groove, the first sealing groove is arranged around the inlet of the first channel, and a first sealing ring is provided in the first sealing groove to seal the connection between the third channel and the first channel; and / or, the axial end face of the flange is provided with a second sealing groove, the second sealing groove is arranged around the outlet of the third channel, and a second sealing ring is provided in the second sealing groove to seal the connection between the third channel and the first channel.

[0016] Optionally, the slider includes a slider tail facing the second end of the slider groove, and an elastic element is provided between the slider tail and the second end of the slider groove.

[0017] Optionally, when the slider moves from the slider groove toward the working cavity to its maximum displacement, the elastic element is in a free state.

[0018] According to a second aspect of the present invention, a compressor is provided, including a pump body assembly for the compressor as described in any of the above-disclosed embodiments.

[0019] The pump body assembly and compressor for a compressor provided in this disclosure can achieve the following technical effects:

[0020] An external gas source allows airflow to flow from the first channel into the second end of the vane groove. The pressure generated by this airflow directly acts on the vane, creating a continuous thrust. Part of the airflow propels the vane towards the working chamber, ensuring a tight fit between the vane and the compressor rollers, effectively improving the sealing between the intake and exhaust chambers. Another part of the airflow enters the groove from the vane groove via the second channel, using the airflow pressure to drive the seal to float axially towards the flange along the cylinder axis. This floating seal fills the wear gap between the vane's axial end face and the flange, dynamically compensating for changes in the gap between the vane and flange, thus improving the sealing performance. By utilizing the airflow pressure from the external gas source to sequentially move the vane and the seal, the pump assembly effectively improves the sealing performance of the working chamber, thereby increasing the compressor's volumetric efficiency.

[0021] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0022] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0023] Figure 1 This is a schematic diagram of the structure of a compressor provided in an embodiment of this disclosure;

[0024] Figure 2 This is a schematic diagram of the structure of a pump body assembly for a compressor provided in an embodiment of this disclosure;

[0025] Figure 3 This is a schematic diagram of another pump body assembly for a compressor provided in an embodiment of this disclosure;

[0026] Figure 4 This is a schematic diagram of another pump body assembly for a compressor provided in an embodiment of this disclosure;

[0027] Figure 5 This is a partial schematic diagram of a pump body assembly for a compressor provided in an embodiment of this disclosure;

[0028] Figure 6 This is a partial schematic diagram of another pump body assembly for a compressor provided in an embodiment of this disclosure;

[0029] Figure 7 This is a schematic diagram of the structure of a cylinder provided in an embodiment of this disclosure;

[0030] Figure 8 This is a schematic diagram of the structure of a slider provided in an embodiment of this disclosure;

[0031] Figure 9 This is a schematic diagram of another slider provided in an embodiment of this disclosure;

[0032] Figure 10 This is a schematic diagram of another slider provided in an embodiment of this disclosure;

[0033] Figure 11 yes Figure 10 A partially enlarged schematic diagram of part A shown;

[0034] Figure 12 This is a schematic diagram of another slider provided in an embodiment of this disclosure;

[0035] Figure 13 This is a schematic diagram of another slider provided in an embodiment of this disclosure;

[0036] Figure 14 yes Figure 13 A magnified view of part B shown;

[0037] Figure 15 This is a schematic diagram of the structure of a reinforcing member provided in an embodiment of this disclosure;

[0038] Figure 16 This is a schematic diagram of the assembly of an elastic element with a guide plate and a thrust plate according to an embodiment of this disclosure;

[0039] Figure 17This is a schematic diagram of the structure of a guide plate provided in an embodiment of this disclosure;

[0040] Figure 18 This is a schematic diagram of the structure of a thrust plate provided in an embodiment of this disclosure.

[0041] Figure label:

[0042] 10: Compressor; 101: Pump assembly;

[0043] 20: Cylinder; 21: First channel; 211: First axial channel; 212: Tangential channel; 22: Sliding vane groove; 221: First end of sliding vane groove; 222: Second end of sliding vane groove; 223: Rear groove wall; 224: Fixed mating part; 225: Fastening hole; 226: Sliding cavity; 227: Reset cavity; 228: Front cavity wall; 229: Suspension force surface; 23: Working cavity; 24: Axial end face of cylinder; 241: First sealing groove; 25: First sealing ring;

[0044] 30: Sliding plate; 301: First end face; 302: Second end face; 31: Second channel; 311: Diversion channel; 312: First pressure channel; 313: Second pressure channel; 32: Groove; 321: First groove; 322: Second groove; 33: Seal; 331: First seal; 332: Second seal; 34: Sliding plate tail; 341: Connecting mating part; 342: Limiting hole; 35: Sliding plate body; 351: Mounting groove; 352: Self-suspending block; 36: Sliding plate head; 37: Reinforcing member; 370: Hollow structure; 371: Protrusion; 3711: First end; 3712: Second end; 372: Transition part; 3721: First connecting rib; 3722: Second connecting rib; 373: Support part; 374: Buffer space;

[0045] 40: Roller; 41: Outer wall surface;

[0046] 50: Flange; 51: Third channel; 511: Radial channel; 512: Second axial channel;

[0047] 61: Elastic element; 62: Guide plate; 621: Connecting part; 622: Limiting column; 623: Flow hole; 63: Thrust plate; 631: Fixing part; 632: Fixing boss. Detailed Implementation

[0048] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0049] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0050] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0051] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0052] Unless otherwise stated, the term "multiple" means two or more.

[0053] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0054] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0055] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0056] Combination Figure 1-12 As shown, this disclosure provides a pump body assembly 101 for a compressor 10, including a cylinder 20, a flange 50, and a vane 30.

[0057] The cylinder 20 is provided with a first channel 21, a sliding vane groove 22, and a working chamber 23; the flange 50 is provided on the axial end face 24 of the cylinder; the sliding vane 30 is provided in the sliding vane groove 22, and the sliding vane 30 can reciprocate in a direction toward or away from the working chamber 23; wherein, the sliding vane groove 22 includes a first end and a second end that are radially opposite to each other along the cylinder 20, the first end 221 of the sliding vane groove is connected to the working chamber 23, the inlet of the first channel 21 is connected to an external gas source, and the outlet of the first channel 21 is connected to the second end 222 of the sliding vane groove, so that the airflow can push the sliding vane 30 toward the working chamber 23; the sliding vane 30 is provided with a second channel 31, the second channel 31 is connected to the first channel 21 through the sliding vane groove 22, the end face of the sliding vane 30 along the axial direction of the cylinder 20 is provided with a groove 32, the groove 32 is provided with a movable seal 33, and the second channel 31 is connected to the groove 32, so that the airflow can drive the seal 33 to float toward the flange 50 along the axial direction of the cylinder 20.

[0058] Combination Figure 4 As shown, the x1 axis indicates the tangential direction of the cylinder, the y1 axis indicates the radial direction of the cylinder, and the z1 axis indicates the axial direction of the cylinder.

[0059] The external gas source comes from the gas supply device outside the compressor, which is independent of the refrigerant system inside the compressor. The external gas source is connected to the compressor cylinder through a dedicated pipeline.

[0060] Using the pump body assembly 101 for compressor 10 provided in this embodiment, airflow from an external gas source flows into the second end 222 of the vane groove from the first channel 21. The pressure generated by the airflow directly acts on the vane 30, creating a continuous thrust on the vane 30. Part of the airflow pushes the vane 30 toward the working chamber 23, ensuring that the vane 30 and the rollers 40 of the compressor 10 remain in close contact, effectively improving the sealing performance between the intake and exhaust chambers of the working chamber 23. Another part of the airflow enters the groove 32 from the vane groove 22 through the second channel 31 of the vane 30, using the pressure of the airflow to drive the seal 33 to float axially toward the flange 50 along the cylinder 20. The floating seal 33 can fill the wear gap between the end face of the vane 30 along the cylinder 20 and the flange 50, dynamically compensating for changes in the gap between the vane 30 and the flange 50, thereby improving the sealing performance between the vane 30 and the flange 50. The pump body assembly 101 utilizes the airflow pressure from an external gas source to sequentially drive the vane 30 and the seal 33, which can effectively improve the sealing performance of the working chamber 23, thereby increasing the volumetric efficiency of the compressor 10.

[0061] Optionally, combined Figure 8 As shown, the height of the seal 33 is less than or equal to the height of the groove 32.

[0062] This prevents the seal 33 from protruding too high from the groove 32, thereby avoiding interference between the seal 33 and the flange 50 and causing wear.

[0063] Optionally, combined Figure 2-4 and Figure 9-10 As shown, the length and width dimensions of the seal 33 are adapted to the length and width dimensions of the groove 32 so that the seal 33 can simultaneously achieve floating and sealing.

[0064] This allows the seal 33 to exist stably and float freely within the groove 32, preventing it from becoming stuck due to being too large or failing to seal properly due to being too small. The groove 32 and the seal 33 are shaped to match, and their cross-sections at the end faces can be rectangular, providing uniform sealing pressure. Alternatively, the cross-sections of the groove 32 and the seal 33 at the end faces can also be other shapes.

[0065] Optionally, combined Figure 2 As shown, the first channel 21 includes a first axial channel 211 and a tangential channel 212. The first axial channel 211 extends along the axial direction of the cylinder 20, and one end of the first axial channel 211 is opened on the end face of the cylinder 20. The tangential channel 212 extends along the tangential direction of the cylinder 20. One end of the tangential channel 212 is connected to the other end of the first axial channel 211, and the other end of the tangential channel 212 is connected to the second end of the sliding groove.

[0066] The tangential direction of cylinder 20 refers to the circumferential tangential direction perpendicular to the axial direction of cylinder 20. The first channel 21 includes a first axial channel 211 extending along the axial direction of cylinder 20 and a tangential channel 212 extending along the tangential direction of cylinder 20. This allows the airflow direction to switch from axial to tangential before flowing into the vane groove 22, changing the path of the airflow into the vane groove 22 and providing a buffering and adjustment process before entering the vane groove 22, thereby improving the uniformity of the airflow. Simultaneously, this also extends the airflow path, providing more buffering for the airflow and effectively reducing the impact force of the airflow on the vane groove 22 and the vane 30. The gas flow direction within the first channel 21 is as follows: Figure 2 The direction indicated by the middle arrow.

[0067] Optionally, combined Figure 5 , Figure 6 and Figure 8-10 As shown, the end face includes a first end face 301 and a second end face 302 at opposite ends of the slide 30 along the axial direction of the cylinder 20; the number of grooves 32 is multiple, including a first groove 321 and a second groove 322, the first groove 321 is disposed on the first end face 301, and the second groove 322 is disposed on the second end face 302; the number of seals 33 is multiple, including a first seal 331 and a second seal 332, the first seal 331 is disposed on the first groove 321, and the second seal 332 is disposed on the second groove 322.

[0068] The compressor 10 typically has two flanges 50, which are mounted opposite each other on both sides of the cylinder 20 along the axial direction. A first end face 301 and a second end face 302 are located at opposite ends of the sliding vane 30 along the axial direction of the cylinder 20. A first groove 321 is provided on the first end face 301 of the sliding vane 30, and a first sealing element 331 is disposed within the first groove 321. Figure 10 and Figure 11 As shown, when airflow enters the second channel 31 of the vane 30, it drives the first seal 331 to float from the first end face 301 of the vane 30 along the axial direction of the cylinder 20 toward a corresponding flange 50, thereby reducing the wear gap between the first end face 301 of the vane 30 and the corresponding flange 50. A second groove 322 is provided on the second end face 302 of the vane 30, and a second seal 332 is disposed within the second groove 322. Driven by airflow, the second seal 332 floats from the second end face 302 of the vane 30 along the axial direction of the cylinder 20 toward another corresponding flange 50, further reducing the wear gap between the second end face 302 of the vane 30 and the corresponding flange 50. When airflow enters the second channel 31 of the vane 30, it simultaneously drives the first seal 331 and the second seal 332 to float toward their respective flanges 50, effectively improving the sealing between the vane 30 and the flange 50, thereby enhancing the working efficiency of the compressor 10.

[0069] Optionally, combined Figure 8-11 As shown, the second channel 31 includes a diversion channel 311, a first pressure channel 312, and a second pressure channel 313. The diversion channel 311 is connected to the sliding vane groove 22 and extends radially along the cylinder 20. One end of the first pressure channel 312 is connected to the diversion channel 311, and the other end of the first pressure channel 312 is connected to the first groove 321. The first pressure channel 312 extends axially toward the first groove 321 along the cylinder 20. One end of the second pressure channel 313 is connected to the diversion channel 311, and the other end of the second pressure channel 313 is connected to the second groove 322. The second pressure channel 313 extends axially toward the second groove 322 along the cylinder 20.

[0070] The gas flow direction in the second channel 31 is as follows: Figure 10 As indicated by the arrow, the flow diversion channel 311 extends radially along the cylinder 20, uniformly guiding the airflow in the vane groove 22 into the vane 30, effectively maintaining stable airflow pressure. The first groove 321 is located on the first end face 301 of the vane 30. The first pressure-applying channel 312 connects the flow diversion channel 311 and the first groove 321, precisely guiding the airflow to the first groove 321, allowing the airflow to directly act on the first seal 331, thereby providing sufficient pressure to the first seal 331 to achieve a floating seal. Similarly, the second groove 322 is located on the second end face 302 of the vane 30. The second pressure-applying channel 313 connects the flow diversion channel 311 and the second groove 322, precisely guiding the airflow to the second groove 322, providing sufficient pressure to the second seal 332 to achieve a floating seal. The flow diversion channel 311 extends radially along the cylinder 20, with the first pressure-applying channel 312 and the second pressure-applying channel 313 located on opposite sides of the flow diversion channel 311. Airflow enters the diversion channel 311 from the sliding vane groove 22, flows through the first pressure-inducing channel 312 and the second pressure-inducing channel 313 respectively, and then flows into the first groove 321 and the second groove 322 respectively. This increases the length and complexity of the airflow path, effectively improving the uniformity and stability of the airflow, while reducing the impact force of the airflow. This airflow path can more stably maintain the floating state of the first seal 331 and the second seal 332, avoiding instability of the first seal 331 and the second seal 332 due to airflow pressure fluctuations. This enhances the sealing effect between the sliding vane 30 and the flange 50, effectively improving the sealing performance of the working chamber 23.

[0071] Optionally, combined Figure 8 As shown, there are multiple first pressure channels 312, and the multiple first pressure channels 312 are evenly distributed along the radial direction of the cylinder 20.

[0072] Multiple first pressure channels 312 work together to improve the driving effect on the first seal 331, avoiding floating failure caused by blockage of a single first pressure channel 312, and enabling the first seal 331 to float continuously and stably. The first groove 321 is located on the first end face 301 of the slide plate 30 and extends radially along the cylinder 20. Multiple first pressure channels 312 are evenly distributed radially along the cylinder 20, allowing airflow to be more evenly introduced to multiple positions in the first groove 321. This improves the force balance of the first seal 331 and prevents the first seal 331 from tilting and floating.

[0073] Optionally, combined Figure 8 As shown, there are multiple second pressure channels 313, which are evenly distributed along the radial direction of the cylinder 20.

[0074] Multiple second pressure channels 313 work together to improve the driving effect on the second seal 332, avoiding floating failure caused by blockage of a single second pressure channel 313, and enabling the second seal 332 to float continuously and stably. The second groove 322 is located on the second end face 302 of the slide plate 30 and extends radially along the cylinder 20. Multiple second pressure channels 313 are evenly distributed radially along the cylinder 20, allowing airflow to be more evenly guided to multiple positions in the second groove 322. This improves the force balance of the second seal 332 and prevents the second seal 332 from tilting and floating.

[0075] Optionally, combined Figure 8-10 As shown, multiple first pressure channels 312 and multiple second pressure channels 313 are symmetrically arranged relative to the diversion channel 311.

[0076] This ensures that the airflow entering the diversion channel 311 is evenly distributed to each of the first pressure-receiving channels 312 and the second pressure-receiving channels 313, thereby achieving uniform driving of the first seal 331 and the second seal 332. This effectively avoids uneven force on the first seal 331 and the second seal 332 due to uneven airflow distribution, and enables the first seal 331 and the second seal 332 to float symmetrically along the axial direction of the cylinder 20, preventing a decrease in sealing performance due to wear on the two end faces of the slide plate 30 along the axial direction of the cylinder 20.

[0077] Optionally, combined Figure 7 and Figure 12 As shown, the slider 30 also includes a slider body 35, which is connected to the slider tail 34. The two sides of the slider body 35 are symmetrically provided with mounting grooves 351, and self-suspending blocks 352 are installed in the two mounting grooves 351 respectively. The two side walls of the slider groove 22 are respectively provided with suspending force surfaces 229 corresponding to the two self-suspending blocks 352. Each self-suspending block 352 and the corresponding suspending force surface have repulsive magnetism.

[0078] During the reciprocating motion of the slide vane 30, the two end faces of the slide vane 30 are subjected to forces of different magnitudes from the two high- and low-pressure chambers, the exhaust chamber and the intake chamber, in the working chamber 23. The resultant force is denoted as F0. The self-suspending blocks 352 on both sides of the slide vane body 35 generate opposite magnetic repulsion with the suspending force surface. During the movement of the slide vane 30, the two sides are subjected to equal and opposite magnetic forces Fc, and Fc > F0. This ensures that the tangential resultant force of the cylinder 20 on the slide vane 30 during its movement is balanced, preventing the slide vane 30 from tilting and colliding and rubbing against the two side walls of the sliding groove. This reduces power consumption and noise.

[0079] Optionally, the gas pressure of the external gas source can be adjusted.

[0080] An external gas source continuously introduces airflow into the slide groove 22. When the slide 30 extends toward the working chamber 23, it pushes the slide 30 to fit tightly against the outer wall surface 41 of the roller 40. When the slide 30 retracts toward the second end 222 of the slide groove, the airflow from the external gas source not only pushes the slide 30 to fit tightly against the outer wall surface 41 of the roller 40, but also buffers the retraction movement of the slide 30, reducing the collision friction between the slide 30 and the slide groove 22.

[0081] In actual operation, different working conditions place different requirements on the contact pressure between the vane 30 and the roller 40, and the sealing force of the seal 33. By adjusting the gas pressure of the external gas source, the airflow pressure acting on the vane 30 and the seal 33 can be precisely controlled. For example, during high-load operation or when the vane 30 moves towards the working chamber 23, appropriately increasing the gas pressure allows the vane 30 to fit more tightly against the roller 40, while simultaneously enhancing the sealing effect of the seal 33 on the flange 50 end face, ensuring the sealing performance of the working chamber 23 and meeting the high-efficiency compression requirements of the compressor 10. When the vane 30 moves towards the working chamber 23, the airflow pressure of the external gas source is greater than the force exerted on the vane 30 by the working chamber 23. The force exerted on the vane 30 by the working chamber 23 includes the refrigerant gas pressure of the working chamber 23 and the force exerted by the roller 40. This allows the airflow to effectively propel the vane 30 towards the working chamber 23. During low load, startup, or when the vane 30 moves toward the second end 222 of the vane groove, the gas pressure can be appropriately reduced to prevent excessive wear of the vane 30 and seal 33 due to excessive pressure, thus extending their service life. By adjusting the gas pressure in real time, the compressor 10 can maintain good operating conditions under different operating conditions.

[0082] Optionally, the gas from the external gas source can be the same refrigerant gas as that inside the working chamber 23.

[0083] The external gas source uses the same refrigerant gas as the working chamber 23. This avoids pressure fluctuations caused by mixing different gases when the external gas source flows into the working chamber, making the compressor's operation more stable. At the same time, this also maintains the stability of the gas composition within the working chamber, preventing refrigerant composition imbalances caused by the mixing of external gases, thus maintaining stable operation of the refrigeration cycle and consistent cooling performance.

[0084] Optionally, combined Figure 2-3 As shown, the pump body assembly 101 for the compressor 10 also includes a roller 40, which is disposed in the working chamber 23. The sliding vane 30 abuts against the outer wall surface 41 of the roller 40, so that the working chamber 23 is divided into an intake chamber and an exhaust chamber. The gas pressure of the external gas source is dynamically adjusted according to the gas pressure changes of the intake chamber and exhaust chamber in different working stages of the compressor 10, and the gas pressure of the external gas source is greater than the gas pressure difference between the exhaust chamber and the intake chamber in the corresponding working stage.

[0085] The compressor 10 operates in two phases: intake and compression / discharge. By dynamically adjusting the gas pressure of the external gas source according to the pressure changes in the intake and discharge chambers of the compressor 10 during different operating phases, the movement of the vane 30 is matched with the movement cycle of the roller 40. This allows the compressor 10 to operate efficiently in each phase of intake, compression, and discharge, improving the overall operating efficiency and performance of the compressor 10.

[0086] The gas pressure of the external gas source is greater than the pressure difference between the exhaust chamber and the intake chamber in the corresponding working stage. This allows the airflow to have enough power to enter the slide groove 22 through the first channel 21 and push the slide 30 toward the working chamber 23. This maintains the tight fit between the slide 30 and the roller 40 so that the working chamber 23 is properly separated. At the same time, it provides enough pressure for the floating of the seal 33 so that the seal 33 can fit tightly against the flange 50.

[0087] Optionally, the cylinder 20 is also provided with an air storage groove, which is connected to the second end 222 of the slide groove, so that when the slide 30 moves toward the second end 222 of the slide groove, part of the airflow in the slide groove 22 can flow into the air storage groove.

[0088] The air storage groove, as an extension of the sliding vane groove 22, provides a buffer and storage space for the airflow within the sliding vane groove 22. When the sliding vane 30 moves toward the second end 222 of the sliding vane groove, the airflow at the second end 222 of the sliding vane groove can gradually flow into the air storage groove through the connecting channel. In this way, the air pressure in the sliding vane groove 22 can be adjusted according to the air pressure of the external gas source. The sliding vane groove 22 is connected to the external gas source, and there is always airflow in the sliding vane groove 22. This airflow can buffer the sliding vane 30 and also push the sliding vane 30 to fit against the outer wall surface 41 of the roller 40. In addition, some of the airflow in the sliding vane groove 22 can flow into the sliding vane groove 22, thereby reducing the air pressure in the sliding vane groove 22, so that the sliding vane 30 can smoothly retract and move into the sliding vane groove 22.

[0089] Optionally, combined Figure 1 As shown, flange 50 is provided with a third channel 51. One end of the third channel 51 is the inlet of an external gas source, and the other end of the third channel 51 is connected to the first channel 21.

[0090] A third channel 51 is provided on flange 50, connecting the external gas source and the first channel 21, allowing the airflow to be stably and continuously delivered from the external gas source to the sliding vane groove 22, providing a reliable power source for the sliding vane 30 and the seal 33. Placing the external gas source inlet on flange 50 facilitates connection to an external gas supply system and simplifies the flow path layout. Compared to directly introducing gas through openings at other locations in cylinder 20, providing the third channel 51 on flange 50 improves the structural strength of cylinder 20 and facilitates sealing at the connection between flange 50 and cylinder 20, thus improving the overall sealing performance of the flow path system.

[0091] Optionally, combined Figure 1 and Figure 2 As shown, the third channel 51 includes a radial channel 511 and a second axial channel 512. One end of the radial channel 511 is an external gas source inlet, which is located on the side wall of the flange 50, and the radial channel 511 extends radially along the flange 50. The second axial channel 512 extends axially along the flange 50. One end of the second axial channel 512 is connected to the radial channel 511, and the other end of the second axial channel 512 is connected to the first axial channel 211.

[0092] Flange 50 is located on the axial end of cylinder 20, and the radial direction of flange 50 is consistent with the radial direction of cylinder 20. An external gas source inlet is located on the side wall of flange 50, making full use of the side wall space to allow airflow to enter the interior of flange 50 radially. This reduces the impact on the structural strength of flange 50. After entering through the inlet on the side wall of flange 50, the airflow first flows radially within radial channel 511, then changes direction to flow axially within second axial channel 512. By switching the airflow direction, the airflow undergoes a change of direction within flange 50, thereby reducing the impact force of the airflow within flange 50. In the case where the first channel 21 includes a first axial channel 211 and a tangential channel 212, the first axial channel 211 is connected to the second axial channel 512. The extension direction of the second axial channel 512 matches that of the first axial channel 211, allowing airflow to smoothly flow from the third channel 51 into the first channel 21. This reduces energy loss during the transition of airflow between flange 50 and cylinder 20, and improves airflow delivery efficiency.

[0093] Optionally, combined Figure 2-4 As shown, the entrance to the first channel 21 is located on the axial end face of the cylinder 20.

[0094] Flange 50 is located on the axial end face 24 of the cylinder, and the inlet of the first channel 21 is opened on the axial end face 24 of the cylinder, which allows the first channel 21 to be more directly connected to the third channel 51 of flange 50. This optimizes the airflow path and improves the smoothness of airflow delivery.

[0095] Optionally, combined Figure 3 As shown, the axial end face 24 of the cylinder is provided with a first sealing groove 241. The first sealing groove 241 is arranged around the entrance of the first channel 21. A first sealing ring 25 is provided in the first sealing groove 241 to seal the connection between the third channel 51 and the first channel 21.

[0096] The first sealing groove 241 is disposed around the inlet of the first channel 21, and the first sealing ring 25 is installed inside the first sealing groove 241. This effectively forms a seal around the connection between the third channel 51 and the first channel 21, preventing gas from leaking outwards from the connection. This improves the sealing of the gas flow path within the pump body assembly 101, thereby increasing the airflow transmission efficiency. When the first channel 21 includes a first axial channel 211, the first sealing groove 241 is disposed around the inlet of the first axial channel 211.

[0097] Optionally, the axial end face of the flange 50 is provided with a second sealing groove, which is arranged around the outlet of the third channel 51. A second sealing ring is provided in the second sealing groove to seal the connection between the third channel 51 and the first channel 21.

[0098] The second sealing groove is disposed around the outlet of the third channel 51, and the second sealing ring is installed in the second sealing groove, which can effectively form a seal around the connection between the third channel 51 and the first channel 21, preventing gas from escaping from the connection between the third channel 51 and the first channel 21. This improves the sealing of the gas flow path within the pump body assembly 101, thereby improving the airflow transmission efficiency. When the third channel 51 includes a second axial channel 512, the second sealing groove is disposed around the outlet of the second axial channel 512.

[0099] Optionally, combined Figure 3 and Figure 4 As shown, the slider 30 includes a slider tail 34 facing the second end 222 of the slider groove, and an elastic member 61 is provided between the slider tail 34 and the second end 222 of the slider groove.

[0100] An elastic element 61 is provided between the tail end 34 of the slide plate and the second end 222 of the slide plate groove. The expansion and contraction of the elastic element 61 can buffer the movement of the slide plate 30 and provide thrust, maintaining a tight fit between the slide plate 30 and the roller 40, thereby improving the sealing performance of the working cavity 23. The elastic force of the elastic element 61 complements the airflow force of the external gas source, jointly driving the movement of the slide plate 30. The airflow from the external gas source can help compensate for insufficient force of the elastic element 61, which could lead to sealing failure. At the same time, when the airflow pressure is insufficient, the elastic force of the elastic element 61 can also help the slide plate 30 maintain a good fit with the roller 40, preventing sealing failure.

[0101] Furthermore, the elastic element 61 reduces the impact and vibration of the slider 30 during movement, making the movement of the slider 30 smoother, reducing wear between the slider 30 and the slider groove 22, thereby extending the service life of the slider 30. The gas pressure of the external gas source is adjustable, and the gas pressure of the airflow can be adjusted according to the elastic force of the elastic element 61 and the compression state of the working chamber 23, so that the slider 30 moves smoothly and fits tightly with the roller 40. The sealing force of the slider 30 against the roller 40 is the resultant force of the airflow pressure of the external gas source and the elastic force of the elastic element 61. The sliding of the slider 30 is achieved by one or both of the elastic force of the elastic element 61 and the airflow pressure of the external gas source. The gas pressure of the external gas source is greater than the total force of the working chamber 23 on the slider. The total force of the working chamber 23 on the slider includes the refrigerant pressure in the working chamber 23 and the force of the roller 40, so that even if the elastic element 61 fails, the airflow can still drive the slider 30 to move normally. The rear groove wall 223 of the slide groove 22 is located at the second end 222 of the slide groove, and the elastic element 61 is disposed between the tail of the slide 34 and the rear groove wall 223 of the slide groove 22. In this way, the elastic force of the elastic element 61 can directly act on the tail of the slide 34 along the radial direction of the cylinder 20.

[0102] Optionally, combined Figure 5 As shown, when the slider 30 moves from the slider groove 22 toward the working cavity 23 to its maximum displacement, the elastic element 61 is in a free state.

[0103] During the operation of the compressor 10, when the roller 40 is in its maximum motion trajectory, the vane 30 moves from the vane groove 22 toward the working chamber 23 to its maximum displacement. At this time, combined with Figure 5 As shown, the elastic element 61 is in a free state, neither stretched nor compressed, and is at its natural length, thus not generating additional elastic force on the slide 30. This avoids the elastic element 61 forming resistance as the slide 30 moves towards the working chamber 23, and also allows the slide 30 to maintain appropriate contact pressure with the outer wall surface 41 of the roller 40, achieving good sealing between the intake and exhaust chambers and reducing wear between the slide 30 and the roller 40. When the movement position of the slide 30 is less than the maximum displacement, combined with... Figure 6 As shown, the elastic element 61 is compressed, generating a reaction force on the sliding vane 30, forming an elastic support. This elastic support allows the sliding vane 30 and the roller 40 to maintain a tight fit, thereby maintaining the sealing effect of the working chamber 23 during the operation of the compressor 10.

[0104] Optionally, the elastic element 61 is provided with a through hole, and the diameter of the through hole is greater than or equal to the inner diameter of the inlet of the second channel 31.

[0105] When the elastic element 61 is located at the tail of the slide plate 34, the through hole is correspondingly set to the inlet of the second channel 31, so that the airflow in the slide plate groove 22 can smoothly enter the inlet of the second channel 31 through the through hole, and prevent the elastic element 61 from obstructing the airflow into the second channel 31.

[0106] Optionally, combined Figure 4-6 and Figure 16 As shown, there are multiple elastic elements 61, which are arranged circumferentially along the end face of the slider tail 34.

[0107] By providing multiple elastic elements 61 between the tail 34 of the slide plate and the second end 222 of the slide plate groove, the expansion and contraction of the elastic elements 61 provide driving force for the slide plate 30, forming a multi-point elastic support for the slide plate 30, thereby improving the motion stability of the slide plate 30. The multiple elastic elements 61 are arranged circumferentially along the end face of the tail 34 of the slide plate, ensuring that the slide plate 30 receives balanced elastic support in all directions. This effectively avoids the slide plate 30 from tilting due to single-point elastic support, thus improving the uniformity of force distribution during the movement of the slide plate 30. This allows the slide plate 30 to maintain a more stable and tight fit with the outer wall surface 41 of the roller 40 of the compressor 10, thereby maintaining good sealing between the intake and exhaust chambers. Furthermore, the multiple elastic elements 61 enhance overall stability, as they can share the force, reducing the risk of decreased motion stability due to malfunctions or lifespan issues of a single elastic element 61.

[0108] Optionally, combined Figure 16 As shown, multiple elastic elements 61 are evenly distributed circumferentially along the end face of the tail of the slide plate 34.

[0109] This ensures that the elastic force on the slide 30 is uniform and consistent at all circumferential positions, effectively preventing the slide 30 from tilting within the slide groove 22 and ensuring good contact between the slide 30 and the outer wall surface 41 of the roller 40. Simultaneously, this also avoids fatigue damage to the slide 30 and elastic element 61 caused by uneven force distribution, extending the service life of the components.

[0110] Optionally, a plurality of elastic elements 61 are arranged symmetrically along the circumferential direction of the end face of the slide tail 34.

[0111] When the slider 30 is subjected to an external force, the reaction force generated by the elastic element 61 is symmetrically distributed circumferentially on the end face of the slider tail 34. This symmetrical force distribution helps the slider 30 maintain stability during movement, preventing the slider 30 from tilting due to excessive elastic force on one side and insufficient elastic force on the other, thus maintaining good contact between the slider 30 and the outer wall surface 41 of the roller 40. In addition, this can also reduce vibration and noise caused by asymmetrical force when the slider 30 slides.

[0112] Optionally, the elastic element 61 is a spring.

[0113] The spring provides stable elastic force and maintains its performance during long-term compression and tension cycles. It also absorbs impacts and vibrations during the movement of the slider 30, thereby improving the movement stability and service life of the slider 30. It can be understood that the elastic element 61 can also be an elastic structure such as elastic rubber or an elastic metal sheet. Elastic rubber has good elasticity and shock absorption properties. Elastic metal sheets have high elastic modulus and strength, and can withstand large loads. The hollow portion of the spring is equivalent to the through hole of the elastic element 61.

[0114] Optionally, the number of elastic elements 61 is greater than or equal to 3.

[0115] This avoids the problem of uneven force distribution caused by the abnormality or failure of a single elastic element 61, and improves the stability of the elastic support. It can be understood that the number of elastic elements 61 can be 3, 4, 5, 6, 7, 8, 9, or 10.

[0116] Optionally, combined Figure 5 , Figure 6 and Figure 16 As shown, the pump body assembly 101 for the compressor 10 also includes a guide plate 62, which is disposed between the elastic member 61 and the tail of the vane 34, and the first end of the elastic member 61 is connected to the guide plate 62.

[0117] During the reciprocating motion of the slider 30, the guide plate 62 can transmit the elastic force of multiple elastic elements 61 to the slider 30 more evenly and accurately, making the elastic force on the slider 30 more uniform and stable, thereby effectively enhancing the stability of the slider 30's motion.

[0118] Optionally, the circumferential direction of the guide plate 62 is consistent with the circumferential direction of the end face of the slider tail 34.

[0119] The guide plate 62 shares the same central axis as the slider 30, and the circumferential direction of the guide plate 62 is consistent with the circumferential direction of the end face of the slider tail 34. Multiple elastic elements 61 are arranged circumferentially along the end face of the slider tail 34, that is, multiple elastic elements 61 are arranged circumferentially along the guide plate 62. This allows the guide plate 62 to uniformly and stably receive and transmit the force of the multiple elastic elements 61, and effectively transmit it to the slider tail 34, so that the slider 30 can obtain uniform and stable elastic support during movement. It can be understood that elastic elements 61 can also be provided in the middle of the guide plate 62.

[0120] Optionally, combined Figure 12 , Figure 16 and Figure 17As shown, the guide plate 62 is provided with a connecting part 621, and the slider tail 34 is provided with a connecting mating part 341. The connecting part 621 and the connecting mating part 341 cooperate to connect the guide plate 62 and the slider tail 34.

[0121] The guide plate 62 engages with the connecting part 341 of the slider tail 34 via the connecting part 621, achieving a stable and reliable connection between the two. This prevents the guide plate 62 from separating or loosening from the slider tail 34 during the reciprocating motion of the slider 30, ensuring that the guide plate 62 maintains a constant direction of motion. The connection between the guide plate 62 and the slider tail 34 also allows the elastic support force of the elastic element 61 to be transmitted more directly and efficiently to the slider 30, thereby improving the stability of the slider 30's movement.

[0122] Optionally, combined Figure 12 , Figure 16 and Figure 17 As shown, one of the connecting part 621 and the connecting mating part 341 is a limiting post 622 and the other is a limiting hole 342. The limiting post 622 is inserted into the limiting hole 342 to fix the guide plate 62 and the tail of the slide plate 34.

[0123] The guide plate 62 and the slider tail 34 are fixedly connected by the limiting post 622 engaging with the limiting hole 342. This connection structure has high connection strength and can effectively prevent relative displacement, loosening, or separation between the guide plate 62 and the slider tail 34. Simultaneously, after the limiting post 622 engages with the limiting hole 342, the degrees of freedom of the guide plate 62 in all directions are restricted, making the guide plate 62 and the slider 30 form a whole, enhancing the rigidity of the overall structure, and thus improving the motion stability of the slider 30. There can be one or more limiting posts 622, and correspondingly, there can also be one or more limiting holes 342. This application uses the connecting part 621 as the limiting post 622 and the connecting mating part 341 as the limiting hole 342 as an example.

[0124] Optionally, combined Figure 12 , Figure 16 and Figure 17 As shown, there are multiple limiting posts 622, which are evenly distributed on the guide plate 62; there are multiple limiting holes 342, which are evenly distributed on the tail of the slider 34, and each limiting hole 342 corresponds to a limiting post 622.

[0125] Multiple limiting posts 622 and multiple limiting holes 342 are arranged in a one-to-one correspondence and engage with each other, so that the guide plate 62 and the slider tail 34 are fixedly connected through multiple connection points, which can improve the connection stability between the guide plate 62 and the slider tail 34. At the same time, this allows the stress to be evenly distributed between the guide plate 62 and the slider tail 34, effectively avoiding stress concentration.

[0126] Optionally, combined Figure 2 , Figure 11 and Figure 17 As shown, the guide plate 62 is provided with a flow hole 623, which corresponds to the inlet of the second channel 31 of the slide tail 34, so that the airflow can enter the second channel 31 through the flow hole 623 after passing through the guide plate 62.

[0127] When the guide plate 62 is located at the tail of the slide plate 34, the flow hole 623 is correspondingly set with the inlet of the second channel 31, so that the airflow in the slide plate groove 22 can smoothly enter the inlet of the second channel 31 through the flow hole 623, and prevent the guide plate 62 from obstructing the airflow into the second channel 31.

[0128] Optionally, the area of ​​the guide plate 62 is greater than or equal to the area of ​​the end face of the slider tail 34.

[0129] This allows the guide plate 62 to fully cover the end face of the slider tail 34, thereby more effectively transmitting force and providing stable support. Simultaneously, this effectively prevents localized stress concentration on the end face of the slider tail 34 during movement, thus improving the motion stability of the slider 30. Furthermore, the larger area of ​​the guide plate 62 can accommodate multiple...

[0130] The elastic element 61 provides a larger range of action, enabling a more uniform distribution of elastic force.

[0131] Optionally, combined Figure 5 , Figure 6 , Figure 16 and Figure 18 As shown, the pump body assembly 101 for the compressor 10 also includes a thrust plate 63, which is disposed between the elastic member 61 and the rear groove wall 223 of the vane groove 22, and the second end of the elastic member 61 is connected to the thrust plate 63.

[0132] The thrust plate 63 is located between the elastic element 61 and the rear groove wall 223 of the vane groove 22 and is connected to the second end of the elastic element 61. It effectively and evenly transmits the force on the elastic element 61 to the rear groove wall 223 of the vane groove 22, allowing multiple elastic elements 61 to undergo coordinated elastic deformation and generate stable elastic force. This also prevents damage to the rear groove wall 223 caused by localized stress concentration in the elastic element 61, thereby extending the service life of the cylinder 20. Simultaneously, the thrust plate 63 provides a stable support platform for the elastic element 61, enabling it to stably exert its elastic effect during operation and preventing performance degradation due to positional misalignment or uneven force. This provides more stable elastic support for the vane 30 during movement, allowing it to more smoothly engage with the roller 40, reducing impact and wear between the vane 30 and the roller 40, and improving the overall operational stability of the compressor 10. Multiple elastic elements 61 are arranged circumferentially along the end face of the slide tail 34 between the guide plate 62 and the thrust plate 63, which enables the multiple elastic elements 61 to smoothly transmit the force.

[0133] Optionally, the circumferential direction of the thrust plate 63 is consistent with the circumferential direction of the end face of the slide tail 34.

[0134] The thrust plate 63 shares the same central axis as the slide 30, and the circumferential direction of the thrust plate 63 is consistent with the circumferential direction of the end face of the slide tail 34. Multiple elastic elements 61 are arranged circumferentially along the end face of the slide tail 34, that is, multiple elastic elements 61 are arranged circumferentially along the thrust plate 63. This allows the thrust plate 63 to uniformly and stably receive and transmit the force of the multiple elastic elements 61, and effectively transmit it to the rear groove wall 223 of the slide groove 22. It can be understood that elastic elements 61 can also be provided in the middle of the thrust plate 63.

[0135] Optionally, the area of ​​the thrust plate 63 is the same as the area of ​​the guide plate 62.

[0136] This ensures that the thrust plate 63 and the guide plate 62 are sized to better transmit the force of the multiple elastic elements 61 and provide stable support for the multiple elastic elements 61.

[0137] For example, both the guide plate 62 and the thrust plate 63 are circular, and multiple springs are evenly distributed and symmetrically arranged between the guide plate 62 and the thrust plate 63 along the circumference. The two ends of the springs are connected to the guide plate 62 and the thrust plate 63, respectively. The circular structure has good symmetry, which makes the force transmission path of the multiple springs symmetrical and uniform during the reciprocating motion of the slider 30. It can be understood that the guide plate 62 and the thrust plate 63 can also adopt other shapes such as rectangles to adapt to different space constraints of the slider groove 22.

[0138] Optionally, combined Figure 5 , Figure 16 and Figure 18 As shown, the thrust plate 63 is provided with a fixing part 631, and the rear groove wall 223 of the slide groove 22 is provided with a fixing mating part 224. The fixing part 631 and the fixing mating part 224 cooperate to fix the thrust plate 63 to the rear groove wall 223 of the slide groove 22.

[0139] The thrust plate 63 is fixedly connected to the rear groove wall 223 of the vane groove 22 via the fixing part 631 and the fixing fit part 224, providing a stable support foundation for the elastic element 61. This effectively prevents the thrust plate 63 from shifting or loosening under the reaction force of the elastic element 61. The fit between the fixing boss 632 and the fastening hole 225 ensures that the thrust plate 63 fits tightly against the rear groove wall 223 of the vane groove 22, avoiding vibration and noise caused by the loosening of the thrust plate 63 and improving the smoothness of the compressor 10 operation. Through the stable connection between the thrust plate 63 and the vane groove 22, the elastic element 61 can function stably throughout the entire operation, thereby maintaining good contact between the vane 30 and the outer wall surface 41 of the roller 40.

[0140] Optionally, combined Figure 6 , Figure 16 and Figure 18 As shown, one of the fixing part 631 and the fixing mating part 224 is a fixing boss 632 and the other is a fastening hole 225. The fixing boss 632 is inserted into the fastening hole 225 to fix the thrust plate 63 to the rear groove wall 223 of the slide groove 22.

[0141] By engaging the fixing boss 632 with the fastening hole 225, the thrust plate 63 can be fixed to the rear groove wall 223 of the vane groove 22, achieving a stable connection between the thrust plate 63 and the rear groove wall 223 of the vane groove 22. During the operation of the compressor 10,

[0142] The elastic force generated by the elastic element 61 is transmitted to the rear groove wall 223 of the sliding groove 22 through the thrust plate 63. This stable connection method can withstand a large elastic reaction force, preventing the thrust plate 63 from loosening or shifting, and ensuring the stable transmission of the elastic force of the elastic element 61. The number of fixing bosses 632 can be one or more, and correspondingly, the number of fastening holes 225 can also be one or more. This application uses one fixing boss 632 as an example. This application uses the fixing part 631 as the fixing boss 632 and the fixing mating part 224 as the fastening hole 225 as an example.

[0143] Optionally, combined Figure 4 As shown, the slider body 35 is connected to the side of the slider tail 34 facing the working cavity 23, and the cross-sectional area of ​​the slider tail 34 is larger than the cross-sectional area of ​​the slider body 35.

[0144] The cross-sectional area of ​​the slider tail 34 is larger than that of the slider body 35, which improves the structural stability and stress performance of the slider 30. During the reciprocating motion of the slider 30, the larger cross-sectional area of ​​the slider tail 34 can withstand greater elastic force and gas pressure, enabling the elastic element 61 to effectively push the slider 30 towards the working chamber 23. It also better resists the lateral forces experienced by the slider 30 during its movement, preventing the slider 30 from tilting or jamming within the slider groove 22. Furthermore, the larger cross-sectional area of ​​the slider tail 34 increases the contact area between it and the elastic element 61 or the guide plate 62, allowing the elastic force to be distributed more evenly across the slider tail 34, reducing local stress concentration and extending the service life of the slider 30.

[0145] Optionally, combined Figure 4 and Figure 7 As shown, the slider groove 22 includes a connected sliding cavity 226 and a reset cavity 227. The slider body 35 moves in the sliding cavity 226, and the slider tail 34 and the elastic member 61 are disposed in the reset cavity 227. The cross-sectional area of ​​the reset cavity 227 is larger than the cross-sectional area of ​​the sliding cavity 226, and the cross-sectional area of ​​the slider tail 34 is larger than the cross-sectional area of ​​the sliding cavity 226. When the slider tail 34 moves toward the working cavity 23, it can abut against the front cavity wall 228 of the reset cavity 227 for limitation.

[0146] The cross-sectional area of ​​the slider tail 34 is larger than that of the slider body 35, and the cross-sectional area of ​​the reset cavity 227 is larger than that of the sliding cavity 226. This ensures that the cross-sectional area of ​​the reset cavity 227 matches the cross-sectional area of ​​the slider tail 34, and the cross-sectional area of ​​the sliding cavity 226 matches the cross-sectional area of ​​the slider body 35. When the slider 30 moves within the slider groove 22, the slider tail 34 can move smoothly within the reset cavity 227 without being obstructed due to insufficient space. Since the cross-sectional area of ​​the slider tail 34 is larger than that of the sliding cavity 226, when the slider 30 moves from the slider groove 22 towards the working cavity 23 to its maximum displacement, the slider tail 34 moves towards the working cavity 23 to its limit position, where it abuts against the front cavity wall 228 of the reset cavity 227 for limitation. This effectively prevents the vane 30 from extending excessively out of the vane groove 22, thereby avoiding excessive compression or collision between the vane 30 and the roller 40, and preventing damage to the vane 30 and the roller 40. Simultaneously, the larger space of the reset chamber 227 provides sufficient installation and movement space for the elastic element 61, ensuring that the elastic element 61 can properly perform its elastic function, providing stable elastic support for the vane 30, and enabling the vane 30 to maintain good sealing and movement stability during operation, thus improving the compression efficiency and operational stability of the compressor 10. Furthermore, the tail of the vane 34 obstructs airflow, preventing airflow from the second end of the vane groove 22 from flowing into the working chamber 23. When the pump body assembly 101 for the compressor 10 includes a guide plate 62 or a thrust plate 63, the guide plate 62 and the thrust plate 63 are also disposed in the reset chamber 227.

[0147] Optionally, combined Figure 13 As shown, the tail portion 34 of the slider protrudes to both sides of the slider body portion 35 along the width direction of the slider body portion 35.

[0148] The tail portion 34 of the slider protrudes along both sides of the main body 35 in the width direction, forming a T-shaped structure or a similar T-shaped structure, which improves the operational balance of the slider 30. The main body 35 of the slider is located inside the sliding cavity 226. The protrusions on both sides of the tail portion 34 of the slider can abut against and limit the movement of the slider 30 by the front cavity wall 228 of the reset cavity 227 located on both sides of the sliding cavity 226, thereby preventing the slider 30 from deviating and improving the balance and stability of the slider 30's movement.

[0149] Optionally, combined Figure 3 , Figure 14 and Figure 15 As shown, the slider 30 also includes a slider head 36, which is located at one end of the slider body 35 facing the roller 40, and the slider head 36 abuts against the roller 40; wherein, a reinforcing member 37 is provided between the slider head 36 and the slider body 35, the reinforcing member 37 includes a hollow structure 370, and the two ends of the hollow structure 370 abut against the slider head 36 and the slider body 35 respectively.

[0150] The vane 30 for compressor 10 provided in this embodiment has a reinforcing member 37 between the vane head 36 and the vane body 35. The hollow structure 370 of the reinforcing member 37 forms a buffer space, and its two ends abut against the vane head 36 and the vane body 35 respectively, effectively dispersing the pressure on the vane head 36. When the vane head 36 contacts the roller 40 and is subjected to force, the hollow structure 370 can evenly distribute the stress, preventing excessive stress concentration at the contact area between the vane head 36 and the roller 40. This improves the impact resistance of the vane 30 and avoids or reduces problems such as deformation and wear of the vane head 36 caused by excessive local stress.

[0151] Optionally, the hollow structure 370 includes a protrusion 371 that protrudes in an arc shape toward the slider head 36 and abuts against the slider head 36.

[0152] The protrusion 371 of the hollow structure 370 protrudes in an arc shape toward the slider head 36 and abuts against the slider head 36, which can effectively enhance the structural strength of the slider head 36. This can effectively improve the impact resistance of the slider head 36 and maintain the tight fit between the slider 30 and the roller 40.

[0153] Furthermore, during the operation of the compressor 10, radial vibration is generated when the roller 40 drives the vane 30 to move. When the vane head 36 is under force, the arc-shaped protrusion 371 can absorb and decompose the radial vibration. When vibration occurs, the protrusion 371 can produce slight elastic deformation, absorbing vibration energy and reducing the impact of vibration on the vane head 36 and the main body. This can reduce the collision and wear between the vane 30 and the roller 40, and between the vane 30 and the vane groove 22 caused by vibration, improve the smoothness of compressor 10 operation, and reduce noise generation.

[0154] Optionally, combined Figure 15 As shown, the hollow structure 370 also includes a transition portion 372, which is provided on the end side of the protrusion 371 facing the slide body portion 35. The transition portion 372 is connected to the protrusion 371, and the transition portion 372 is inclined and contracted inward along the direction of the slide head 36 toward the slide body portion 35.

[0155] The transition portion 372 is located on the end side of the protrusion 371 facing the slide head 35, that is, the transition portion 372 is located on the end side of the protrusion 371 away from the slide head 36. The transition portion 372 is connected to the protrusion 371, which protrudes in an arc shape towards the slide head 36, and the transition portion 372 slopes inward and contracts in the direction from the slide head 36 towards the slide head 35, so that the hollow structure 370 is formed with a structure that gradually contracts inward at both ends of the arc-shaped protrusion. When the roller 40 applies pressure to the slide head 36, the sloped contraction structure of the transition portion 372 can play a buffering role. When the pressure is transmitted from the slide head 36 through the protrusion 371 to the transition portion 372, it can be gradually dispersed and the impact reduced. This transition design can avoid stress concentration caused by sudden changes in force, alleviate the stress on the slide head 36, improve the stability of the contact between the slide head 36 and the roller 40, and enhance the overall strength of the slide 30 under stress.

[0156] Optionally, combined Figure 15 As shown, the protrusion 371 includes a first end 3711 and a second end 3712 located at both ends of the arc-shaped protrusion. The transition portion 372 includes a first connecting rib 3721 and a second connecting rib 3722. One end of the first connecting rib 3721 is connected to the first end 3711, and the first connecting rib 3721 is inclined toward the second connecting rib 3722. One end of the second connecting rib 3722 is connected to the second end 3712, and the second connecting rib 3722 is inclined toward the first connecting rib 3721.

[0157] The transition portion 372 is connected to the first end 3711 and the second end 3712 of the protrusion 371 via the first connecting rib 3721 and the second connecting rib 3722, respectively, forming a continuous support structure that allows the slider head 36 to better distribute stress when subjected to force. The first connecting rib 3721 and the second connecting rib 3722 are inclined inwards towards each other, causing the first connecting rib 3721 and the second connecting rib 3722 to gradually contract along the direction from the slider head 36 towards the slider body 35, thereby forming a buffer structure. When vibration occurs, the inclined first connecting rib 3721 and the second connecting rib 3722 can effectively absorb and disperse vibration energy, reducing the impact of vibration on the slider head 36 and the body.

[0158] Optionally, combined Figure 15 As shown, the hollow structure 370 also includes a support portion 373, which is connected to the transition portion 372. The support portion 373 extends along the width direction of the slide body portion 35, and a buffer space 374 is formed between the protrusion 371, the transition portion 372 and the support portion 373 of the hollow structure 370.

[0159] Combination Figure 13As shown, the x2 axis indicates the width direction of the slider body, the y2 axis indicates the length direction of the slider body, and the z2 axis indicates the height direction of the slider body.

[0160] The hollow structure 370 has a protrusion 371, a transition portion 372, and a support portion 373 arranged sequentially along the length of the slider body 35. The protrusion 371 protrudes in an arc shape toward the slider head 36. The transition portion 372 is connected to the protrusion 371 and slopes inward toward the slider body 35 along the slider head 36. The support portion 373 is connected to the transition portion 372 and extends along the width of the slider body 35. This makes the hollow structure 370 form an inverted Ω shape or a similar inverted Ω shape, thereby improving the impact resistance of the hollow structure 370 and enhancing the overall structural strength and stability of the slider 30.

[0161] The support portion 373 connects to the transition portion 372 and extends along the width direction of the slide body portion 35. The protrusion 371, transition portion 372, and support portion 373 form a buffer space 374. When subjected to pressure from the roller 40, the buffer space 374 effectively disperses the impact force and absorbs vibration energy. Simultaneously, the connection between the support portion 373 and the transition portion 372, extending along the width direction of the slide body portion 35, enhances the overall rigidity and stability of the hollow structure 370. Under pressure from the roller 40, the support portion 373 provides strong support, enhancing the reinforcement 37's resistance to deformation.

[0162] Optionally, combined Figure 14 As shown, the reinforcing member 37 includes a plurality of hollow structures 370, which are arranged along the width direction of the slide body 35.

[0163] Multiple hollow structures 370 of the reinforcing member 37 are arranged along the width direction of the slide body 35, which can buffer and support different positions of the slide head 36. When the roller 40 applies pressure to the slide head 36, the multiple hollow structures 370 can more comprehensively disperse the stress, making the force on the slide head 36 more balanced and effectively reducing the possibility of local stress concentration. This can enhance the overall structural strength and deformation resistance of the slide head 36, and effectively improve the structural strength of the slide 30.

[0164] Optionally, multiple hollow structures 370 are arranged sequentially along the width direction of the slide body 35.

[0165] When multiple hollow structures 370 are arranged sequentially, they form a continuous support structure, which reinforces the slider head 36 as a whole. This effectively disperses stress and improves the structural strength of the slider 30.

[0166] Optionally, a plurality of hollow structures 370 are arranged at intervals along the width direction of the slide body 35.

[0167] When multiple hollow structures 370 are arranged at intervals, they can form multiple distributed support points at the slider head 36. These support points cooperate with each other to evenly distribute stress.

[0168] Optionally, combined Figure 14 As shown, the support portions 373 of adjacent hollow structures 370 are connected in sequence.

[0169] Multiple hollow structures 370 are arranged along the width direction of the slide body 35, and the support portions 373 of adjacent hollow structures 370 are connected in sequence to form a continuous integral structure. The multiple hollow structures 370 support each other and can collectively withstand the pressure applied by the roller 40. When the slide head 36 is subjected to pressure, the pressure is transmitted and dispersed among the hollow structures 370 through the sequentially connected support portions 373, thereby effectively improving the overall load-bearing capacity of the slide 30 and enhancing its resistance to deformation. The support portion 373 can be a support plate, and the support plates of adjacent hollow structures 370 are connected in sequence to form a complete support panel.

[0170] Optionally, the hollow structure 370 extends along the height direction of the slide body 35.

[0171] The height direction of the slider body 35 is the same as the height direction of the slider head 36. The hollow structure 370 extends along the height direction of the slider body 35, enabling it to provide comprehensive support and reinforcement for the slider head 36 in the height direction of the slider body 35. When the slider head 36 contacts the roller 40 and is subjected to force, the hollow structure 370 can effectively disperse and transmit the force along the entire height direction of the slider body 35, preventing local deformation of the slider head 36 due to excessive force and improving the overall structural strength of the slider 30.

[0172] Optionally, combined Figure 13 As shown, the height of the slider head 36 is the same as the height of the slider body 35 and the height of the hollow structure 370.

[0173] The height of the slider head 36 is consistent with the height of the slider body 35 and the height of the hollow structure 370. This can maintain the structural continuity and integrity of the slider 30 in the height direction, and effectively enhance the stability and deformation resistance of the slider 30.

[0174] Optionally, combined Figure 14As shown, the slider head 36 protrudes in an arc shape in the direction away from the slider body 35; when there are multiple hollow structures 370, the dimensions of the multiple hollow structures 370 in the length direction of the slider body 35 gradually decrease from the middle to both ends in the width direction of the slider body 35.

[0175] During actual operation of the compressor 10, the vane head 36 is in contact with the outer wall surface 41 of the roller 40, and the roller 40 rotates, meaning there is relative movement between the outer wall surface 41 of the roller 40 and the vane head 36, generating friction. The arc-shaped protrusion of the vane head 36 matches the outer arc surface of the roller 40, enabling more uniform force transmission and reducing wear and friction noise when the vane head 36 contacts the roller 40. Furthermore, the arc-shaped structure can undergo a certain degree of elastic deformation under stress, providing cushioning and shock absorption, effectively reducing the impact and vibration experienced by the vane head 36.

[0176] The middle portion of the slider head 36 typically experiences relatively higher stress, while the ends experience relatively lower stress. Multiple hollow structures 370 are designed to match the arcuate extension shape of the slider head 36 along the length of the slider body 35, gradually decreasing in size from the middle to both ends along the width of the slider body 30. This provides stronger support and stress dispersion for the middle portion of the slider head 36. The slider head 36 is designed with a gradually changing fan-shaped arc edge, forming a symmetrical structure that allows it to maintain better balance and stability under stress.

[0177] Combination Figure 1 As shown, this disclosure provides a compressor 10, including a pump body assembly 101 for the compressor 10 as described in any of the above-disclosed embodiments.

[0178] The compressor 10 provided in this embodiment includes the pump body assembly 101 for the compressor 10 as described in any of the above-described embodiments, and therefore has all the beneficial effects of the pump body assembly 101 for the compressor 10 as described in any of the above-described embodiments, which will not be repeated here.

[0179] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A pump body assembly for a compressor, characterized in that, include: The cylinder is provided with a first channel, a vane groove, and a working chamber; A flange is located on the axial end face of the cylinder; A slider is provided in a slider groove, and the slider can reciprocate in a direction toward or away from the working cavity; The sliding vane groove includes a first end and a second end that are radially opposite to each other along the cylinder. The first end of the sliding vane groove is connected to the working chamber. The inlet of the first channel is connected to an external gas source, and the outlet of the first channel is connected to the second end of the sliding vane groove, so that the airflow can push the sliding vane toward the working chamber. The sliding vane is provided with a second channel, which is connected to the first channel through the sliding vane groove. The end face of the sliding vane along the cylinder axis is provided with a groove, and a movable seal is provided in the groove. The second channel is connected to the groove, so that the airflow can drive the seal to float toward the flange along the cylinder axis.

2. The pump body assembly for a compressor according to claim 1, characterized in that, The end face includes the first end face and the second end face at opposite ends of the sliding vane along the cylinder axis; The number of grooves is multiple, including a first groove and a second groove, with the first groove located on the first end face and the second groove located on the second end face; The number of seals is multiple, including a first seal and a second seal. The first seal is disposed in a first groove, and the second seal is disposed in a second groove.

3. The pump body assembly for a compressor according to claim 2, characterized in that, The second channel includes: The flow divider channel is connected to the vane groove and extends radially along the cylinder. The first pressure channel has one end connected to the diversion channel and the other end connected to the first groove, and the first pressure channel extends along the axial direction of the cylinder toward the first groove. The second pressure channel is connected at one end to the diversion channel and at the other end to the second groove, and the second pressure channel extends along the axial direction of the cylinder toward the second groove.

4. The pump body assembly for a compressor according to claim 3, characterized in that, There are multiple first pressure-applying channels, which are evenly distributed radially along the cylinder; and / or, There are multiple second pressure channels, which are evenly distributed along the radial direction of the cylinder.

5. The pump body assembly for a compressor according to claim 1, characterized in that, Also includes: The roller is located in the working chamber, and the sliding vane abuts against the outer wall of the roller to divide the working chamber into an intake chamber and an exhaust chamber. The gas pressure of the external gas source is dynamically adjusted according to the gas pressure changes of the intake and exhaust chambers in different working stages of the compressor, and the gas pressure of the external gas source is greater than the gas pressure difference between the exhaust chamber and the intake chamber in the corresponding working stage.

6. The pump body assembly for a compressor according to any one of claims 1 to 5, characterized in that, The flange is equipped with a third channel, one end of which is the inlet of an external gas source, and the other end of which is connected to the first channel.

7. The pump body assembly for a compressor according to claim 6, characterized in that, The cylinder has a first sealing groove on its axial end face, which surrounds the entrance of the first channel. A first sealing ring is provided within the first sealing groove to seal the connection between the third channel and the first channel; and / or, The flange has a second sealing groove on its axial end face. The second sealing groove is arranged around the outlet of the third channel. A second sealing ring is provided in the second sealing groove to seal the connection between the third channel and the first channel.

8. The pump body assembly for a compressor according to any one of claims 1 to 5, characterized in that, The slider includes a slider tail facing the second end of the slider groove, and an elastic element is provided between the slider tail and the second end of the slider groove.

9. The pump body assembly for a compressor according to claim 8, characterized in that, When the slider moves from the slider groove toward the working cavity to its maximum displacement, the elastic element is in a free state.

10. A compressor, characterized in that, Includes a pump body assembly for a compressor as described in any one of claims 1 to 9.

Images