Compressor and refrigeration equipment

Abstract

The invention relates to the technical field of compressors, in particular to a compressor and refrigeration equipment. The compressor comprises an air cylinder, a cylindrical cylinder cavity is defined in the air cylinder, a sliding way communicated with the cylinder cavity is arranged on the side wall of the air cylinder, and an air inlet channel and an air supplementing channel which are oppositely arranged are further arranged on the side wall of the air cylinder; an opening is formed in the side, facing the air supply channel, of the first side end face of the slideway. The rotating assembly comprises a main shaft and a roller which is driven by the main shaft to do eccentric motion in the cylinder cavity; a built-in channel used for transmitting airflow is formed in the sliding piece, one end of the built-in channel can communicate with the middle section of the cylinder cavity, and the other end of the built-in channel is formed in the side, facing the opening, of the sliding piece and can selectively communicate with the air supplementing channel; the sliding piece is arranged to stretch out or move into the sliding way in the extending direction of the sliding way when the rotating assembly rotates, so that the built-in channel and the air supplementing channel are in periodic butt joint to intermittently form an air supplementing flow path communicating with the cylinder cavity. The compression efficiency of the compressor can be improved.

Description

Technical Field

[0001] This application relates to the field of compressor technology, and more specifically, to a compressor and refrigeration equipment. Background Technology

[0002] Currently, a compressor is a fluid machine that raises low-pressure gas to high-pressure gas. It is the heart of a heat exchange system, periodically drawing in, compressing, and discharging gas during operation. Within a compressor, the cylinder assembly is the core component, directly affecting its heat exchange performance.

[0003] To improve the compression efficiency and heat exchange efficiency of cylinder assemblies during heating in extremely low temperatures and cooling in extremely high temperatures, related technologies incorporate a gas supply channel on the cylinder, within which a valve structure is installed. The valve structure and the gas supply channel are fitted with a clearance fit. When the valve is open, the gas supply channel connects to the cylinder's compression chamber, allowing intermediate-pressure gas to be introduced into the compression chamber to increase the compression volume and thus increase enthalpy. However, the valve structure only closes the middle section of the gas supply channel; leakage exists between the valve structure and the gas supply channel, leading to a decrease in compression efficiency. Summary of the Invention

[0004] In view of this, this application provides a compressor and refrigeration equipment to achieve gas replenishment and ionization of the compressor, thereby improving the compressor's compression efficiency and making the compressor operate stably and efficiently.

[0005] In a first aspect, this application provides a compressor, comprising: a cylinder having a cylindrical cavity defined inside, a slide rail communicating with the cavity on the side wall of the cylinder; an intake passage and a replenishment passage arranged opposite to each other on the side wall of the cylinder, the intake passage being used for intake, one end of the replenishment passage being configured to communicate with an external medium-pressure air source, and the other end of the replenishment passage extending to a first side end of the slide rail and configured to be controllably connected to the slide rail; wherein the first side end of the slide rail has an opening facing the replenishment passage; a rotating assembly including a main shaft and a roller driven by the main shaft to perform eccentric motion within the cylinder cavity, the outer peripheral surface of the roller forming a dynamically sealed working chamber with the inner wall of the cylinder cavity; and a rotating assembly including a main shaft and a roller that performs eccentric motion within the cylinder cavity, the roller forming a dynamically sealed working chamber with the inner wall of the cylinder cavity; and a slide rail. The slide plate has one end connected to the side of the slide rail away from the working chamber by a spring; the other end of the slide plate can slide radially within the slide rail to abut against the outer circumferential surface of the roller, dividing the chamber into an intake chamber and a compression chamber; wherein, the slide plate has an internal channel for transmitting airflow, one end of the internal channel can communicate with the compression chamber, and the other end of the internal channel is opened in the slide plate and can selectively communicate with the air supply channel through the opening; the slide plate is configured to extend or move into the slide rail along the extension direction of the slide rail when the rotating assembly rotates, so that the internal channel and the air supply channel periodically align to intermittently form an air supply path communicating with the cylinder chamber.

[0006] By employing the above technical solution, the enthalpy increase of the cylinder cavity can be achieved through the cooperation of the air replenishment channel provided on the side wall of the cylinder and the sliding vane with a built-in channel in the slide rail. Specifically, after the intake is completed during compressor operation, the air replenishment channel and the built-in channel of the sliding vane can be connected during the rotation of the rotating assembly. When the rotating assembly rotates to block the intake channel, the sliding vane moves out of the slide rail, so that the built-in channel and the air replenishment channel are connected to the middle section of the cylinder cavity. At this time, an external air source can be introduced into the cylinder cavity, thereby achieving directional air replenishment of the compressor, thereby increasing the pressure and gas density in the cylinder cavity and improving the compression efficiency. As the rotating assembly continues to rotate, the sliding vane gradually moves into the slide rail to close the air replenishment channel. The periodic connection between the built-in channel of the sliding vane and the air replenishment channel can flexibly adjust the air replenishment amount according to the actual working conditions, thereby achieving air replenishment and enthalpy increase of the compressor, ensuring that the compressor can maintain a highly efficient and stable operating state under different load conditions. In addition, this solution can also avoid the problem of decreased compression efficiency caused by untimely or excessive air replenishment, optimizing the overall performance of the compressor.

[0007] In an optional embodiment of the compressor described above, the built-in channel includes: an inflow section extending along the direction of the replenishment channel, wherein the inlet of the inflow section is disposed on a first side end wall of the vane facing the replenishment channel; a guide section that bends and communicates with the inflow section and extends along the first direction, wherein the guide section is configured to bend in a direction away from the replenishment channel; and an outflow section that bends and communicates with the guide section, wherein the outlet of the outflow section is formed on the first side end wall.

[0008] In an optional embodiment of the compressor described above, the portion of the first side end wall located between the inlet of the inflow section and the outlet of the outflow section is configured as a sealing portion; the replenishment channel has a connecting port communicating with the built-in channel; the cross-sectional area of ​​the inlet of the inflow section is larger than the cross-sectional area of ​​the connecting port; and when the vane is fully moved into the slide, the sealing portion abuts against the connecting port, and the side of the sealing portion near the inlet of the inflow section is at least flush with the side wall of the connecting port, so that the inlet of the inflow section is misaligned with the connecting port.

[0009] In an optional embodiment of the compressor described above, the cross-sectional area of ​​the inlet of the inflow section is larger than the cross-sectional area of ​​the outlet of the outflow section.

[0010] In an optional embodiment of the compressor described above, the spring is fixedly connected to the slide plate; the spring is configured to be stretched when the slide plate extends along the slide rail and compressed when the slide plate moves in; wherein, during the stroke of the rotating assembly from opening the air intake channel to closing the air intake channel, the roller abuts against the slide plate and compresses the spring; the rotating assembly gradually rotates to avoid the slide plate, and the slide plate extends out of the slide rail under the elastic force of the spring so that the built-in channel gradually connects with the air replenishment channel.

[0011] In an optional embodiment of the compressor described above, a backflow preventer is provided in the gas supply channel. The valve body of the backflow preventer extends obliquely along the airflow direction in the gas supply channel. The backflow preventer is configured to open the gas supply channel when the slide plate extends out of the slide and the pressure in the cylinder cavity is less than the pressure in the gas supply channel, and to close the gas supply channel when the pressure in the cylinder cavity is greater than or equal to the pressure in the gas supply channel.

[0012] In an optional embodiment of the compressor described above, the gas supply channel includes a first channel and a second channel connected in sequence; the first channel is connected to an external gas source, and the diameter of the second channel is smaller than the diameter of the first channel; wherein, the backflow preventer is disposed in the first channel.

[0013] In an optional embodiment of the compressor described above, the fixed end of the valve plate body is fixedly connected to the side wall of the first channel; the free end of the valve plate body can abut against the side wall of the first channel; wherein, a portion of the side wall of the first channel is recessed inward to abut against the free end of the valve plate body.

[0014] In an alternative embodiment of the compressor described above, the first channel is configured such that its diameter gradually decreases along the direction toward the second channel.

[0015] In an optional embodiment of the compressor described above, it further includes: an upper flange and a lower flange, which are respectively covered on the upper end face and the lower end face of the cylinder, and both the upper flange and the lower flange are rotatably engaged with the main shaft; wherein, the upper flange and the upper end face of the cylinder and the lower flange and the lower end face of the cylinder are in contact and sealed; or, a sealing gasket is provided between the upper flange and the upper end face of the cylinder and between the lower flange and the lower end face of the cylinder.

[0016] In the optional embodiment of the compressor described above, the eccentricity of the main shaft is e, and the eccentric diameter is D1; ​​the outer diameter of the roller is D2; the diameter of the cylinder mounting surface is D3; the distance from the inlet end of the air supply channel 210 to the center of the cylinder is L1; the inlet of the built-in channel 321 on the first side end wall 322 of the slide vane 320 includes a first side and a second side opposite to each other, the first side being close to the spring 400; the distance between the first side and the end of the slide vane close to the spring 400 is L2, and the distance between the second side and the end of the slide vane close to the spring 400 is L3; when the roller completely blocks the air supply channel, the following requirements must be met: L1-e-D2 / 2-L2≥0, to prevent the air supply channel from opening too early; and D3-e-D2 / 2-L3≥1, to prevent air leakage during the air supply process.

[0017] Secondly, this application provides a refrigeration device, including a compressor as described above. Attached Figure Description

[0018] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this application, illustrate exemplary embodiments of the invention and, together with their description, serve to explain the invention and do not constitute an undue limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the structure of a compressor provided in this application; Figure 2 yes Figure 1 A magnified view of a portion of the image; Figure 3 This is a cross-sectional schematic diagram of a compressor provided in this application; Figure 4This is a schematic diagram of a slide plate being fully inserted into the slide rail, as provided in this application. Figure 5 yes Figure 4 A magnified view of a portion of the image; Figure 6 This is a schematic diagram of a slider moving out of the slide provided in this application; Figure 7 yes Figure 6 A magnified view of a portion of the image; Figure 8 This is a schematic diagram of the structure of an air replenishment channel and a built-in channel provided in this application; Figure 9 This is a schematic diagram of the structure of a slider provided in this application; Figure 10 This is a schematic diagram of another compressor provided in this application; Figure 11 yes Figure 10 BB cross-sectional diagram; Figure 12 This application provides a schematic diagram of the compressor rotation angle and pressure change; Figure 13 This is a schematic diagram showing the relationship between the rotation angle of a rotating component and the connection between the air supply channel and the built-in channel provided in this application; Figure 14 yes Figure 13 A magnified view of a portion of the image; Figure 15 yes Figure 13 A magnified view of a portion of the image; Figure 16 This is a structural schematic diagram of another compressor provided in this application.

[0019] Figure label: 100. Rotating assembly; 110. Main shaft; 120. Roller; 200. Cylinder; 210. Air supply channel; 2101. Connecting interface; 211. First channel section; 212. Second channel section; 310. Slide rail; 320. Sliding plate; 3201. Inlet; 3202. Outlet; 321. Internal channel; 3211. Inflow section; 3212. Guide section; 3213. Outflow section; 322. First side end wall; 3220. Sealing part; 400. Spring; 500. Anti-backflow valve plate; 510. Valve plate body; 610. Upper flange; 620. Lower flange. Detailed Implementation

[0020] The following specific embodiments illustrate the implementation of this application. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0021] The terminology used in the embodiments of this application is for the purpose of describing particular embodiments only and is not intended to limit the application. The singular forms “a,” “said,” and “the” used in the embodiments of this application and the appended claims are also intended to include the plural forms, unless the context clearly indicates otherwise. “Multiple” generally includes at least two, but does not exclude the inclusion of at least one.

[0022] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0023] It should also be noted that the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a product or system comprising a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a product or system. Without further limitation, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the product or system that includes said element.

[0024] The embodiments of this application are described in detail below. Examples of the embodiments are shown in the accompanying drawings. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application.

[0025] As mentioned in the background, a compressor is a fluid machine that raises low-pressure gas to high-pressure gas. It is the heart of a heat exchange system, periodically drawing in, compressing, and discharging gas during operation. Within a compressor, the cylinder assembly is the core component, directly affecting its heat exchange performance.

[0026] To improve the compression efficiency and heat exchange efficiency of cylinder assemblies during heating in extremely low temperatures and cooling in extremely high temperatures, related technologies incorporate a gas supply channel on the cylinder, within which a valve structure is installed. The valve structure and the gas supply channel are fitted with a clearance fit. When the valve is open, the gas supply channel connects to the cylinder cavity, allowing intermediate-pressure gas to be introduced into the compression chamber to increase the compression volume and thus increase enthalpy. However, the valve structure only closes the middle section of the gas supply channel, and leakage exists between the valve structure and the gas supply channel, leading to a decrease in compression efficiency.

[0027] To address the problem of reduced compression efficiency, this disclosure provides a compressor and a refrigeration device that can improve the compressor's compression efficiency, making the compressor operate stably and efficiently.

[0028] Firstly, combining Figures 1 to 15 As shown, this application provides a compressor, including a rotating assembly 100, a cylinder 200, a slide rail 310, and a vane 320.

[0029] The cylinder 200 has a cylindrical cavity inside, and a slide 310 communicating with the cavity is provided on the side wall of the cylinder 200. The side wall of the cylinder 200 is also provided with an intake channel and a supplementary air channel 210 arranged opposite to each other. The intake channel is used for intake, and one end of the supplementary air channel 210 is configured to communicate with an external medium-pressure air source. The other end of the supplementary air channel 210 extends to the first side end of the slide 310 and is configured to be controllably connected to the slide 310. The first side end of the slide 310 has an opening on the side facing the supplementary air channel 210.

[0030] The rotating assembly 100 includes a main shaft 110 and a roller 120 driven by the main shaft 110 to make eccentric movements in the cylinder cavity. The outer peripheral surface of the roller 120 forms a dynamically sealed working cavity with the inner wall of the cylinder cavity of the cylinder 200.

[0031] One end of the slide plate 320 is connected to the side of the slide rail 310 away from the working chamber by a spring 400; the other end of the slide plate 320 can slide radially along the cylinder 200 within the slide rail 310 to abut against the outer circumferential surface of the roller 120, thus dividing the chamber into an intake chamber and a compression chamber. The slide plate 320 has an internal channel 321 for transmitting airflow. One end of the internal channel 321 connects to the middle section of the compression chamber, and the other end of the internal channel 321 is located within the slide plate 320 and can selectively connect to the air supply channel 210 through an opening.

[0032] The slide 320 is configured to extend or move into the slide 310 along the extension direction of the slide 310 when the rotating assembly 100 rotates, so that the built-in channel 321 periodically aligns with the air supply channel 210 to intermittently form an air supply path that connects to the compression chamber.

[0033] Optionally, the rotating assembly 100 is the core component of the compressor, and the cooperative design of its main shaft 110 and rollers 120 can effectively improve the overall operating efficiency of the compressor. Specifically, the main shaft 110 can rotate around its own axis under the drive of the driving component, thereby driving the rotation of the rollers 120. The rollers 120 rotate within the cylinder cavity of the cylinder 200. During rotation, the space between the rollers 120 and the inner wall of the cylinder 200 changes periodically, thereby realizing the intake, compression, and discharge of gas. Specifically, the main shaft 110 drives the rollers 120 to make eccentric movements within the cylinder cavity, and the outer peripheral surface of the rollers 120 forms a dynamically sealed working chamber with the inner wall of the cylinder cavity of the cylinder 200. During this process, the other end of the vane 320 can slide radially along the cylinder 200 within the slide rail 310 to abut against the outer peripheral surface of the rollers 120, and divide the chamber into an intake chamber and a compression chamber. Thus, as the main shaft 110 continues to rotate, the volume of the intake chamber gradually increases, drawing external gas into the cylinder cavity through the intake passage. As the roller 120 continues to rotate, the intake chamber is gradually closed by the sliding vane 320 and transformed into a compression chamber, with its volume continuously decreasing, achieving gas compression. The built-in channel 321 reciprocates with the sliding vane 320, and its end furthest from the compression chamber periodically aligns with the opening, connecting the supplementary air passage 210 with the middle section of the compression chamber. Low-pressure gas is injected into the intake chamber at appropriate times, increasing the exhaust volume and energy efficiency ratio. This process is repeated cyclically, ensuring the compressor operates in a highly efficient and stable state.

[0034] In other words, during compressor operation, the compressor cylinder cavity can be replenished with gas through the gas replenishment channel 210. The external gas source is low-pressure gas. This increases the gas density within the cylinder cavity, thereby enhancing the compressor's compression capacity. The design of the gas replenishment channel ensures that the external gas source can be introduced into the cylinder cavity after the intake process is complete.

[0035] Furthermore, in this design, the supplementary air passage 210 is arranged opposite to the intake passage of the cylinder cavity. This ensures that the relative position of the supplementary air passage 210 and the intake passage achieves optimal gas flow during compressor operation.

[0036] Specifically, the air replenishment channel 210 extends to the first side end of the slide rail 310. Further, the first side end extends along a first direction, which is the radial direction of the cylinder 200. The first side end faces the air replenishment channel 210 and has an opening. When the roller 120 rotates to block the air intake channel, the slide vane 320 completely moves out along the slide rail 310, allowing the internal channel 321 to connect with the air replenishment channel 210 through the opening and communicate with the middle section of the compression chamber. At this time, an external medium-pressure air source is directionally introduced into the compression chamber through the air replenishment channel 210 and the internal channel 321, thereby achieving precise air replenishment to the compression chamber, increasing the gas density in the compression chamber, and improving compression efficiency. This avoids the leakage problems present in traditional valve structures, ensuring the sealing and controllability of the air replenishment process. Through the periodic movement of the slide vane 320, the internal channel 321 and the air replenishment channel 210 can connect at specific times, thereby adjusting the air replenishment amount and avoiding efficiency reduction due to insufficient or excessive air replenishment.

[0037] Furthermore, as the roller 120 continues to rotate, the vane 320 gradually moves into the slide rail 310, separating the built-in channel 321 from the air supply channel 210, and the air supply path gradually closes until the roller fully opens the intake channel, thus preventing gas backflow or leakage. In other words, it ensures that the gas in the cylinder cavity does not flow back into the air supply channel 210, while maintaining stable pressure within the cylinder cavity. In this way, the compressor can maintain efficient operation under different working conditions and improve overall performance.

[0038] In this design, as the slide plate 320 gradually extends out of the slide rail 310, the cross-sectional area of ​​the internal channel 321 gradually increases until it is fully connected with the internal channel 321. During this process, the connection between the internal channels 321 is a gradual process and is located at the end of one revolution of the main shaft 110 and the roller 120, which has minimal impact on air intake and avoids the impact of the re-expansion of supplementary gas on the unit air intake volume.

[0039] One end of the vane 320 is connected to the side of the slide rail 310 away from the working chamber via a spring 400. The spring 400 provides stable power support for the vane 320's movement in and out. Specifically, when the vane 320 moves within the slide rail 310, the spring 400, through its own tension and compression characteristics, stores elastic energy when the vane 320 moves in and releases that energy when the vane 320 moves in, effectively reducing the need for external driving force. This design not only improves the smoothness of the vane 320's movement but also reduces mechanical wear and energy loss, further improving the overall efficiency of the compressor.

[0040] By employing the above technical solution, the enthalpy increase of the compression chamber can be achieved through the cooperation of the air supply channel provided on the side wall of the cylinder and the sliding vane with a built-in channel in the slide rail. Specifically, during compressor operation, the air supply channel and the built-in channel of the sliding vane can be connected during the rotation of the rotating assembly. When the rotating assembly rotates to block the intake channel, the sliding vane moves out of the slide rail, allowing the built-in channel to connect with the air supply channel and reach the middle section of the cylinder. At this time, an external air source can be introduced into the cylinder, thereby achieving air supply to the compressor, increasing the pressure and gas density in the compression chamber, and improving compression efficiency. As the rotating assembly continues to rotate, the sliding vane gradually moves into the slide rail to close the air supply channel. The periodic connection between the built-in channel of the sliding vane and the air supply channel allows for flexible adjustment of the air supply amount according to actual operating conditions, thereby achieving air supply and enthalpy increase of the compressor. This ensures that the compressor maintains a highly efficient and stable operating state under different load conditions. In addition, this solution can also avoid the problem of decreased compression efficiency caused by untimely or excessive air supply, optimizing the overall performance of the compressor.

[0041] In an alternative embodiment of the compressor described above, the built-in channel 321 is configured as an arc-shaped channel and bends in a direction away from the replenishment channel 210.

[0042] By configuring the built-in channel 321 as an arc-shaped channel, curving away from the direction of the supplementary air channel 210, the airflow can be made smoother during transmission, reducing energy loss and pressure fluctuations caused by abrupt changes in direction. The arc-shaped channel design can also effectively reduce the impact of airflow impact on the gas distribution inside the cylinder cavity, thereby improving the stability of the compression process. In addition, this design can optimize the dynamic performance of the vanes when moving into and out of the slideway, ensuring more precise and efficient docking and separation of the built-in channel and the supplementary air channel. In this way, not only can the controllability of the supplementary air volume be improved, but the adaptability of the compressor under different operating conditions can also be further enhanced, making its operation more stable and reliable.

[0043] Optionally, to further improve the performance of the arc-shaped channel, a low-resistance coating can be added to its inner wall to reduce energy loss caused by airflow friction.

[0044] Furthermore, the curved design of the built-in channel 321 also provides a certain degree of backflow prevention. As the vane 320 gradually moves into the slide rail 310, the outlet of the arc-shaped channel will preferentially disconnect from the cylinder cavity, thereby preventing high-pressure gas from flowing back into the replenishment channel 210. This ingenious structural design not only simplifies the sealing mechanism but also improves the overall reliability of the compressor, providing a strong guarantee for long-term, high-efficiency operation.

[0045] In an alternative embodiment of the compressor described above, the vane has a first side end wall 322 facing the opening, and the built-in channel 321 includes an inflow section 3211, a guide section 3212, and an outflow section 3213. The inflow section 3211 extends along the direction of the replenishment channel, and the inlet 3201 of the inflow section 3211 is disposed on the first side end wall 322 of the vane 320 facing the replenishment channel 210; the guide section 3212 is bent and connected to the inflow section 3211 and extends along a first direction, wherein the guide section 3212 is configured to bend in a direction away from the replenishment channel 210; the outflow section 3213 is bent and connected to the guide section 3212, and the outlet 3202 of the outflow section 3213 is formed on the first side end wall 322.

[0046] Specifically, the built-in channel 321 includes an inlet section 3211, a guide section 3212, and an outlet section 3213. This forms a C-shaped built-in channel to effectively guide the airflow direction and reduce energy loss during transmission. The inlet section 3211 ensures that external low-pressure gas can smoothly enter the interior of the vane 320, while the bend and extension of the guide section 3212 optimizes the airflow path. The outlet section 3213 allows the airflow to enter the middle section of the compression chamber more gently, thereby improving the uniformity of gas distribution. This design makes the gas replenishment process more efficient and stable, while reducing the risk of pressure fluctuations caused by airflow turbulence.

[0047] Furthermore, by positioning the inlet of the inflow section 3211 on the first side end wall 322 of the vane 320 facing the supplementary air passage 210, and forming the outlet of the outflow section 3213 on the first side end wall 322, the communication between the built-in passage 321 and the compression chamber can be cut off when the vane 320 is fully moved into the slide rail 310. The inlet 3201 of the inflow section 3211 and the outlet 3202 of the outflow section 3213 are hidden within the slide rail 310 to avoid reverse airflow and ensure stable pressure within the compression chamber. This improves the accuracy of supplementary air and enhances the reliability of compressor operation. Simultaneously, the docking and disengagement of the built-in passage 321 and the supplementary air passage 210 during the movement of the vane 320 into and out of the slide rail 310 can be seamlessly switched, reducing efficiency losses due to mechanical lag. Furthermore, the curved design of the outflow section 3213 effectively reduces the impact of airflow impact on the gas distribution within the cylinder, thereby improving the smoothness of the compression process.

[0048] Optionally, when the vane 320 is fully inserted into the slide rail 310, the airflow outlet of the supplementary air passage 210, which connects with the built-in passage 321, is located between the inlet of the inflow section 3211 and the outlet of the outflow section 3213, and abuts against the side wall of the first side end wall 322 of the vane 320. This further prevents airflow leakage when the supplementary air passage 210 separates from the built-in passage 321. At this time, the first side end wall 322 of the vane 320, after being fully inserted into the slide rail 310, forms a reliable sealing barrier through its tight contact with the supplementary air passage 210. This not only ensures that the supplementary air path remains highly sealed in the closed state, but also effectively prevents high-pressure gas in the cylinder cavity from flowing back into the supplementary air passage, thereby further improving the stability and efficiency of the compressor operation.

[0049] Optionally, to further optimize the motion performance of the slide 320, the inner wall of the slide rail 310 is precision machined to reduce frictional resistance and improve the response speed of the slide 320. The slide 320 is made of high-strength, wear-resistant material, which can maintain stable performance during long-term, high-frequency reciprocating motion. Meanwhile, the gap between the slide 320 and the slide rail 310 is strictly controlled to ensure smooth movement of the slide 320 while minimizing gas leakage, thereby improving the overall sealing effect.

[0050] Alternatively, to enhance the fit accuracy between the slide plate 320 and the slide rail 310, a wear-resistant coating can be applied to the outer surface of the slide plate 320. This reduces the frictional resistance of the slide plate 320 as it moves within the slide rail 310, extends its service life, and ensures that it maintains good sealing performance throughout long-term operation. Simultaneously, the inner wall of the slide rail can be precision-machined to ensure surface smoothness and dimensional accuracy, further optimizing the dynamic fit between the slide plate and the slide rail.

[0051] Optionally, the inflow section 3211, guide section 3212, and outflow section 3213 are connected by sequentially curved bends, which further optimizes the airflow state within the built-in channel 321. The curved transition reduces energy loss during airflow transitions between different sections and avoids eddies and pressure fluctuations caused by right-angle bends. Simultaneously, the curved structure enhances the overall structural strength of the vane 320, making it less prone to deformation or damage during high-frequency reciprocating motion. Optionally, during the design process, the angle and radius of curvature of each curved section can be set differently to accommodate compressors of different power, thereby maintaining a stable flow velocity and direction throughout the transmission process, improving the efficiency and stability of the air replenishment process, effectively reducing airflow noise, and ensuring quiet operation of the compressor.

[0052] In an optional embodiment of the compressor described above, the portion of the first side end wall 322 located between the inlet 3201 of the inflow section 3211 and the outlet 3202 of the outflow section 3213 is configured as a sealing portion 3220; the supplementary air passage 210 has a connecting port 2101 communicating with the built-in passage; the cross-sectional area of ​​the inlet 3201 of the inflow section 3211 is larger than the cross-sectional area of ​​the connecting port 2101; and when the vane 320 is fully moved into the slide rail 310, the sealing portion 3220 abuts against the connecting port 2101, and the side of the sealing portion 3220 near the inlet 3201 of the inflow section 3211 is at least flush with the side wall of the connecting port 2101, so that the inlet 3201 of the inflow section 3211 is misaligned with the connecting port 2101.

[0053] In this way, when the sliding vane 320 initially moves outward from the slide rail 310, the air supply channel 210 is connected to the internal channel 321 via the interface 2101. As the sliding vane 320 gradually moves into the cylinder cavity, the air supply channel 210 gradually becomes fully connected to the internal channel 321. Throughout this process, the continuity of the air supply channel 210 is maintained. Simultaneously, the cross-sectional area of ​​the inlet of the inflow section 3211 is larger than the cross-sectional area of ​​the interface 2101, ensuring that the air supply channel 210 remains fully connected to the internal channel 321 as the sliding vane 320 gradually moves into the cylinder cavity along the slide rail 310.

[0054] In other words, the connection between the air supply channel 210 and the built-in channel 321 is a gradual process. In this design, this connection process occurs at the end of one rotation of the rotating assembly 100. Specifically, the angle at which the rotating assembly 100 rotates to the intake closing position is set to 0°, i.e., the intake closing angle is 0°. The rotating assembly 100 continues to rotate from this angle, allowing the slide plate 320 to gradually extend out of the slide rail 310. The air supply channel 210 gradually begins to connect with the built-in channel 321, thus initiating air supply. This continues until the slide plate 320 is gradually compressed and moved into the slide rail 310 under the rotation of the rotating assembly 100. After the slide plate 320 is completely moved into the slide rail 310, the inlet of the built-in channel 321 and the interface of the air supply channel 210 are misaligned, and the connection between them is broken. This allows for precise gas replenishment control throughout the entire compressor operating cycle. It not only avoids the gas backflow and leakage problems common in traditional gas replenishment methods, but also, due to the long replenishment stroke, helps improve the overall performance and efficiency of the compressor. This ensures the compressor maintains stable operation under various conditions, reducing energy loss and increasing efficiency. Furthermore, because the gas replenishment process occurs after the intake phase and at the end of the spindle rotation stroke, its impact on the unit intake volume is minimized, further enhancing the overall efficiency of the compressor.

[0055] Optionally, the outlet 3202 of the outflow section 3213 is positioned near the end of the vane 320 facing the cylinder cavity. This allows the internal channel 321 to connect with the cylinder cavity as the vane 320 initially moves out of the slide rail 310, thus enabling the air supply channel 321 to be open. This arrangement ensures that the connection between the internal channel 321 and the cylinder cavity is faster and more stable as the vane 320 moves out of the slide rail 310. This not only improves the efficiency of air supply but also avoids pressure fluctuations caused by untimely airflow path switching. Furthermore, the position of the outlet of the outflow section 3213 allows for a more uniform distribution of airflow upon entering the cylinder cavity, further optimizing the gas density and pressure state within the cylinder cavity.

[0056] In an alternative embodiment of the compressor described above, the cross-sectional area of ​​the inlet of the inflow section 3211 is larger than the cross-sectional area of ​​the outlet of the outflow section 3213.

[0057] This design helps reduce the flow resistance of gas during the inflow process, improves the gas injection response speed, and creates a certain throttling effect on the outflow side, which is beneficial for maintaining stable pressure within the cylinder cavity. The design of this cross-sectional area difference, combined with the reciprocating motion characteristics of the sliding vanes, further optimizes the dynamic balance of airflow during the gas injection process, thereby improving gas injection efficiency and the overall energy efficiency of the compressor.

[0058] In an alternative embodiment of the compressor described above, the spring 400 is fixedly connected to the vane 320; the spring 400 is configured to be stretched when the vane 320 extends along the slide rail and compressed when the vane 320 moves in.

[0059] During the stroke of the rotating assembly 100 from opening the air intake channel to closing the air intake channel, the roller 120 abuts against the slide 320 and compresses the spring 400; the rotating assembly gradually rotates to avoid the slide 320, and the slide extends out of the slide 310 under the action of the elastic force of the spring 400 so that the built-in channel 321 gradually connects with the air replenishment channel 210.

[0060] The spring 400 provides stable power support for the movement of the vane 320. Specifically, when the vane 320 moves within the slide rail 310, the spring 400, through its own tension and compression characteristics, stores elastic energy when the vane 320 moves in and releases that energy when the vane 320 moves in, thus effectively reducing the need for external driving force. This design not only improves the smoothness of the vane 320's movement but also reduces mechanical wear and energy loss, further improving the overall efficiency of the compressor.

[0061] Optionally, the side wall of the cylinder 200 is provided with a spring receiving hole, one end of the spring 400 is fixedly installed in the spring receiving hole, and the other end is fixedly connected to the slide plate 320.

[0062] Preferably, spring 400 is a spring. Alternatively, spring 400 may be an elastic rubber component or a component made of other materials with similar elasticity.

[0063] Optionally, spring 400 is made of a highly elastic, fatigue-resistant material, enabling it to maintain stable performance during long-term operation. Simultaneously, the stiffness coefficient of spring 400 is calculated to ensure it provides appropriate elasticity under different operating conditions, avoiding problems such as uncoordinated movement of the slider 320 due to insufficient or excessive elasticity. This design allows the slider 320 to maintain precise displacement control under various operating conditions, thereby improving the reliability of the air supply path's connection and closure.

[0064] Furthermore, the spring 400 and the vane 320 can be connected via a detachable fixing structure, allowing the spring 400 to be quickly disassembled when maintenance or replacement is required, thus simplifying the compressor maintenance process. Simultaneously, the connection points are precision-machined to ensure they do not loosen or detach during high-frequency operation, further enhancing the stability and safety of the compressor operation.

[0065] In an optional embodiment of the compressor described above, a backflow preventer 500 is provided in the gas supply passage 210. The valve body 510 of the backflow preventer 500 extends obliquely along the airflow direction in the gas supply passage 210. The backflow preventer 500 is configured to open the gas supply passage 210 when the slide plate 320 extends out of the slide rail 310 and the pressure in the cylinder cavity is less than the pressure in the gas supply passage 210, and to close the gas supply passage 210 when the pressure in the cylinder cavity is greater than or equal to the pressure in the gas supply passage 210.

[0066] By incorporating the backflow preventer 500, the precise opening and closing of the gas supply channel 210 can be ensured while effectively preventing gas backflow. Specifically, when the vane 320 moves out of the slide rail 310, the backflow preventer 500 automatically opens under the action of the gas flow used for gas supply, allowing external low-pressure gas to smoothly pass through the gas supply channel 210 and enter the internal channel 321 before entering the cylinder cavity. Conversely, when the vane 320 moves into the slide rail 310, the internal channel 321 cuts off the connection with the gas supply channel 210, i.e., cuts off the connection between the cylinder cavity and the gas supply channel 210. At this time, the backflow preventer 500 quickly resets due to its structural characteristics, tightly fitting against the inner wall of the gas supply channel 210, thereby cutting off the airflow path and preventing high-pressure gas in the cylinder cavity from leaking back into the gas supply channel 210. This not only improves the controllability of the gas supply process but also further enhances the sealing and stability of the compressor operation.

[0067] Furthermore, when the rotating assembly 100 rotates to the point where the pressure in the compressor cavity and the gas supply channel 210 are the same, the backflow preventer 500 can automatically prevent the high-pressure gas in the cylinder cavity from flowing back.

[0068] In addition, combined Figure 12 As shown (where the horizontal axis represents the rotation angle of the rotating component and the vertical axis represents the cylinder pressure inside the compressor), the backflow preventer 500 changes with the cylinder pressure and the injection pressure when it opens or closes: assuming the intake pressure is A, the exhaust pressure is B, and the cylinder pressure is C, then the injection pressure... When D > C, the check valve 500 opens to allow for gas replenishment; when D ≤ C, the cylinder pressure and the gas replenishment pressure reach a pressure balance, and the check valve 500 resets. Thus, the gas replenishment channel 210 can be closed according to the balance point between the cylinder pressure and the gas replenishment pressure, maximizing the utilization of the gas replenishment stroke and further optimizing the compressor's gas replenishment efficiency.

[0069] Furthermore, the inclined arrangement of the backflow preventer 500 optimizes its response speed and sealing effect. Because the valve body 510 extends inclined along the airflow direction, the airflow impact force can directly act on the surface of the valve body 510, allowing it to respond quickly when needed and, when closed, rely on its own elasticity to form a tight seal with the inner wall of the channel. This reduces efficiency losses caused by mechanical lag and effectively reduces pressure fluctuations caused by gas leakage, thus providing a more stable operating environment for the compressor.

[0070] Optionally, to further improve the performance of the check valve plate, a highly elastic and corrosion-resistant alloy material is selected to ensure good mechanical properties and fatigue resistance during long-term, high-frequency opening and closing. Simultaneously, the surface of the valve plate body 510 undergoes special treatment to form a low-friction coating, reducing wear when in contact with the inner wall of the air supply channel and improving its operational sensitivity. This comprehensive optimization enables the check valve plate to exhibit excellent reliability and durability under various operating conditions, providing strong support for improving the overall performance of the compressor.

[0071] In an optional embodiment of the compressor described above, the gas supply channel 210 includes a first channel 211 and a second channel 212 connected in sequence; the first channel 211 is connected to an external gas source, and the diameter of the second channel 212 is smaller than the diameter of the first channel 211; wherein, the backflow preventer 500 is disposed in the first channel 211.

[0072] By setting a difference in diameter between the first channel 211 and the second channel 212, the transmission efficiency and control precision of the airflow can be further optimized. Specifically, the larger diameter of the first channel 211 reduces the resistance when the airflow enters, ensuring that the external low-pressure gas can flow into the replenishment channel 210 quickly and smoothly; while the smaller diameter of the second channel 212 can create a certain acceleration effect when the airflow approaches the cylinder cavity, allowing the gas to enter the built-in channel 321 at a higher flow rate, thereby improving the efficiency and uniformity of the replenishment process. In addition, this structural design can also enhance the sealing performance of the backflow preventer 500 to a certain extent, because the narrow space of the second channel 212 can increase the resistance when the gas flows back, further reducing the risk of leakage.

[0073] Optionally, to better match the gas replenishment requirements under different operating conditions, a transition section can be provided at the connection between the first channel 211 and the second channel 212. The transition section adopts an arc-shaped design to reduce energy loss caused by sudden changes in airflow direction. Simultaneously, a low-friction coating can be added to the inner wall of the transition section to further reduce airflow resistance during transmission and improve overall gas replenishment efficiency. This refined design not only meets the compressor's operating requirements under high-load conditions but also maintains a stable gas replenishment effect under low-load conditions, thereby comprehensively improving the compressor's adaptability and reliability.

[0074] Furthermore, the connection between the first section of channel 211 and the external air source can be designed as an adjustable structure. By adjusting the opening during air intake, the amount of supplementary air can be controlled, allowing the compressor to flexibly adjust the supplementary air parameters according to the actual operating conditions, thereby maintaining optimal operating efficiency under different operating conditions. Simultaneously, to prevent external impurities from entering the supplementary air channel 210, a filter device can be added at the air intake of the first section of channel 211 to block particulate matter without increasing airflow resistance.

[0075] In an optional embodiment of the compressor described above, the fixed end of the valve plate body 510 is fixedly connected to the side wall of the second channel 212; the free end of the valve plate body 510 can abut against the side wall of the second channel 212; wherein, the side wall portion of the second channel 212 is recessed inward to abut against the free end of the valve plate body 510.

[0076] In this section, the sidewall portion of the second channel 212 is recessed inward to form a recessed portion, and the free end of the valve body 510 abuts against the side of the recessed portion away from the first channel 211. Specifically, the sidewall abutting against the free end of the valve body 510 is recessed inward.

[0077] By setting the sidewall portion of the second channel 212 to be recessed inward to abut against the free end of the valve body 510, the sealing performance of the check valve 500 in the closed state can be improved. Specifically, when the free end of the valve body 510 is tightly fitted with the recessed portion, a more reliable sealing barrier can be formed, effectively preventing high-pressure gas in the cylinder cavity from flowing back into the gas supply channel 210. This not only enhances the sealing effect but also reduces pressure fluctuations caused by gas leakage, thereby further improving the stability and efficiency of compressor operation.

[0078] Optionally, the diameter of the channel on the side of the recess near the built-in channel within the second channel 212 is larger than the diameter of the channel on the side of the recess near the first channel 211.

[0079] Optionally, the surface of the recessed portion needs to be set as a flat and smooth surface to ensure a high degree of flatness and smoothness when in contact with the free end of the valve plate body 510, so as to avoid affecting the sealing performance due to uneven surface. At the same time, this design can also reduce the mechanical stress on the valve plate body 510 during frequent opening and closing, extend its service life, and provide a guarantee for the long-term efficient operation of the compressor.

[0080] Furthermore, by creating the recessed portion, a sudden change in flow can be formed within the second channel 212, further improving the uniformity of the velocity and pressure distribution of the airflow used for replenishment, reducing airflow stagnation within the channel, and avoiding uneven replenishment caused by excessively high or low local pressure. Simultaneously, the recessed portion design can also optimize the closing action of the check valve 500 to a certain extent, making its reset more precise and rapid, thereby further improving the opening and closing efficiency of the replenishment channel 210.

[0081] Alternatively, to further enhance the functionality of the recess, its edges can be designed with rounded transitions to reduce the impact of airflow on the valve body 510 and reduce noise problems caused by turbulence.

[0082] Optionally, adding a wear-resistant coating to the surface of the recess can further improve its wear resistance, especially during high-frequency opening and closing processes, effectively extending the service life of the first channel 211. Simultaneously, this coating can reduce the friction between the valve body 510 and the recess, making the backflow preventer valve 500 more sensitive, thereby improving the overall system's response speed and reliability.

[0083] Alternatively, to further optimize the fit accuracy between the valve body 510 and the sidewall of the first channel 211, an elastic sealing material can be added to the surface of the recessed portion. This material provides additional cushioning when the free end of the valve body 510 contacts it, reducing the impact of impact forces on the valve body and improving the tightness of the seal. Furthermore, the selection of the elastic sealing material must consider high-temperature resistance, corrosion resistance, and aging resistance to ensure stable performance under various operating conditions. This comprehensive optimization not only improves the overall reliability of the check valve 500 but also provides strong support for the stability of the compressor in complex operating environments.

[0084] In an alternative embodiment of the compressor described above, the first channel 211 is configured such that its diameter gradually decreases along the direction toward the second channel 212.

[0085] By configuring the first channel 211 with a gradually decreasing diameter along the direction towards the second channel 212, the airflow can be gradually accelerated before entering the second channel 212, thereby improving the smoothness and efficiency of gas flow. This design not only reduces energy loss caused by abrupt diameter changes but also effectively prevents the formation of eddies or pressure fluctuations in the airflow within the channel, further optimizing the stability of the gas replenishment process. Furthermore, the gradually decreasing diameter design can also enhance the sealing performance of the check valve 500 to some extent, as the airflow forms a more uniform pressure distribution as it passes through the first channel 211, thus reducing the possibility of gas backflow.

[0086] Optionally, to better control the acceleration effect of the airflow, the inner wall of the first channel 211 can adopt a multi-stage conical design. The angle of each stage of the cone is precisely calculated to ensure that the acceleration process of the airflow is smooth and controllable at different stages. At the same time, a low-resistance coating can be added to the inner wall surface to further reduce energy loss caused by airflow friction and improve the overall gas supply efficiency. This refined design not only meets the operating requirements of the compressor under high-load conditions but also maintains a stable gas supply effect under low-load conditions, thereby comprehensively improving the adaptability and reliability of the compressor.

[0087] Furthermore, the tapered diameter design of the first channel 211 can be matched with the intake parameters of the external air source, adapting to different intake pressure and flow requirements by adjusting the tapering angle and length. This flexibility allows the compressor to dynamically adjust the supplementary air parameters according to the actual operating conditions, thereby achieving optimal operating efficiency under various operating conditions. Simultaneously, to prevent excessively high local pressure caused by the tapered diameter, a pressure balancing device can be added at the end of the first channel 211 to ensure a stable pressure distribution when the airflow transitions to the second channel 212.

[0088] In an optional embodiment of the compressor described above, an upper flange 610 and a lower flange 620 are also included. The upper flange 610 and the lower flange 620 are respectively covered on the upper end face and the lower end face of the cylinder 200, and both the upper flange 610 and the lower flange 620 are rotatably engaged with the main shaft 110; wherein, the upper flange 610 and the upper end face of the cylinder 200 are in contact and sealed, and the lower flange 620 and the lower end face of the cylinder 200 are in contact and sealed; or, a sealing gasket is provided between the upper flange 610 and the upper end face of the cylinder 200, and between the lower flange 620 and the lower end face of the cylinder 200.

[0089] By setting up an upper flange and a lower flange structure, the sealing performance between the cylinder and the main shaft can be effectively improved, while ensuring the stability of the compressor during long-term operation.

[0090] Optionally, the upper flange 610 and the upper end face of the cylinder 200, and the lower flange 620 and the lower end face of the cylinder 200, are both abutted and sealed. Specifically, the abutment sealing structure achieves a gapless fit through precision-machined contact surfaces, effectively blocking the path of gas leakage along the main shaft, while avoiding the sealing failure caused by aging and deformation of the gasket under high temperature and high pressure conditions. This not only improves the operational reliability of the compressor under extreme conditions but also reduces maintenance frequency and operating costs, making it particularly suitable for refrigeration equipment operating under long-term high loads.

[0091] In addition, the choice of sealing structure can be adapted according to the actual working conditions, taking into account both assembly convenience and cost control while ensuring sealing reliability.

[0092] Alternatively, the addition of a gasket can form a reliable sealing barrier between the flange and the cylinder end face, preventing gas leakage or intrusion of external impurities, thereby further optimizing the overall efficiency and reliability of the compressor. Furthermore, the rotational fit design between the upper and lower flanges and the main shaft not only reduces frictional losses but also improves the smoothness of the main shaft operation, providing strong support for the efficient operation of the compressor.

[0093] Optionally, the gasket is made of high-performance materials that are resistant to high temperatures and corrosion to ensure excellent sealing performance under high pressure and high temperature conditions. At the same time, the thickness and elasticity of the gasket are precisely calculated to adapt to pressure changes under different operating conditions, avoiding seal failure due to overpressure or underpressure. This design enables the compressor to exhibit outstanding stability and durability in various complex environments.

[0094] In addition, to further enhance the connection strength between the upper flange 610 and / or the lower flange 620 and the cylinder 200, an anti-slip texture design can be added to the contact surface between the upper flange 610 and / or the lower flange 620 and the cylinder 200 to enhance the friction between the two and prevent loosening during high-frequency vibration or high-load operation.

[0095] Optionally, reinforcing ribs can be added to the outer side of the upper flange 610 and / or the lower flange 620 to improve their resistance to deformation, especially under high-pressure conditions, effectively dispersing stress concentration and extending the service life of the flange. Furthermore, the reinforcing rib design can also optimize the heat dissipation performance of the upper flange 610 and / or the lower flange 620 to a certain extent, avoiding the problem of material performance degradation due to localized overheating, thus providing additional protection for the long-term stable operation of the compressor.

[0096] In the optional implementation of the compressor described above, combined with Figures 13 to 15 As shown, the eccentricity of the main shaft is e, and the eccentric diameter is D1; ​​the outer diameter of the roller is D2; the diameter of the cylinder assembly surface is D3; the distance from the inlet end of the air replenishment channel 210 to the center of the cylinder is L1; the inlet of the built-in channel 321 on the first side end wall 322 of the vane 320 includes a first side and a second side, with the first side close to the spring 400; the distance between the first side and the end of the vane close to the spring 400 is L2, and the distance between the second side and the end of the vane close to the spring 400 is L3. When the roller completely blocks the air intake channel, the following requirements must be met: L1-e-D2 / 2-L2≥0, to prevent the air replenishment channel from opening too early and affecting the unit intake volume of the compressor; and D3-e-D2 / 2-L3≥1, to prevent air leakage during the air replenishment process.

[0097] The structural design provided in this solution can be referenced and slightly modified by professionals in related industries. Therefore, anything with the same working principle can be considered a derivative of this solution, which can also be used for twin-cylinder structures. Combined with... Figure 16 As shown, exemplarily, the compressor includes an upper cylinder section 201 and a lower cylinder section 202, with a partition 203 between the upper cylinder section 201 and the lower cylinder section 202. The first section 211 of the air supply channel 210 is symmetrically arranged on the side walls of the upper cylinder section 201 and the lower cylinder section, respectively. The second section 212 of the air supply channel 210 is arranged on the partition 203, and the second section 212 of the air supply channel 210 communicates simultaneously with the first section 211 of the air supply channel 210 arranged in the upper cylinder section 201 and the lower cylinder section. Further, two sets of sliding vanes 320 and sliding rails 310 are provided, symmetrically arranged on the side walls of the upper cylinder section 201 and the lower cylinder section 202.

[0098] Secondly, this application provides a refrigeration device, including a compressor as described above.

[0099] The above description is only a preferred embodiment of this application. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. A compressor, characterized in that, include: A cylinder has a cylindrical cavity defined inside. A slide rail communicating with the cavity is provided on the side wall of the cylinder. The side wall of the cylinder also has an intake channel and a replenishment channel. The intake channel is used for drawing in air. One end of the replenishment channel is configured to communicate with an external medium-pressure air source, and the other end of the replenishment channel extends to a first side end of the slide rail, configured to be controllably connected to the slide rail. The first side end of the slide rail has an opening facing the replenishment channel. The rotating assembly includes a main shaft and a roller driven by the main shaft to make eccentric movements in the cylinder cavity, wherein the outer peripheral surface of the roller forms a dynamically sealed working cavity with the inner wall of the cylinder cavity; A sliding plate, one end of which is connected to the side of the slide rail away from the working chamber by a spring; the other end of which can slide radially within the slide rail to abut against the outer circumferential surface of the roller, thus dividing the chamber into an intake chamber and a compression chamber; wherein, the sliding plate has an internal channel for transmitting airflow, one end of which can be controllably connected to the compression chamber, and the other end of which is opened in the sliding plate and can selectively communicate with the air supply channel through the opening; The slide is configured to extend or move into the slide along the extension direction of the slide when the rotating assembly rotates, so that the built-in channel and the air supply channel periodically align to intermittently form an air supply path that connects to the cylinder cavity.

2. The compressor according to claim 1, characterized in that, The slide has a first side end wall facing the opening; The built-in channel includes: The inflow section extends along the direction of the air replenishment channel, and the inlet of the inflow section is located on the first side end wall; A guide section, which bends and connects with the inflow section and extends along the first direction, wherein the guide section is configured to bend toward a direction away from the air supply channel; The outflow section is bent and connected to the guide section, and the outlet of the outflow section is formed on the first side end wall.

3. The compressor according to claim 2, characterized in that, The portion of the first side end wall located between the inlet of the inflow section and the outlet of the outflow section is configured as a sealing portion; the air replenishment channel has a connecting interface communicating with the built-in channel; The cross-sectional area of ​​the inlet of the inflow section is larger than the cross-sectional area of ​​the docking interface; When the slide plate is fully moved into the slide channel, the blocking part abuts against the docking interface, and the side of the blocking part near the inlet of the inflow section is at least flush with the side wall of the docking interface, so that the inlet of the inflow section is misaligned with the docking interface.

4. The compressor according to claim 2, characterized in that, The cross-sectional area of ​​the inlet of the inflow section is larger than the cross-sectional area of ​​the outlet of the outflow section.

5. The compressor according to claim 1, characterized in that, The spring is fixedly connected to the slider, and the spring is configured to be stretched when the slider extends along the slide rail and compressed when the slider moves in. During the stroke of the rotating assembly from opening the air intake channel to closing the air intake channel, the roller abuts against the slide and compresses the spring; the rotating assembly gradually rotates to avoid the slide, and the slide extends out of the slide under the elastic force of the spring so that the built-in channel gradually connects with the air replenishment channel.

6. The compressor according to claim 5, characterized in that, The air supply channel is equipped with a backflow preventer, and the valve body of the backflow preventer extends obliquely along the airflow direction in the air supply channel. The anti-backflow valve is configured to open the air supply channel when the slide plate extends out of the slide and the pressure in the cylinder cavity is less than the pressure in the air supply channel, and to close the air supply channel when the pressure in the cylinder cavity is greater than or equal to the pressure in the air supply channel.

7. The compressor according to claim 6, characterized in that, The gas replenishment channel includes a first channel and a second channel connected in sequence. The first channel is connected to an external air source, and the diameter of the second channel is smaller than the diameter of the first channel. The anti-backflow valve is located in the first channel section.

8. The compressor according to claim 7, characterized in that, The fixed end of the valve plate body is fixedly connected to the side wall of the first channel section; The free end of the valve plate body can abut against the side wall of the first channel. The sidewall portion of the first channel is recessed inward to abut against the free end of the valve body.

9. The compressor according to claim 7, characterized in that, The first channel segment is configured such that its diameter gradually decreases along the direction toward the second channel segment.

10. The compressor according to claim 1, characterized in that, Also includes: The upper flange and the lower flange are respectively covered on the upper end face and the lower end face of the cylinder, and both the upper flange and the lower flange are rotatably engaged with the main shaft; Wherein, the upper flange and the upper end face of the cylinder are in contact and sealed, and the lower flange and the lower end face of the cylinder are in contact and sealed; or, a sealing gasket is provided between the upper flange and the upper end face of the cylinder, and between the lower flange and the lower end face of the cylinder.

11. The compressor according to claim 1, characterized in that, The spindle has an eccentricity of e and an eccentric diameter of D1. The outer diameter of the roller is D2; The diameter of the cylinder mounting surface is D3; The distance from the inlet end of the air supply channel to the center of the cylinder is L1; The inlet of the built-in channel on the first side wall of the slider includes a first side and a second side opposite to each other, the first side being close to the spring; the distance between the first side and the end of the slider close to the spring is L2, and the distance between the second side and the end of the slider close to the spring is L3. When the roller completely blocks the air intake passage, the following requirements must be met: L1-e-D2 / 2-L2≥0 to prevent the air replenishment passage from opening too early; and D3-e-D2 / 2-L3≥1 to prevent air leakage during the air replenishment process.

12. A refrigeration device, characterized in that, include: The compressor as described in any one of claims 1 to 11.

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