Compression air cylinder, compressor and refrigeration equipment

Abstract

The invention relates to a compression air cylinder, a compressor and refrigeration equipment, and relates to the technical field of compressors. The compression cylinder according to the present invention comprises: a cylinder having a chute; the rolling piston is located in the center hole of the air cylinder, part of the cylindrical surface of the rolling piston is attached to the hole wall of the center hole, and the rolling piston is used for rotating in the center hole; the sliding piece is arranged in the sliding groove in a sliding mode, and the sliding piece and the rolling piston can divide the space between the air cylinder and the rolling piston into a high-pressure cavity and a low-pressure cavity together. Wherein an annular groove is formed in the end face of the rolling piston, the vertical distances from all positions of the annular groove to the cylindrical surface are equal, the sliding piece is provided with a matching part, the matching part is inserted into the annular groove, and the matching part can slide or roll in the extending direction of the annular groove, so that the abutting surface of the sliding piece abuts against the cylindrical surface all the time. A gap is prevented from being reserved between the sliding vane and the rolling piston in the using process, the sealing performance in the gas compression process can be guaranteed, and abnormal sound caused by collision of the sliding vane in the running process is reduced.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and particularly to a compression cylinder, compressor, and refrigeration equipment. Background Technology

[0002] In the field of air conditioning compressors, rolling piston compressors are often used to compress gas. A rolling piston compressor includes a cylinder, a rolling piston housed within the cylinder, and a sliding vane slidably mounted in a groove within the cylinder. A spring within the cylinder groove pushes the vane, ensuring it remains in contact with the rolling piston at all times. The cylinder cavity is divided into two chambers by the vane and the rolling piston. As the rolling piston rotates, one chamber expands, creating negative pressure that draws in outside gas, while the other chamber contracts, pressurizing and expelling the gas inside.

[0003] However, in actual use, the limitations of the conventional spring-and-slider structure mean that the slider cannot maintain constant contact with the rolling piston during low-frequency operation, resulting in a gap between the slider and the cylinder. This causes the cavities on both sides of the slider to connect, reducing the gas compression effect, and also produces abnormal noise due to the collision between the slider and the cylinder, leading to a poor user experience. Summary of the Invention

[0004] This invention provides a compression cylinder, a compressor, and a refrigeration device to optimize the problem of vane and rolling piston disengagement during low-frequency operation of the compressor and improve the overall lubrication of the compressor, so as to achieve better gas compression effect and reduce abnormal noise of the compressor.

[0005] This invention provides a compression cylinder, comprising: A cylinder, which has a sliding groove; A rolling piston, located within the central bore of the cylinder, wherein a portion of the cylindrical surface of the rolling piston is in contact with the bore wall of the central bore, and the rolling piston is configured to rotate within the central bore; and A sliding plate is slidably disposed in the sliding groove, and the sliding plate, together with the rolling piston, can divide the space between the cylinder and the rolling piston into a high-pressure chamber and a low-pressure chamber; The end face of the rolling piston is provided with an annular groove, and the vertical distance from each part of the annular groove to the cylindrical surface is equal. The slide is provided with a mating part, which is inserted into the annular groove and can slide or roll along the extension direction of the annular groove, so that the contact surface of the slide is always in contact with the cylindrical surface.

[0006] In one embodiment, the slide includes a main body portion received in the slide groove, the abutting surface being the side of the main body portion facing the cylindrical surface, the slide also includes a guide portion extending out of the slide groove, the guide portion extending along the extension direction of the slide groove to the axial outer side of the rolling piston, and the mating portion being disposed on the side of the guide portion facing the rolling piston.

[0007] In one embodiment, the cylinder is connected to a first flange and a second flange at its two axial ends respectively. The end face of the rolling piston with the annular groove abuts against the first flange, and the other end face of the rolling piston abuts against the second flange to seal the two axial ends of the central hole. The first flange is provided with a guide groove that communicates with the slide groove, and the guide part is inserted into the guide groove.

[0008] In one embodiment, the annular groove stores lubricant.

[0009] In one embodiment, the mating part is a rolling ball embedded in the slide, and the portion of the mating part protruding from the slide is inserted into the annular groove, wherein the mating part is capable of rolling relative to the slide.

[0010] In one embodiment, the mating part is a protruding structure integrated with the slider.

[0011] In one embodiment, the cylindrical surface of the rolling piston is cylindrical, the annular groove surrounds to form an annular structure, and the central axis of the cylindrical surface coincides with the central axis of the annular groove.

[0012] In one embodiment, the groove extends radially along the central hole, the radius of the central hole is r1, the radius of the cylindrical surface is r2, the radius of the annular trajectory of the annular groove is r3, and r1, r2, and r3 satisfy r3 + r2 > r1 > r2 > r3.

[0013] In one embodiment, the rolling piston is connected to a drive shaft, the rotation axis of which is parallel to and spaced apart from the central axis of the rolling piston, so that the rolling piston rotates eccentrically within the central hole.

[0014] In one embodiment, the drive shaft has an eccentric portion that is eccentric to its axis of rotation, and the rolling piston is a sleeve structure fitted over the eccentric portion.

[0015] In one embodiment, the cylinder is further provided with an air inlet and an air outlet, both of which are connected to the central hole and are located on opposite sides of the slide groove.

[0016] Secondly, the present invention also provides a compressor, characterized in that it includes the aforementioned compression cylinder.

[0017] Secondly, the present invention also provides a refrigeration device, which includes the compressor described above.

[0018] Compared with the prior art, the advantages of this invention lie in the provision of an annular groove at the end of the rolling piston and a mating part on the slide. By inserting the mating part into the annular groove, the rolling piston can directly drive the slide to move, realizing the reciprocating sliding of the slide, thus eliminating the need for a spring structure. Because the distance from all points of the annular groove to the cylindrical surface is equal, the distance between the mating part and the cylindrical surface remains constant at all times. This ensures that the contact surface of the slide is always in contact with the cylindrical surface, avoiding gaps between the slide and the rolling piston during use, guaranteeing the sealing of the gas compression process, and reducing abnormal noise from slide collisions during operation. Attached Figure Description

[0019] The invention will now be described in more detail with reference to embodiments and the accompanying drawings.

[0020] Figure 1 This is a cross-sectional structural diagram of a rolling piston compressor pump in related technologies; Figure 2 This is a three-dimensional structural diagram of the compression cylinder with the second flange hidden in an embodiment of the present invention; Figure 3 for Figure 2 A cross-sectional view of a medium compression cylinder; Figure 4 for Figure 3 A partially enlarged schematic diagram of the connection between the middle sliding plate and the rolling piston; Figure 5 This is a three-dimensional structural diagram of the rolling piston in an embodiment of the present invention; Figure 6 This is a three-dimensional structural diagram of the slider in an embodiment of the present invention; Figure 7 This is a three-dimensional structural diagram of the first flange in an embodiment of the present invention; Figure 8 This is a schematic diagram illustrating the change in distance between the mating part and the contact surface during the movement of the rolling piston in an embodiment of the present invention; Figure 9 for Figure 8 Dimensional relationship diagram under state ②.

[0021] Figure label: 100. Cylinder; 110. Center hole; 111. High-pressure chamber; 112. Low-pressure chamber; 120. Slide groove; 200, rolling piston; 210, cylindrical surface; 220, annular groove; 300, sliding plate; 310, mating part; 320, main body; 321, contact surface; 330, guide part; 400. First flange; 410. Guide groove; 500, drive shaft; 510, eccentric part; 600. Spring; 700, Second Flange. Detailed Implementation

[0022] The invention will now be further described with reference to the accompanying drawings.

[0023] See Figure 1 The diagram shows a type of compression pump using a rolling piston 200 in the prior art. The rolling piston 200 can push the sliding vane 300 away from the center of the cylinder 100, while the spring 600 can push the sliding vane 300 towards the center of the cylinder 100. Through the cooperation of the rolling piston 200 and the spring 600, the sliding vane 300 can always remain in contact with the cylindrical side of the rolling piston 200, thereby dividing the chamber within the cylinder 100 into a high-pressure chamber 111 and a low-pressure chamber 112.

[0024] However, the spring 600 is prone to aging under frequent compression and elongation changes, often resulting in a delay in pushing the slide 300 back to the center of the cylinder 100. This leads to a gap between the slide 300 and the rolling piston 200, causing the high-pressure chamber 111 and the low-pressure chamber 112 to connect, thus preventing the gas compression function from being achieved. Moreover, due to the reciprocating eccentric motion of the rolling piston 200, even if the slide 300 is stuck, the rolling piston 200 will still rotate to re-engage with the slide 300. When the rolling piston 200 and the slide 300 engage, they will collide, generating collision noise and affecting the customer's user experience.

[0025] See Figures 1-3 As shown, in order to solve the above technical problems, this application provides a compression cylinder 100, which includes: The cylinder 100, the rolling piston 200, and the sliding vane 300 are provided. The cylinder 100 has a central hole 110 and a sliding groove 120, which are connected to the central hole 110. The rolling piston 200 is installed in the center, and the sliding vane 300 is disposed in the sliding groove 120 and extends out of the sliding groove 120 to abut against the cylindrical surface 210 of the rolling piston 200.

[0026] Furthermore, an annular groove 220 is provided on the end face of the rolling piston 200. The vertical distance from each part of the annular groove 220 to the cylindrical surface 210 is equal. A mating part 310 is provided on the slide plate 300. The mating part 310 is inserted into the annular groove 220. Through the mating part 310 and the annular groove 220, a tight connection between the rolling piston 200 and the slide plate 300 can be achieved, preventing the slide plate 300 from detaching from the rolling piston 200.

[0027] Because the vertical distance from all points of the annular groove 220 to the cylindrical surface 210 is equal, during the rotation of the rolling piston 200, the mating part 310 will move along the annular groove 220 under the action of the groove wall of the annular groove 220, and the vertical distance between the mating part 310 and the cylindrical surface 210 remains constant. Since the mating part 310 is set on the slide plate 300, the movement of the mating part 310 can synchronously drive the movement of the slide plate 300, thereby making the distance between the slide plate 300 and the cylindrical surface 210 remain constant, so that the contact surface 321 of the slide plate 300 can remain in contact with the cylindrical surface 210.

[0028] Because the cylindrical surface 210 of the rolling piston 200 will also fit against the hole wall of the central hole 110, the rolling piston 200 and the sliding plate 300 can form a high-pressure chamber 111 and a low-pressure chamber 112 separated by the sliding plate 300 in the central hole 110 of the cylinder 100.

[0029] See Figure 1 , Figure 2 as well as Figure 8 As shown, if the rolling piston 200 rolls clockwise, it causes the high-pressure chamber 111 to gradually shrink, thus pressurizing the gas, while the low-pressure chamber 112 gradually increases in size, forming a low-pressure region. The high-pressure chamber 111 is connected to an exhaust port, while the low-pressure chamber 112 is connected to an intake port, enabling low-pressure intake into the low-pressure chamber 112 and high-pressure exhaust from the high-pressure chamber 111.

[0030] Combination Figure 5 When the rolling piston 200 rotates to fit against the side of the cylinder 100 with the slide groove 120, the low-pressure chamber 112 and the high-pressure chamber 111 are connected on the side away from the slide groove 120. At this time, the gas in the low-pressure chamber 112 can be introduced into the high-pressure chamber 111 to replenish the gas in the high-pressure chamber 111 and complete one gas pressurization.

[0031] It is understandable that a one-way valve is installed at the exhaust port to prevent low-pressure gas from being discharged. The pressure exerted on the one-way valve by the high-pressure gas on the side of the exhaust port away from the high-pressure chamber 111 can prevent low-pressure gas from being discharged from the exhaust port.

[0032] Because the linkage between the slide plate 300 and the rolling piston 200 can be achieved through the mating part 310 and the annular groove 220 in this application, the synchronous movement of the slide plate 300 and the rolling piston 200 can be ensured. This eliminates the need for the spring 600 that pushes the slide plate 300 to the center of the cylinder 100, and also eliminates the need for related structures that include the spring 600, thus reducing the size of the compression cylinder 100. Of course, in other implementations, a compression spring 600 can also be provided at the end of the slide plate 300 in this application, providing two methods for pushing the slide plate 300 and improving the reliability of the equipment.

[0033] It should also be noted that, since the annular groove 220 in this application is provided on the end face of the rolling piston 200, rather than on the cylindrical surface 210 of the rolling piston 200, the high pressure chamber 111 and the low pressure chamber 112 will not be connected by the annular groove 220, and the air compression performance of the rolling piston 200 will not be reduced by the annular groove 220.

[0034] See Figure 4 , Figure 6 , Figure 7 as well as Figure 8 As shown, in some implementations, the slide 300 includes a main body 320 housed in the slide groove 120, and the abutting surface 321 is the side of the main body 320 facing the cylindrical surface 210. The slide 300 also includes a guide portion 330 extending out of the slide groove 120. The guide portion 330 extends along the extension of the slide groove 120 to the axial outer side of the rolling piston 200, and the mating portion 310 is disposed on the side of the guide portion 330 facing the rolling piston 200.

[0035] That is, the main body 320 and the mating part 310 are connected by the guide part 330 extending out of the slide groove 120. While ensuring that the abutting surface 321 of the main body 320 can abut against the cylindrical surface 210, the guide part 330 is inserted into the annular groove 220 of the rolling piston 200.

[0036] It is understandable that the main body 320 and the guide part 330 can be integrated and form an L-shaped structure to connect the slide 300 and the annular groove. Of course, the main body 320 and the guide part 330 can also be a separate and detachable structure so that the guide part 330 can be installed on both sides of the main body 320.

[0037] For example Figure 3 as well as Figure 6 As shown, in some implementations, a main body 320 is connected to only one guide part 330. In this case, the main body 320 and the guide part 330 can be designed as an integrated unit or as separate units, and both can be easily installed on the rolling slide 120.

[0038] See Figure 3 ,6 as well as Figure 7 As shown, in some implementations, the cylinder 100 is connected to a first flange 400 and a second flange 700 at its two axial ends respectively. The end face of the rolling piston 200 with an annular groove 220 abuts against the first flange 400, and the other end face of the rolling piston 200 abuts against the second flange 700 to seal the two axial ends of the central hole 110. The first flange 400 is provided with a guide groove 410 that communicates with the slide groove 120, and the guide part 330 is inserted into the guide groove 410.

[0039] In other words, by providing a guide groove 410 structure on the first flange 400, the installation and sliding of the guide part 330 can be satisfied, and the end face of the rolling piston 200 can also abut against the area of ​​the first flange 400 where the guide groove 410 is not provided, thereby reducing gas leakage.

[0040] Of course, the first flange 400 and the second flange 700 in this application are also provided with mounting holes, and the drive shaft 500 is inserted into the two mounting holes to achieve axial positioning.

[0041] See Figure 2 as well as Figure 7 As shown, in some implementations, the guide groove 410 extends to communicate with the mounting hole. During the process of adding lubricant to the mounting hole, the lubricant will flow from the mounting hole to the guide groove 410 and along the guide groove 410 to lubricate the slide plate 300. At the same time, the lubricant can also flow along the guide portion 330 into the annular groove 220, thereby lubricating the mating portion 310. In other words, lubrication of the slide plate 300 and the mating portion 310 can be achieved while lubricating the drive shaft 500, greatly reducing the difficulty of adding lubricant.

[0042] See Figure 2 , Figure 6 as well as Figure 7 As shown, the height of the guide portion 330 is H1, and the depth of the guide groove 410 can be correspondingly set to H1 so that after the guide portion 330 is inserted into the guide groove 410, the guide portion 330 abuts against the first flange 400, and the first flange 400 presses the guide portion 330 against the end face of the rolling piston 200. The figure also shows that the height of the main body portion 320 is H2, and the depth of the slide groove 120 can be correspondingly set to H2 so that when the main body portion 320 extends into the slide groove 120, the guide portion 330 can completely extend out of the slide groove 120.

[0043] In some implementations, the annular groove 220 stores lubricant. By providing lubricant, the friction between the mating part 310 and the sidewall of the annular groove 220 can be reduced, thereby making the movement of the rolling piston 200 smoother. The lubricant in the annular groove 220 can be pre-added or replenished by adding it to the flange mounting hole.

[0044] Because both ends of the rolling piston 200 abut against the flange, and the annular groove 220 is relatively closed, the lubricant can be well retained.

[0045] See Figure 4 As shown, in some implementations, the mating part 310 is a ball embedded in the slide 300, the portion of the mating part 310 protruding from the slide 300 is inserted into the annular groove 220, and the mating part 310 can roll relative to the slide 300.

[0046] In other words, part of the ball is embedded in the slide 300, and the other part is inserted into the annular groove 220, using the ball structure to connect the slide 300 and the rolling piston 200. To prevent the ball from detaching from the slide 300, an anti-detachment structure can be installed on the guide 330. During installation, the ball is first installed in the hemispherical groove of the guide 330, and then the anti-detachment structure with a through hole is installed on the guide 330, allowing the ball to extend out through the through hole of the anti-detachment structure. Alternatively, the anti-detachment structure can be omitted, and the cross-section of the annular groove 220 can be set as a semicircle with a radius equal to that of the ball, and a hemispherical groove with a radius equal to that of the ball can be set on the guide 330. One of the guide 330 and the annular groove 220 supports the ball, while the other is fastened to the outside of the ball, thus restricting the ball.

[0047] Compared to fixing the mating part 310 on the slide plate 300 and using a ball bearing to achieve linkage between the slide plate 300 and the rolling piston 200, sliding friction can be adjusted to rolling friction, reducing energy loss and wear on the annular groove 220, and improving the service life of the compression cylinder 100.

[0048] In some implementations, the mating part 310 is a protruding structure integrated with the slide 300, which is relatively simple to install compared to a ball bearing structure. The mating part 310 can be set as a cylindrical protrusion, a spherical protrusion, or a conical protrusion, which avoids the wear of the annular groove 220 by sharp edges compared to square or prismatic protrusions.

[0049] See Figure 2 , Figure 8 as well as Figure 9 As shown, in some implementations, the cylindrical surface 210 of the rolling piston 200 is a cylindrical surface 210, and the annular groove 220 forms an annular structure around the central axis of the cylindrical surface 210, and the central axis of the cylindrical surface 210 coincides with the central axis of the annular groove 220.

[0050] By aligning the central axis of the cylindrical surface 210 with the central axis of the annular groove 220, the vertical distance from each point of the annular groove 220 to the axial surface is equal.

[0051] It is understandable that the cylindrical surface 210 of the rolling piston 200 can also be set as an elliptical cylindrical surface 210, which can also achieve rolling within the central hole 110 through the rolling of the rolling piston 200. Corresponding to the cylindrical surface 210 of the elliptical cylindrical surface 210, the extension trajectory of the annular groove 220 can be set as an ellipse similar to the cylindrical surface 210, and the major axis and minor axis of the ellipse formed by the annular groove 220 can be aligned with the major axis and minor axis of the elliptical section of the cylindrical surface 210, respectively.

[0052] See Figure 2 , Figure 8 as well as Figure 9 As shown, in some implementations, the groove 120 extends radially along the central hole 110. To ensure that the abutment surface 321 of the slide 300 remains in contact with the cylindrical surface 210 of the rolling piston 200, the distance L between the abutment surface 321 and the center of the mating portion 310 is set equal to the distance a between the annular groove 220 and the cylindrical surface 210. This ensures that when the rolling piston 200 is at its furthest or closest distance from the groove 120, the extension direction of the slide 300 is radial to the rolling piston 200. At this time, the abutment surface 321 abuts precisely against the cylindrical surface 210. Alternatively, L can be set slightly less than a, allowing the abutment surface 321 to fit tightly against the cylindrical surface 210.

[0053] When the rolling piston 200 moves to other positions, the extension direction of the slide 300 will be at an angle to the radial direction of the rolling piston 200. At this time, the distance d between the mating part 310 and the abutment surface 321 will be greater than the distance a between the annular groove 220 and the cylindrical surface 210. That is, there will be a certain amount of compression deformation at the abutment surface 321 of the main body 320.

[0054] It is understandable that in order for the mating part 310 provided on the radially extending slide 300 to be connected with the annular groove 220, it is necessary to make r3 + r2 > r1, so that the extension direction of the slide groove 120 can intersect with the trajectory of the annular groove 220, where r1 is the radius of the central hole 110, r2 is the radius of the cylindrical surface 210, and r3 is the radius of the extension trajectory of the annular groove 220. Obviously, r1 > r2 > r3.

[0055] Combination Figure 3 , Figure 8 as well as Figure 9 It can be seen that when in the state Figure 8In states ② and ④, the distance between the extending direction of the slider 300 and the central axis of the rolling piston 200 reaches its maximum value, and the angle α between the extending direction of the slider 300 and the radial direction of the rolling piston 200 reaches its maximum. That is, the distance d between the mating part 310 and the abutment surface 321 reaches its maximum value, and the engagement... Figure 9 It can be seen that α satisfies the following formula at this time.

[0056]

[0057] Right now

[0058] Where b is the actual distance between the mating part 310 and the contact surface 321 at this time. As can be seen from the attached figure, 0 < r2 - r3 < b < r2.

[0059] Simplifying the above equation, we get:

[0060] The table below lists several sets of r1, r2, and r3 values. Substituting these values ​​into the table yields the corresponding b (maximum value of d), a (minimum value of d), and c (range of d, i.e., ba). As shown in the table, it can be seen that by reasonably controlling r1, r2, and r3, the range c of d can be kept within a very small range. This allows the elastic deformation of the slider 300 to adapt to changes in the length of d, ensuring that the slider 300 always remains in contact with the cylindrical surface 210.

[0061]

[0062] When r1 and r2 are determined, the included angle α is a constant. In this case, the closer r3 is to r2, the smaller the calculated value of c. That is to say, when designing the annular groove 220, the annular groove 220 can be made as close as possible to the cylindrical surface 210 as possible, within the limits of processing capability and the strength of each component, in order to reduce the value of c, thereby reducing the deformation of the slider 300 and making the slider 300 fit the cylindrical surface 210 better.

[0063] See Figures 2 to 4 As shown, in some implementations, the rolling piston 200 is connected to a drive shaft 500. The rotation axis of the drive shaft 500 is parallel to and spaced from the central axis of the rolling piston 200, causing the rolling piston 200 to perform eccentric motion within the central hole 110. By driving the rolling piston 200 to perform eccentric motion, a gas storage cavity structure can be formed within the central hole 110, and the cylindrical surface 210 of the rolling piston 200 can remain in contact with the hole wall of the central hole 110, thereby adjusting the volume of the high-pressure chamber 111 and the low-pressure chamber 112 during the rotation of the rolling piston 200.

[0064] See Figures 2-5As shown, in some implementations, the drive shaft 500 has an eccentric portion 510 that is eccentric to its rotation axis, and the rolling piston 200 is a sleeve structure fitted over the eccentric portion 510. Because the rolling piston 200 is fitted over the eccentric portion 510, rather than being integrated with it, the rolling piston 200 can rotate freely relative to the eccentric portion 510, thereby reducing the frictional force on the eccentric portion 510 and reducing the load on the compression cylinder 100. Of course, in some cases, the drive shaft 500 and the rolling piston 200 can also be integrated.

[0065] See Figure 2 As shown, in some implementations, the cylinder 100 is further provided with an air inlet and an air outlet, both of which are connected to the central hole 110, and are located on opposite sides of the slide groove 120. After the slide plate 300 is installed in the slide groove 120 and connected to the rolling piston 200, the slide plate 300 in the slide groove 120 can separate the air inlet and the air outlet, forming a high-pressure chamber 111 and a low-pressure chamber 112 that are not connected to each other.

[0066] It is understandable that although the above examples are mainly for compressed gases, they can also be applied to the compression of liquids.

[0067] The present invention also provides a compressor, which includes any of the compression cylinders 100 described above. By engaging the mating part 310 with the annular groove 220, the sliding vane 300 can be prevented from disengaging from the rolling piston 200, thereby improving the stability during the compression process and reducing the noise generated by the collision between the sliding vane 300 and the rolling piston 200 during the compression process.

[0068] The present invention also provides a refrigeration device including the compressor described above, which can achieve stable gas compression, improve compression efficiency, and reduce noise during compression, thus providing customers with a better user experience.

[0069] Although the invention has been described with reference to preferred embodiments, various modifications can be made and components can be replaced with equivalents without departing from the scope of the invention. In particular, the technical features mentioned in the various embodiments can be combined in any manner as long as there is no structural conflict. The invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A compression cylinder, characterized in that, It includes: A cylinder, which has a sliding groove; A rolling piston, located within the central bore of the cylinder, wherein a portion of the cylindrical surface of the rolling piston is in contact with the bore wall of the central bore, and the rolling piston is configured to rotate within the central bore; and A sliding plate is slidably disposed in the sliding groove, and the sliding plate, together with the rolling piston, can divide the space between the cylinder and the rolling piston into a high-pressure chamber and a low-pressure chamber; The end face of the rolling piston is provided with an annular groove, and the vertical distance from each part of the annular groove to the cylindrical surface is equal. The slide is provided with a mating part, which is inserted into the annular groove and can slide or roll along the extension direction of the annular groove, so that the contact surface of the slide is always in contact with the cylindrical surface.

2. The compression cylinder according to claim 1, characterized in that, The slide includes a main body portion housed in the slide groove, the abutting surface being the side of the main body portion facing the cylindrical surface, the slide also includes a guide portion extending out of the slide groove, the guide portion extending along the extension direction of the slide groove to the axial outer side of the rolling piston, and the mating portion being disposed on the side of the guide portion facing the rolling piston.

3. The compression cylinder according to claim 2, characterized in that, The cylinder is connected to a first flange and a second flange at its two axial ends respectively. The end face of the rolling piston with the annular groove abuts against the first flange, and the other end face of the rolling piston abuts against the second flange to seal the two axial ends of the central hole. The first flange is provided with a guide groove that communicates with the slide groove, and the guide part is inserted into the guide groove.

4. The compression cylinder according to claim 1, characterized in that, The annular groove stores lubricating fluid.

5. The compression cylinder according to any one of claims 1-4, characterized in that, The mating part is a rolling ball embedded in the slide plate, and the portion of the mating part protruding from the slide plate is inserted into the annular groove, wherein the mating part is capable of rolling relative to the slide plate.

6. The compression cylinder according to any one of claims 1-4, characterized in that, The mating part is a protruding structure integrated with the slide plate.

7. The compression cylinder according to any one of claims 1-4, characterized in that, The cylindrical surface of the rolling piston is cylindrical, and the annular groove surrounds the central axis of the cylindrical surface to form an annular structure, and the central axis of the cylindrical surface coincides with the central axis of the annular groove.

8. The compression cylinder according to claim 7, characterized in that, The groove extends radially along the central hole, the radius of the central hole is r1, the radius of the cylindrical surface is r2, the radius of the annular track of the annular groove is r3, and r1, r2, and r3 satisfy r3 + r2 > r1 > r2 > r3.

9. The compression cylinder according to any one of claims 1-4, characterized in that, The rolling piston is connected to a drive shaft, and the rotation axis of the drive shaft is parallel to and spaced apart from the central axis of the rolling piston, so that the rolling piston rotates eccentrically within the central hole.

10. The compression cylinder according to claim 9, characterized in that, The drive shaft has an eccentric portion that is off-center relative to its axis of rotation, and the rolling piston is a sleeve structure fitted outside the eccentric portion.

11. The compression cylinder according to any one of claims 1-4, characterized in that, The cylinder is also provided with an air inlet and an air outlet, both of which are connected to the central hole and are located on opposite sides of the slide groove.

12. A compressor, characterized in that, It includes, The compression cylinder according to any one of claims 1-11.

13. A refrigeration device, characterized in that, It includes the compressor according to claim 12.

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