Sliding vane and roller cooperation structure, rotary compressor and air conditioner

Abstract

The present disclosure relates to a sliding vane and roller matching structure, a rotary compressor and an air conditioner. The sliding vane and roller matching structure comprises a roller, a sliding vane and a roller shaft structure. The roller is sleeved on an eccentric section of a rotor, is configured to perform a revolution motion around the rotor with the eccentric section, and is configured to perform a small driven rotation motion. The roller is used to push refrigerant for compression. The sliding vane has a first end face at one end close to the roller. Along the width direction of the sliding vane, the first end face has a roller shaft mounting groove and a blocking part arranged on both sides of the roller shaft mounting groove. The roller shaft structure is mounted in the roller shaft mounting groove. The roller shaft mounting groove comprises a first plane, and the blocking part comprises a second plane. A gap is left between the first plane and the second plane. The roller shaft structure is in rolling contact with the outer circumferential surface of the roller in the gap area, and the blocking part is in close contact with the outer circumferential surface of the roller through the second plane.

Description

Technical Field

[0001] This disclosure relates to the field of rotary compressors with vanes and rollers, and more particularly to a vane and roller mating structure, a rotary compressor, and an air conditioner. Background Technology

[0002] In refrigeration and heat pump applications, rotary compressors are core power components due to their compact structure and stable operation. The sliding vane and roller coupling structure is the key unit for achieving gas compression. Currently, in mainstream rotary compressors, the sliding vane and roller use line contact, with the overall movement resembling a cam: as the roller rotates, the vane reciprocates vertically, separating the compression chamber through contact to complete the intake, compression, and exhaust cycles. However, this structure has significant drawbacks: firstly, the vane easily separates from the roller during rotation, directly leading to a decrease in compressor power and increased operating noise; secondly, the line contact characteristic results in insufficient sealing, especially prone to leakage at low frequencies, and the sliding friction generated by the line contact at high speeds causes heat generation and power loss, severely affecting compressor efficiency and lifespan.

[0003] To address the aforementioned issues, existing technologies mostly improve the situation through localized methods such as optimizing materials and adjusting spring stiffness, failing to resolve the fundamental contradictions at the level of contact form and structural design. A few solutions involving structural innovation suffer from high complexity and poor compatibility with existing cylinder blocks, hindering large-scale application. Therefore, there is an urgent need for a vane and roller structure that can simultaneously solve the problems of separation, sealing, and frictional loss, breaking through the bottlenecks of traditional designs and improving the overall performance of rotary compressors. Utility Model Content

[0004] This disclosure provides a vane and roller mating structure, a rotor compressor, and an air conditioner to solve the technical problems of separation, sealing, and frictional loss in the vane and roller structures of the prior art.

[0005] The rotor compressor vane and roller mating structure provided in this disclosure includes: a roller, a vane, and a roller structure; the roller is sleeved on an eccentric section of the rotor, the roller is configured to follow the eccentric section in a revolution around the rotor, and the roller is configured to perform a slight self-rotation driven motion, the roller being used to push the refrigerant to compress; one end of the vane near the roller is a first end face, and along the width direction of the vane, the first end face has a roller mounting groove and blocking portions disposed on both sides of the roller mounting groove; the roller structure is mounted in the roller mounting groove, the roller mounting groove includes a first plane, the blocking portion includes a second plane, a gap is left between the first plane and the second plane, the roller structure rolls in the region of the gap with the outer circumferential surface of the roller, and the blocking portion is fitted to the outer circumferential surface of the roller through the second plane.

[0006] Wherein, the portion of the second plane that contacts the outer circumferential surface of the roller is arc-shaped, and the curvature matches the outer circumferential surface of the roller; the contact surface between the first plane and the roller structure is a line contact or a point contact.

[0007] Roller mounting posts are provided in the roller mounting groove, and one roller mounting post is installed at each end of one roller structure.

[0008] Along the length of the slide, the first end face is provided with anti-leakage groove structures on both sides of the roller mounting groove. The anti-leakage groove structure is a continuously curved concave structure, and the opening direction of the anti-leakage groove structure faces the roller.

[0009] The roller has a continuous protrusion at the edge of its outer circumference. This protrusion engages and seals with the leak-proof groove structure of the sliding plate, enhancing the vertical seal. Wherein, along the length direction of the slide, the continuously curved recessed structure of the anti-leakage groove is constructed as at least two arc-shaped recessed structures; correspondingly, the continuous protrusion is constructed as at least two arc-shaped protrusions.

[0010] The side of the blocking part that contacts the outer circumferential surface of the roller is a sealing arc segment, and the curvature of the sealing arc segment is adapted to the curvature of the outer circumferential surface of the roller.

[0011] The vane has a stepped structure on the side near the roller. The lower part of the stepped structure forms the blocking part. There is an open groove structure between the upper and lower parts of the stepped structure. An elastic blocking member is provided in the open groove structure. The elastic blocking member is located on the exhaust chamber side of the rotor compressor and is used to adjust the downward pressure of the vane on the roller.

[0012] The elastic blocking member is configured to directly bear the vertically downward flow field resistance and to at least partially export the flow field resistance to the sliding plate.

[0013] The elastic blocking member includes an elastic element and a guide plate. One end of the guide plate is rotatably connected to the edge of the upper structure of the stepped structure, and the other end of the guide plate is movable within the open groove structure. The elastic element is connected between the upper structure and the guide plate.

[0014] The lower structure has a blocking edge on its outer edge, which is used to prevent the guide plate from moving out of the open groove structure.

[0015] The guide plate is configured to be angled in its initial state, one end of the elastic element is connected to the outer side of the upper structure, and the other end of the elastic element is connected to the large surface area of ​​the guide plate.

[0016] The elastic element has an initial spring force and can adjust its expansion and contraction amount according to the pressure changes inside the rotor compressor to adapt to the flow field resistance.

[0017] This disclosure also provides a rotary compressor, including the aforementioned vane and roller mating structure.

[0018] This disclosure also provides an air conditioner, including the aforementioned rotary compressor.

[0019] The technical solutions provided in this disclosure have the following advantages compared with the prior art: The vane and roller mating structure, rotor compressor, and air conditioner provided in this disclosure transform the line contact sliding friction between the vane and roller into rolling friction through the setting of the roller structure and roller mounting groove. Combined with the motion characteristics of the roller's revolution and slight rotation, the frictional resistance during the mating process is significantly reduced. Especially when the compressor is running at high speed, it can significantly reduce frictional heat generation and power loss, while reducing the wear rate of the contact surface and extending the service life of the core components. At the same time, the blocking parts set on both sides of the roller mounting groove along the width direction of the vane have their second planes in contact with the outer circumferential surface of the roller. With the roller structure rolling with the roller in the gap area, a lateral sealing barrier can be formed on both sides of the roller structure, effectively blocking the refrigerant leakage channel and solving the sealing leakage problem in the prior art during low-frequency operation. Furthermore, the limiting effect of the roller mounting groove on the roller structure can reduce the separation of the vane and roller caused by gas pressure fluctuations and motion inertia, improve the operating stability of the compressor, and avoid the power reduction and noise caused by separation.

[0020] Furthermore, the gap between the first plane of the roller mounting groove and the second plane of the blocking part not only provides the roller structure with the necessary space for rolling, but also prevents excessive leakage by precisely controlling the gap size. At the same time, the fitting of the blocking part is highly compatible with the motion characteristics of the roller. Without interfering with the core function of the roller driving the refrigerant compression, the compressor's intake, compression, and exhaust cycles are ensured to operate efficiently and stably through the dual effects of friction optimization and sealing enhancement, thereby further improving the overall energy efficiency and operational reliability of the compressor. Attached Figure Description

[0021] The accompanying drawings, which are incorporated in and form a part of this specification, illustrate embodiments consistent with this disclosure and, together with the description, serve to explain the principles of this disclosure.

[0022] To more clearly illustrate the technical solutions in the embodiments of this disclosure or the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, those skilled in the art can obtain other drawings based on these drawings without creative effort.

[0023] One or more embodiments are illustrated by way of example with reference numerals in the accompanying drawings. These illustrations do not constitute a limitation on the embodiments. Elements with the same reference numerals in the drawings are denoted as similar elements. Unless otherwise stated, the figures in the drawings are not to be limited by scale.

[0024] Figure 1 This is a schematic diagram of the sliding vane and roller mating structure, the installation structure between the cylinder and the rotor provided in the embodiments of this disclosure; Figure 2 This is an enlarged structural diagram of the mating surface between the slide and the roller provided in an embodiment of the present disclosure. Figure 1 ; Figure 3 for Figure 2 Enlarged structural schematic diagram of a medium-elasticity retaining member; Figure 4 This is an enlarged structural schematic diagram of the mating surface between the roller and the cylinder body, provided in an embodiment of this disclosure. Figure 5 This is an enlarged structural diagram of the mating surface between the slide and the roller provided in an embodiment of the present disclosure. Figure 2 (Sectional view); Figure 6 This is an enlarged structural diagram of the area outside the mating surface between the slide and the roller provided in an embodiment of this disclosure; Figure 7 An enlarged structural schematic diagram of the inner peripheral surface of the cylinder provided in an embodiment of this disclosure; Figure 8This is a schematic diagram of the structure of the bottom end of the slider provided in an embodiment of this disclosure.

[0025] Explanation of reference numerals in the attached figures: 1. Roller; 11. Continuous protrusion; 2. Rotor; 3. Sliding vane; 31. First end face; 311. Roller mounting groove; 311A. First plane; 312. Blocking part; 312A. Second plane; 312B. Sealing arc segment; 32. Stepped structure; 321. Upper structure; 322. Lower structure; 3221. Blocking edge; 323. Open groove structure; 4. Roller structure; 5. Roller mounting column; 6. Leak-proof groove structure; 7. Elastic blocking member; 71. Elastic element; 72. Guide plate; 8. Cylinder body. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this disclosure. Based on the embodiments of this disclosure, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this disclosure.

[0027] The following disclosure provides numerous different embodiments or examples for implementing various structures of this disclosure. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of this disclosure. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed.

[0028] For ease of description, spatial relative terms may be used in this text to describe the relative position or movement of one element or feature relative to another element or feature, as shown in the figure. These relative terms include, for example, "inside," "outside," "middle," "outer," "below," "below," "above," "front," "back," etc. Such spatial relative terms are intended to include different orientations of the device in use or operation, other than those depicted in the figure. For example, if the device in the figure undergoes a positional flip, orientation change, or change of motion, these directional indications will change accordingly. For instance, an element described as "below other elements or features" or "below other elements or features" will subsequently be oriented "above other elements or features" or "above other elements or features." Therefore, the example term "below" can include both upper and lower orientations. The device may be otherwise oriented (rotated 90 degrees or in other directions), and the spatial relative descriptions used in this text have been explained accordingly.

[0029] The vane and roller mating structure disclosed in this embodiment is applied to a rotary compressor. It addresses the friction between the roller and vane by proposing a vane and roller structure that reduces friction while increasing the sealing performance. Furthermore, protruding portions are added to both sides of the vane to increase the pressure on it, and a spring structure is provided on the exhaust chamber side for more accurate control of the increased downward pressure. This can, to some extent, reduce the separation between the roller and vane at low frequencies.

[0030] In a rotary compressor, the core assembly relationship of the rotor, rollers, and vanes is as follows: The eccentric section of the rotor passes through the central hole of the roller. The rollers and the eccentric section are interference-fitted or clearance-fitted to ensure synchronous movement. The rollers can revolve around the rotor axis with the eccentric section. At the same time, due to the rolling friction with the vanes, they generate a small self-rotating driven motion, which in turn drives the refrigerant in the compressor to complete the compression process.

[0031] refer to Figures 1-8This disclosure provides a sliding vane 3 and roller 1 mating structure, including: roller 1, sliding vane 3, and roller structure 4; roller 1 is sleeved on the eccentric section of rotor 2, and roller 1 is configured to follow the eccentric section in a revolution around rotor 2, and roller 1 is configured to perform a small self-rotation driven motion, roller 1 is used to push refrigerant compression; the end of sliding vane 3 near roller 1 is a first end face 31, and along the width direction of sliding vane 3, the first end face 31 has roller mounting... The roller mounting groove 311 and the blocking parts 312 are provided on both sides of the roller mounting groove 311; the roller structure 4 is mounted in the roller mounting groove 311. The roller mounting groove 311 includes a first plane 311A ​​and the blocking part 312 includes a second plane 312A. There is a gap between the first plane 311A ​​and the second plane 312A. The roller structure 4 rolls with the outer circumferential surface of the roller 1 in the gap area. The blocking part 312 is fitted with the outer circumferential surface of the roller 1 through the second plane 312A.

[0032] For example, micro-rotation refers to the movement of roller 1 at a very low speed while it revolves around the compressor main shaft (or eccentric shaft). The rotation amplitude is small, the speed is much lower than the revolution speed, and the movement is generated by passive following.

[0033] It should be noted that the rotation of roller 1 is not actively driven by a dedicated drive structure, but passively triggered by the frictional force generated from its contact with the cylinder inner wall, sliding vane 3, and other components. The "micro" rotational speed is mainly reflected in two aspects: firstly, the rotational speed is much lower than the revolution speed, which is typically tens or even hundreds of times faster; secondly, the rotation angle is extremely small per unit time, preventing rapid rotation. Furthermore, this micro-rotation is primarily used to coordinate with compression, reducing frictional wear between roller 1 and the contacting components, avoiding excessive localized wear that could affect sealing performance, and thus ensuring the stability and efficiency of the refrigerant compression process.

[0034] For example, the vane 3 is arranged along the radial groove of the compressor cylinder 8 of the rotor 2, and can reciprocate linearly along the groove; the end near the roller 1 is the first end face 31, and along the width direction of the vane 3, that is, perpendicular to the reciprocating motion direction of the vane 3, the first end face 31 is integrally formed with a roller mounting groove 311 and two symmetrically distributed blocking parts 312, and the roller mounting groove 311 is located between the two blocking parts 312; the roller structure 4 is fixed by the mounting structure in the roller mounting groove 311, such as the roller mounting column 5 mentioned later, and only in the gap area formed by the first plane 311A ​​of the roller mounting groove 311 and the second plane 312A of the blocking part 312, it contacts the outer circumferential surface of the roller 1 and maintains rolling fit; the second plane 312A of the blocking part 312 is always in contact with the outer circumferential surface of the roller 1 to form a lateral seal.

[0035] For example, the roller 1 has a cylindrical structure, and the diameter of its central hole is adapted to the outer diameter of the eccentric section of the rotor 2 to ensure the synchronization of the revolution motion; the outer circumferential surface can be precision ground, and the surface roughness is controlled below Ra0.8 to reduce the rolling friction resistance with the roller structure 4; at the same time, according to the sealing requirements, the edge of the outer circumferential surface of the roller 1 can be integrally formed with a continuous protrusion 11, such as along the axial direction of the roller 1, that is, the length direction of the slide 3, for sealing with the anti-leakage groove structure 6 of the slide 3.

[0036] For example, the slider 3 is a long strip structure, and the cross section along the length direction can be set as a stepped shape according to the functional requirements, that is, parallel to the reciprocating motion direction of the slider 3. The roller mounting groove 311 of the first end face 31 is a rectangular groove, and the bottom of the groove is the first plane 311A. The contact surface between the plane and the roller structure 4 can be set as line contact or point contact to ensure that the roller structure 4 only rolls stably in the groove and does not undergo lateral displacement.

[0037] For example, the first plane 311A ​​is a plane, the roller structure 4 is cylindrical, and the two are in line contact.

[0038] For example, the first plane 311A ​​is an arc-shaped concave surface, the roller structure 4 is spherical, and the two are in point contact.

[0039] For example, the blocking part 312 is located on both sides of the roller mounting groove 311. The side facing the roller 1 is the second plane 312A, and the part that fits with the outer circumferential surface of the roller 1 is set as an arc shape. The arc is completely matched with the arc of the outer circumferential surface of the roller 1. For example, if the radius of the roller 1 is R, the radius of the arc is also R, to ensure tight fit. If it is necessary to strengthen the seal, the side of the blocking part 312 that contacts the roller 1 can be further set as a sealing arc segment 312B. The axial length of the arc segment covers the axial length of the roller 1 to prevent refrigerant from leaking axially from the roller 1.

[0040] For example, along the length of the slide plate 3, the first end face 31 can also be provided with a leak-proof groove structure 6 on both sides of the roller mounting groove 311. This structure is a continuously curved recessed structure with the opening facing the roller 1. Specifically, it can be set as at least two arc-shaped recessed structures, such as two semi-circular arc recesses, with the center of the circle collinear with the center of the roller 1. Correspondingly, the continuous protrusion 11 on the outer circumference of the roller 1 is set as at least two arc-shaped protrusion structures. The arc-shaped recesses and arc-shaped protrusions are perfectly matched in terms of curvature and size. After fitting together, they form a labyrinth seal, further blocking the refrigerant leakage channel.

[0041] For example, the side of the slide plate 3 near the roller 1 can be configured as a stepped structure 32. The lower structure 322 of the stepped structure 32 forms the aforementioned blocking part 312, and an open groove structure 323 is left between the upper structure 321 and the lower structure 322. An elastic blocking member 7 is installed in the open groove structure 323. This member is located on the exhaust chamber side of the rotor 2 compressor and is used to adjust the downward pressure of the slide plate 3 on the roller 1. The elastic blocking member 7 includes an elastic element 71 and a guide plate 72. One end of the guide plate 72 is rotatably connected to the edge of the upper structure 321 of the stepped structure 32 via a hinge, and the other end can move along the length direction of the slide plate 3 in the open groove structure 323. One end of the elastic element 71 is fixedly connected to the outer side of the upper structure 321, and the other end is connected to the large surface area of ​​the guide plate 72 (such as the middle position of the guide plate 72). The elastic element 71 has a preset initial spring force in the initial state, and can adjust the amount of expansion and contraction according to the pressure change in the compressor, thereby adapting to the flow field resistance.

[0042] For example, to prevent the guide plate 72 from coming out of the open groove structure 323, the outer edge of the lower structure 322 may be integrally formed with a blocking edge 3221, such as a protruding edge extending along the moving direction of the guide plate 72. The height of the blocking edge 3221 is higher than the thickness of the guide plate 72, ensuring that the guide plate 72 only moves within the groove and does not deviate from the preset trajectory.

[0043] For example, the roller structure 4 can be made of cylindrical needle rollers or spherical balls, and the material is selected as bearing steel or ceramic material. After quenching treatment, the hardness reaches HRC60 or above to improve wear resistance. If it is a cylindrical roller, its axial length is adapted to the width of the roller mounting groove 311, and both ends are respectively fitted onto the roller mounting posts 5 in the roller mounting groove 311. One roller structure 4 corresponds to two roller mounting posts 5. The roller mounting posts 5 are perpendicular to the first plane 311A ​​and are integrally formed with the slide plate 3 to ensure that the roller structure 4 can rotate freely around the roller mounting posts 5 without jamming.

[0044] In this way, by setting the roller structure 4 and the roller mounting groove 311, the line contact sliding friction between the vane 3 and the roller 1 is converted into rolling friction. Combined with the motion characteristics of the roller 1's revolution and slight rotation, the frictional resistance during the cooperation process is greatly reduced. Especially when the compressor is running at high speed, it can significantly reduce frictional heat generation and power loss, while reducing the wear rate of the contact surface and extending the service life of the core components. At the same time, the blocking parts 312 set on both sides of the roller mounting groove 311 along the width direction of the vane 3 have their second plane 312A in contact with the outer circumferential surface of the roller 1. With the rolling cooperation of the roller structure 4 and the roller 1 in the gap area, a lateral sealing barrier can be formed on both sides of the roller structure 4, effectively blocking the refrigerant leakage channel and solving the sealing leakage problem in the prior art during low-frequency operation. Moreover, the limiting effect of the roller mounting groove 311 on the roller structure 4 can reduce the separation of the vane 3 and the roller 1 caused by gas pressure fluctuations and motion inertia, improve the operating stability of the compressor, and avoid the power drop and noise caused by separation.

[0045] Furthermore, the gap between the first plane 311A ​​of the roller mounting groove 311 and the second plane 312A of the blocking part 312 provides the roller structure 4 with the necessary space for rolling, and can also prevent excessive leakage by precisely controlling the gap size. At the same time, the fitting of the blocking part 312 is highly compatible with the motion characteristics of the roller 1. Without interfering with the core function of the roller 1 in driving the refrigerant compression, the compressor's intake, compression, and exhaust cycles are ensured to operate efficiently and stably through the dual effects of friction optimization and sealing enhancement, thereby further improving the overall energy efficiency and operational reliability of the compressor.

[0046] Considering the sealing scheme between the blocking part 312 and the outer circumferential surface of the roller 1, in this embodiment of the present disclosure, the part of the second plane 312A that is in contact with the outer circumferential surface of the roller 1 is arc-shaped, and the curvature matches the outer circumferential surface of the roller 1; the contact surface between the first plane 311A ​​and the roller structure 4 is a line contact or a point contact.

[0047] Thus, the part of the second plane 312A that fits against the outer circumference of the roller 1 is set as an arc, with the center of the arc coinciding with the center of the roller 1, and the axial length of the arc being consistent with the axial length of the roller 1, ensuring that there is no gap between the mating surfaces; when the contact surface between the first plane 311A ​​and the roller structure 4 is in line contact, the first plane 311A ​​is a flat rectangular plane, and the roller structure 4 is cylindrical, with the cylindrical surface tangent to the first plane 311A ​​to form a line contact; if it is in point contact, the first plane 311A ​​is set as an arc-shaped concave surface, that is, the radius of the concave surface is slightly larger than the radius of the roller structure 4, and the roller structure 4 is spherical, with the spherical surface contacting the concave surface to form a point contact. Both contact methods can reduce the friction between the roller structure 4 and the mounting groove, ensuring smooth rolling.

[0048] Considering the specific installation scheme of the roller structure 4, in this embodiment of the disclosure, a roller mounting post 5 is provided in the roller mounting groove 311, and a roller mounting post 5 is installed at each end of a roller structure 4.

[0049] Thus, within the roller mounting groove 311, along the direction perpendicular to the reciprocating motion of the slide 3, which is also the axial direction of the roller structure 4, two parallel roller mounting posts 5 are integrally formed. The diameter of the mounting posts is adapted to the diameter of the center holes at both ends of the roller structure 4, which can be a clearance fit. The center holes at both ends of the roller structure 4 are respectively fitted onto the two mounting posts, allowing for flexible rotation around the mounting posts. Furthermore, the height of the mounting posts is lower than the depth of the roller mounting groove 311, ensuring that the roller structure 4 only contacts the roller 1 within the groove and does not interfere with the groove opening.

[0050] Considering the specific sealing scheme between the slide plate 3 and the roller 1, in this embodiment of the present disclosure, along the length direction of the slide plate 3, the first end face 31 is provided with a leak-proof groove structure 6 on both sides of the roller mounting groove 311. The leak-proof groove structure 6 is constructed as a continuously curved concave structure, and the opening direction of the leak-proof groove structure 6 faces the roller 1.

[0051] In this way, the anti-leakage groove structure 6 can form a recessed and outer circumferential sealing interface with the outer circumference of the roller 1. The continuously curved groove shape can extend the leakage path of the refrigerant. Compared with the existing line contact seal, it significantly increases the sealing contact area and sealing length. Especially when the compressor is running at low frequency, it can effectively prevent refrigerant liquid from leaking from the gap between the sliding vane 3 and the roller 1, avoiding the reduction in compression efficiency and component corrosion caused by leakage. At the same time, the anti-leakage groove structure 6 is set on both sides of the roller mounting groove 311 along the length direction of the sliding vane 3. It can form a two-sided sealing protection for the roller mating area without interfering with the rolling fit between the roller structure 4 and the roller 1, preventing refrigerant from penetrating from the lateral gap of the roller mounting groove 311. At the same time, the continuously curved groove structure can adapt to the movement trajectory of the roller 1 during its revolution, always maintaining a close fit with the outer circumferential surface of the roller 1, ensuring the continuity and stability of the sealing effect, and further ensuring the sealing reliability of the compressor under different operating conditions.

[0052] In addition, the anti-leakage groove structure 6 can be directly integrally formed with the first end face 31 of the slide plate 3 without the need for additional sealing components. This simplifies the structure and reduces assembly complexity and cost. The recessed structure can store a small amount of lubricating oil, which forms an oil film when the slide plate 3 and the roller 1 move relative to each other. This not only enhances the sealing effect but also helps to reduce the rolling friction resistance of the roller structure 4, indirectly reducing power loss.

[0053] Considering the specific sealing scheme between the roller 1 and the anti-leakage groove, in this embodiment of the present disclosure, a continuous protrusion 11 is provided at the edge of the outer circumferential surface of the roller 1. The continuous protrusion 11 is used to fit and match the anti-leakage groove structure 6 of the slide plate 3 for sealing.

[0054] In this way, by setting a continuous protrusion 11 at the edge of the outer circumference of the roller 1, which fits and seals with the anti-leakage groove structure 6 of the vane 3, the leakage problem of the existing rotor 2 compressor vane 3 and roller 1 can be specifically solved, significantly improving the sealing reliability. The fit between the continuous protrusion 11 and the anti-leakage groove structure 6 forms a complementary sealing form of protrusion and depression. Compared with the traditional line contact seal, it greatly increases the length of the refrigerant leakage path. Especially under the conditions of low-frequency operation of the compressor and discontinuous oil film, it can effectively block the refrigerant liquid from leaking from the gap between the vane 3 and roller 1, avoid the decrease in compression efficiency caused by leakage, and prevent component corrosion caused by leakage, thus extending the service life of core components.

[0055] Furthermore, the matching seal between the continuous protrusion 11 and the anti-leakage groove structure 6 can adapt to the motion characteristics of the revolution and slight rotation of the roller 1. During the movement of the roller 1 with the eccentric section of the rotor 2, the protrusion always remains in an engaged state with the groove structure, and the seal will not fail due to changes in the movement trajectory of the roller 1. Moreover, this sealing structure does not require additional complex sealing components. High-efficiency sealing can be achieved simply by matching the structure of the roller 1 and the sliding vane 3. While simplifying the assembly process and controlling costs, it can also form a matching effect with the roller structure 4 on the sliding vane 3. This does not interfere with the function of the roller structure 4 in converting sliding friction into rolling friction to reduce losses, and further ensures the overall operating efficiency of the compressor through reliable sealing.

[0056] Considering the specific construction scheme of the anti-leakage groove and the continuous protrusion 11, in this embodiment of the disclosure, along the length direction of the slide plate 3, the continuous curved recessed structure of the anti-leakage groove is constructed as at least two arc-shaped recessed structures; correspondingly, the continuous protrusion 11 is constructed as at least two arc-shaped protrusion structures.

[0057] In this way, by setting the continuous curved recessed structure of the anti-leakage groove as at least two arc-shaped recessed structures, and correspondingly constructing the continuous protrusion 11 as at least two arc-shaped protrusions, the sealing effect between the sliding vane 3 and the roller 1 is further enhanced, effectively solving the leakage problem of the existing rotor 2 compressor. The corresponding interlocking of at least two arc-shaped recesses and arc-shaped protrusions forms a stepped sealing interface with multiple protrusions and recesses. Compared with a single arc-shaped structure, this significantly increases the complexity of the refrigerant leakage path and the sealing contact area. Even under the condition of low-frequency operation of the compressor and easy rupture of the oil film, the refrigerant liquid penetration can be blocked through multiple sealing barriers, avoiding the loss of compression efficiency caused by leakage, while reducing the corrosive effect of leakage on components and extending the service life of the compressor's core components.

[0058] In summary, along the length of the slide plate 3, that is, parallel to the direction of the reciprocating motion of the slide plate 3, the first end face 31 is symmetrically provided with anti-leakage groove structures 6 on both sides of the roller mounting groove 311. This structure is a continuously curved recessed structure, specifically set as two arc-shaped recesses, such as the central angle of the first arc-shaped recess being 90° and the central angle of the second arc-shaped recess being 60°. The two recesses are arranged sequentially along the length of the slide plate 3, and the openings are all facing the roller 1. Correspondingly, two arc-shaped protrusions are integrally formed at the edge of the outer circumference of the roller 1. The curvature and central angle of the protrusions are perfectly matched with the recesses. After fitting, a double seal is formed, which effectively prevents refrigerant liquid from leaking from the roller mating area during low-frequency operation.

[0059] To further improve the sealing effect, the number of arc-shaped recesses and protrusions can be increased, such as three arc-shaped recesses and three arc-shaped protrusions, or tiny sealing grooves can be opened on the contact surface of the recesses and protrusions. Lubricating oil can be stored in the grooves to form an oil film seal.

[0060] For example, the width of the sealing groove can be 0.5 mm and the depth can be 0.3 mm.

[0061] Considering the sealing scheme between the blocking part 312 and the outer circumferential surface of the roller 1, in this embodiment of the present disclosure, the side of the blocking part 312 that is in contact with the outer circumferential surface of the roller 1 is a sealing arc segment 312B, and the curvature of the sealing arc segment 312B is adapted to the curvature of the outer circumferential surface of the roller 1.

[0062] In this way, the side of the blocking part 312 that contacts the outer circumferential surface of the roller 1 is set as a sealing arc segment 312B. The radius of the arc segment is equal to the radius of the outer circumferential surface of the roller 1. The axial length of the arc segment covers the axial length of the roller 1, and the two ends of the arc segment extend to the two sides of the slide 3 to form a wrapping fit. The surface roughness of the sealing arc segment 312B is controlled below Ra0.4 to reduce the frictional resistance of the contact surface and ensure no leakage gap, which is especially suitable for high-pressure compressor scenarios.

[0063] Considering the scheme of using an elastic blocking member 7 to adjust the downward pressure of the slide plate 3 on the roller 1, in this embodiment of the present disclosure, the slide plate 3 has a stepped structure 32 on the side near the roller 1, the lower structure 322 of the stepped structure 32 forms a blocking part 312, and an open groove structure 323 is provided between the upper structure 321 and the lower structure 322 of the stepped structure 32. An elastic blocking member 7 is provided in the open groove structure 323. The elastic blocking member 7 is located on the exhaust chamber side of the rotor 2 compressor and is used to adjust the downward pressure of the slide plate 3 on the roller 1.

[0064] In this way, by setting a stepped structure 32 on the side of the vane 3 near the roller 1, forming a blocking part 312 with the lower structure 322, and constructing an open groove between the upper structure 321 and the lower structure 322, and setting an elastic blocking member 7 in the groove on the exhaust chamber side, the downward pressure of the vane 3 on the roller 1 can be precisely adjusted, effectively improving the separation problem between the vane 3 and the roller 1 in the existing rotor compressor 2. When the compressor is operating at low frequency and the internal pressure is low, the elastic blocking member 7 can provide a stable downward pressure to ensure that the vane 3 and the roller 1 always remain in contact, avoiding separation caused by insufficient pressure, thereby reducing the compressor power reduction and operating noise caused by separation; when the operating conditions change, the elastic blocking member 7 can adaptively adjust the downward pressure according to the pressure change on the exhaust chamber side, preventing the downward pressure from being too large to increase friction loss or too small to affect the seal, ensuring the stability of the cooperation between the vane 3 and the roller 1 under different operating conditions.

[0065] Furthermore, the stepped structure 32 allows the elastic blocking member 7 to be integrated into the open groove of the vane 3 itself, without taking up too much space inside the compressor or making major modifications to other core components such as the compressor cylinder 8. This simplifies the assembly complexity of the overall structure. At the same time, the layout of the elastic blocking member 7 on the exhaust chamber side allows it to respond more directly to changes in exhaust chamber pressure and quickly adjust the downpressure to adapt to real-time operating conditions.

[0066] Considering the specific function of the elastic blocking member 7, in this embodiment of the disclosure, the elastic blocking member 7 is configured to directly bear the vertically downward flow field resistance and at least partially derive the flow field resistance to the slider 3.

[0067] In this way, by configuring the elastic blocking member 7 to directly bear the vertically downward flow resistance and at least partially dissipate this resistance to the vane 3, the energy loss during the operation of the vane 3 can be effectively reduced, and the operating efficiency problem caused by the flow resistance in the existing rotor 2 compressor can be improved. When the vane 3 moves back and forth along the groove of the cylinder 8 with the movement of the roller 1, a vertically downward flow resistance will be generated on the exhaust chamber side. If this resistance is entirely borne by the vane 3, it will easily increase the motion load of the vane 3, resulting in additional power loss. However, the elastic blocking member 7 directly bears the flow resistance and partially dissipates it, which can greatly reduce the stress on the vane 3, reduce the frictional resistance between the vane 3 and the groove, reduce the energy waste caused by the resistance, and at the same time prevent the vane 3 from deforming or wearing due to long-term excessive resistance, thus extending the service life of the vane 3.

[0068] Furthermore, the elastic blocking member 7, by bearing and partially dissipating the vertically downward flow resistance, indirectly ensures the stability of the downward pressure exerted by the sliding vane 3 on the roller 1. When the flow resistance fluctuates, the elastic blocking member 7 can buffer the flow through its own force, preventing the resistance from being directly transmitted to the mating surface of the sliding vane 3 and the roller 1. This prevents abnormal changes in downward pressure caused by sudden changes in resistance, thereby ensuring that the sliding vane 3 and the roller 1 always maintain a stable fit. This not only does not interfere with the rolling friction fit between the two through the roller structure 4, but also helps maintain the sealing effect and reduces the risk of separation during low-frequency operation.

[0069] Considering the specific structural scheme of the elastic blocking member 7, in this embodiment of the disclosure, the elastic blocking member 7 includes an elastic element 71 and a guide plate 72. One end of the guide plate 72 is rotatably connected to the edge of the upper structure 321 of the stepped structure 32, and the other end of the guide plate 72 is movable in the open groove structure 323. The elastic element 71 is connected between the upper structure 321 and the guide plate 72.

[0070] In this way, with one end of the guide plate 72 rotatably connected to the edge of the upper structure 321 of the stepped structure 32 and the other end movable in the open groove, and the elastic element 71 connecting the upper structure 321 and the guide plate 72, it can provide stable downward pressure for the sliding vane 3 by relying on the elastic force of the elastic element 71, avoiding the separation of the sliding vane 3 and the roller 1 during low-frequency operation of the compressor. At the same time, when the flow field resistance changes, the movement of the guide plate 72 drives the elastic element 71 to extend and retract, dynamically adjusting the downward pressure to adapt to the working conditions, preventing excessive downward pressure from increasing friction or insufficient downward pressure from affecting the seal. At the same time, the rotation of the guide plate 72 combined with the movable engagement method can flexibly adapt to the reciprocating motion of the sliding vane 3, avoiding jamming with the groove, and without the need for additional complex components, the downward pressure can be dynamically adjusted through simple mechanical engagement, without interfering with the rolling friction engagement between the sliding vane 3 and the roller 1.

[0071] Considering the limiting scheme for the guide plate 72, in this embodiment of the disclosure, the outer edge of the lower structure 322 has a blocking edge 3221, which is used to prevent the guide plate 72 from moving out of the open groove structure 323 to the outside.

[0072] This design prevents the guide plate 72 from detaching from the groove due to vibrations and flow resistance fluctuations during compressor operation, and prevents the failure of the elastic blocking component 7 from causing uncontrolled adjustment of the sliding vane 3's downward pressure. This ensures that the sliding vane 3 and roller 1 maintain a stable fit, reducing the risk of separation and abnormal frictional losses. At the same time, the blocking edge 3221 can constrain the guide plate 72 simply by structural limiting, without the need for additional locking or limiting components. This does not interfere with the normal movement and rotation of the guide plate 72 within the groove, nor does it affect the downward pressure adjustment function of the elastic component 71. While simplifying the structure, this design ensures the reliable operation of the elastic blocking component 7, helping to maintain the overall stability and reliability of the compressor's operation.

[0073] Considering the specific connection scheme of the elastic member 71 between the guide plate 72 and the upper structure 321, in this embodiment of the disclosure, the guide plate 72 is configured to be inclined in its initial state, one end of the elastic member 71 is connected to the outer side of the upper structure 321, and the other end of the elastic member 71 is connected to the large surface area of ​​the guide plate 72.

[0074] In this way, by initially configuring the guide plate 72 at an angle, and connecting one end of the elastic element 71 to the outer side of the upper structure 321 of the stepped structure 32 and the other end to the large surface area of ​​the guide plate 72, the initial elastic force of the elastic element 71 can provide stable downward pressure for the sliding vane 3, ensuring that the sliding vane 3 and the roller 1 are tightly fitted during low-frequency operation of the compressor to reduce separation. At the same time, the connection between the angled guide plate 72 and the elastic element 71 in the large surface area allows the elastic force of the elastic element 71 to be transmitted more evenly to the guide plate 72, thereby acting smoothly on the sliding vane 3. Meanwhile, this connection method is adapted to the movement and rotation requirements of the guide plate 72 in the open groove. The elastic element 71 can flexibly extend and retract with the movement of the guide plate 72, ensuring that the downward pressure can be dynamically adjusted when the flow field resistance changes, avoiding increased friction loss or sealing failure caused by abnormal downward pressure. Moreover, no additional structural assistance is required. The adjustment reliability of the elastic blocking component 7 can be ensured by simply setting a reasonable initial posture and connection position, without interfering with the rolling friction cooperation between the sliding vane 3 and the roller 1.

[0075] Considering the specific function of the elastic element 71, in this embodiment of the disclosure, the elastic element 71 has an initial spring force and can adjust the amount of expansion and contraction according to the pressure change inside the rotor 2 compressor to adapt to the flow field resistance.

[0076] In this way, when the compressor is operating at low frequency and the internal pressure is low, the initial spring force can provide a stable downward pressure for the vane 3, ensuring that the vane 3 and the roller 1 are in close contact, effectively reducing the phenomenon of separation between the two and avoiding power reduction and noise caused by separation. At the same time, when the pressure change inside the compressor causes fluctuations in the flow field resistance, the elastic element 71 can dynamically adapt to the change in resistance by adjusting the amount of extension and retraction. This prevents the vane 3 from being overloaded and increasing friction loss when the flow field resistance is too large, and also prevents the downward pressure from being insufficient when the resistance is too small, thus affecting the sealing effect. Moreover, this process does not require additional control components, and can achieve adaptive adjustment solely through the characteristics of the elastic element 71 itself, without interfering with the rolling friction cooperation between the vane 3 and the roller 1.

[0077] In summary, the side of the slide plate 3 closest to the roller 1 is configured as a stepped structure 32. The lower structure 322 of the stepped structure 32 is the side closest to the roller 1, forming a blocking part 312. The upper structure 321 is the side away from the roller 1. The open groove structure 323 between the lower structure 322 and the upper structure 322 is a rectangular groove. The depth of the groove is 1 / 3 to 1 / 2 of the thickness of the slide plate 3. The guide plate 72 of the elastic blocking member 7 is a rectangular thin plate made of spring steel. One end is rotatably connected to the edge of the upper structure 321 by a hinge, and the other end can move along the bottom surface of the groove. The elastic element 71 is a compression spring. One end is fixed to the outer side of the upper structure 321, which is the side closest to the exhaust chamber, by welding or snap-fit. The other end is connected to the middle position of the guide plate 72 by a hook.

[0078] The guide plate 72 is initially set at an angle, and the elastic element 71 is in a slightly compressed state, providing initial downward pressure to ensure that the slide plate 3 and the roller 1 do not separate during low-frequency operation. When the compressor runs at high speed and the pressure in the exhaust chamber increases, the flow field resistance acts vertically on the guide plate 72, pushing the guide plate 72 to move into the groove and compressing the elastic element 71. The reaction force of the elastic element 71 can adjust the downward pressure of the slide plate 3 on the roller 1, avoiding excessive pressure that could lead to increased friction. At the same time, the guide plate 72 can directly bear the vertically downward flow field resistance and transmit part of the resistance through the elastic element 71 to the upper structure 321, and then to the slide plate 3, reducing the impact of the flow field resistance on the roller mating area.

[0079] For example, the initial angle between the guide plate 72 and the length direction of the slider 3 can be 30°-45°.

[0080] The lower structure 322 has an integrally formed blocking edge 3221 on its outer edge. When the guide plate 72 moves to its maximum stroke, the blocking edge 3221 contacts the end of the guide plate 72 to prevent it from falling out of the groove. The stiffness of the elastic element 71 can be set according to the rated pressure of the compressor. For example, when the rated pressure is 3MPa, the spring stiffness is 5N / mm to ensure that it can flexibly adjust the amount of expansion and contraction with pressure changes and adapt to the flow field resistance under different working conditions.

[0081] For example, the blocking edge 3221 may extend along the moving direction of the guide plate 72 and have a height of 1-2 mm.

[0082] This disclosure also provides a rotor compressor 2, including the aforementioned structure of sliding vanes 3 and rollers 1 working together.

[0083] Specifically, the rotor compressor 2 includes a cylinder 8, a rotor 2, a sliding vane 3 and roller 1 mating structure, an intake assembly, and an exhaust assembly. The interior of the cylinder 8 is a cylindrical chamber, the diameter of which is adapted to the outer diameter of the roller 1, with a mating clearance of 0.05-0.1mm. The eccentric section of the rotor 2 passes through the roller 1, and both ends of the rotor 2 are supported on the end caps of the cylinder 8 by bearings, allowing it to rotate around its own axis. The sliding vane 3 is embedded in the radial groove of the cylinder 8, the roller structure 4 on the first end face 31 rolls with the outer circumferential surface of the roller 1, the blocking part 312 fits and seals with the roller 1, and the anti-leakage groove structure 6 fits with the continuous protrusion 11 of the roller 1. The intake assembly is connected to the intake port of the cylinder 8, and the exhaust assembly is connected to the exhaust port of the cylinder 8.

[0084] For example, the intake assembly includes an intake tube, an intake valve, etc.

[0085] For example, the exhaust assembly includes an exhaust pipe, an exhaust valve, etc.

[0086] During operation, rotor 2 drives roller 1 to revolve, and roller 1 pushes slide 3 to reciprocate along the slide groove. The rolling cooperation between roller structure 4 and roller 1 reduces friction loss. The blocking part 312 and the anti-leakage groove structure 6 form multiple seals to prevent leakage. The elastic blocking component 7 adjusts the downward pressure of slide 3 to prevent separation during high and low frequency operation, ultimately achieving efficient refrigerant intake, compression and exhaust.

[0087] This disclosure also provides an air conditioner, including the aforementioned rotor compressor 2.

[0088] Specifically, the air conditioner includes the aforementioned rotor compressor 2, condenser, evaporator, throttling device, and piping system. The rotor compressor 2 is connected to the condenser, throttling device, and evaporator in sequence through piping to form a refrigerant circulation loop. When the compressor is running, it compresses the low-temperature, low-pressure refrigerant vapor into high-temperature, high-pressure vapor, discharges it into the condenser to condense it into liquid, and after being throttled and depressurized by the throttling device, it enters the evaporator to evaporate and absorb heat, thus realizing the cooling or heating function of the air conditioner. Due to the optimized structure of the sliding vane 3 and roller 1, the compressor's energy efficiency is improved by 5%-10%, noise is reduced, and the operational stability is significantly improved, extending the overall service life of the air conditioner.

[0089] The sliding vane 3 and roller 1 mating structure provided in this embodiment replaces the sliding fit with a rolling fit, significantly reducing friction loss and heat generation, and improving compressor efficiency. It has multiple sealing structures, such as the fitting of the blocking part 312, the anti-leakage groove and the protrusion fitting, which can solve the problem of low-frequency leakage. The elastic blocking member 7 is used to adjust the downward pressure to prevent the sliding vane 3 and roller 1 from separating during high and low frequency operation, thus reducing noise. The components are simple in structure, easy to process and assemble, suitable for mass production, and can be widely used in various rotor compressors and air conditioners.

[0090] To better understand the technical solution of the sliding vane 3 and roller 1 mating structure and the rotor 2 compressor provided in this disclosure, the following implementation examples are provided for reference: This disclosure proposes a structure for a sliding vane 3 and a roller 1. To address the problem of high friction at the contact point between the sliding vane 3 and the roller 1, a solution of assembling a roller in the middle is proposed. In addition, to address the separation phenomenon during low-frequency operation of the compressor, an adjustable downward pressure structure is provided, along with a sealing structure. When the roller bounces, leakage can be effectively reduced.

[0091] The three-dimensional models of the sliding vane 3, roller 1, and cylinder 8 are as follows: Figure 1 As shown, in Figure 1 As can be seen, the basic working principle of this disclosure is the same as that of the rotor compressor 2, both of which involve pressure changes as the volume of the intake and exhaust chambers changes with the rotation of the roller 1.

[0092] It should be noted that two sealing structures (i.e., blocking parts 312) are provided on the left and right sides of roller 1. The sealing structure is in the form of two raised arc-shaped structures. In actual use, the number of raised sealing structures can be increased, which is not limited here. The structure of sliding plate 3 is as follows. Figure 8 As shown, a leak-proof groove structure 6 is provided at the bottom of the slide plate 3, symmetrically arranged on both sides, and cooperates with the protruding structure on the roller 1. On the other hand, an adjustable downward pressure structure is provided on the left side of the slide plate 3. Specifically, the roller mounting groove 311 is a whole rectangular structure. If a sealing structure is not used, leakage will occur during movement. Therefore, a groove structure is provided in the vertical direction to cooperate with the roller 1 for sealing. At the same time, arc-shaped mating surfaces are provided on the left and right sides of the bottom surface of the slide plate 3. This is a specially extended bottom surface of the slide plate 3 to cooperate with the roller 1 for sealing. The number of rollers installed on the bottom surface of the slide plate 3 is not limited in this embodiment. However, it should be noted that the rollers are not arranged in a straight line. A straight line arrangement would cause abnormal cooperation with the roller 1. During installation, the height of the axis of each roller is slightly different (very small). From the mating point of the roller and the roller 1, it can be seen that the mating point from left to right is actually an arc. This ensures that each roller rotates during movement.

[0093] It is important to note that if the 3D model of roller 1 changes and no corresponding changes are made to cylinder 8, the intake and exhaust chambers will be connected. This will cause the entire compressor to malfunction during operation. Therefore, the structure of cylinder 8 should be as follows: Figure 7 As shown, the inner ring of the cylinder body 8 is modified to correspond with the structure of the roller 1, with mating grooves on the upper and lower parts. With this structural design, the intake and exhaust chambers are not directly connected when the cylinder body 8 mates with the roller 1.

[0094] Additionally, considering the increased length on the left side, a sloping structure is incorporated. The spring retains its initial force, ensuring that during low-frequency rotation and when the compressor pressure is low, the vertical downward flow resistance is greater when the sliding vane 3 moves in the exhaust chamber on the left side, compared to a structure without a sloping surface. On the other hand, considering that the flow resistance has a smaller impact when the pressure increases, a spring structure is included. When the compressor speed is high under excessive pressure, the flow resistance can be appropriately reduced. The remaining flow resistance can be used to compensate for the sealing problem caused by the overall roller's vibration during high-speed movement, maintaining appropriate fluid resistance during upward or downward sliding.

[0095] It should be understood that the terminology used herein is for the purpose of describing particular exemplary embodiments only and is not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms “a,” “an,” and “described” as used herein may also include the plural forms. The terms “comprising,” “including,” “containing,” and “having” are inclusive and therefore indicate the presence of the stated features, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not construed as requiring them to be performed in a particular order described or illustrated unless the order of performance is explicitly indicated. It should also be understood that additional or alternative steps may be used.

[0096] Although terms such as first, second, third, etc., may be used in this document to describe multiple elements, components, regions, layers, and / or segments, these elements, components, regions, layers, and / or segments should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or segment from another. Unless the context clearly indicates otherwise, terms such as "first," "second," and other numerical terms used herein do not imply order or sequence. Therefore, the first element, component, region, layer, or segment discussed below may be referred to as the second element, component, region, layer, or segment without departing from the teachings of the exemplary embodiments.

[0097] The above description is merely a specific embodiment of this disclosure, enabling those skilled in the art to understand or implement it. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this disclosure. Therefore, this disclosure is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A vane and roller mating structure, applied to a rotary compressor, characterized in that, include: A roller, which is fitted onto an eccentric section of the rotor, is configured to follow the eccentric section in a revolution around the rotor, and is also configured to perform a slight self-rotational driven motion, the roller being used to compress the refrigerant; The slide has a first end face at one end near the roller, and along the width direction of the slide, the first end face has a roller mounting groove and blocking portions disposed on both sides of the roller mounting groove. A roller structure is installed in a roller mounting groove, the roller mounting groove includes a first plane, the blocking part includes a second plane, a gap is left between the first plane and the second plane, the roller structure rolls with the outer circumferential surface of the roller in the area of ​​the gap, and the blocking part is fitted with the outer circumferential surface of the roller through the second plane.

2. The sliding plate and roller mating structure according to claim 1, characterized in that, The portion of the second plane that contacts the outer circumferential surface of the roller is arc-shaped, and the curvature matches the outer circumferential surface of the roller; the contact surface between the first plane and the roller structure is a line contact or a point contact.

3. The sliding plate and roller mating structure according to claim 1, characterized in that, Roller mounting posts are provided in the roller mounting groove, and one roller mounting post is installed at each end of one of the roller structures.

4. The sliding plate and roller mating structure according to claim 1, characterized in that, Along the length of the slide, the first end face is provided with anti-leakage groove structures on both sides of the roller mounting groove. The anti-leakage groove structure is constructed as a continuously curved concave structure, and the opening direction of the anti-leakage groove structure faces the roller.

5. The sliding plate and roller mating structure according to claim 4, characterized in that, The outer circumferential surface of the roller is provided with a continuous protrusion at the edge position, which is used to fit and match the anti-leakage groove structure of the slide plate for sealing.

6. The sliding plate and roller mating structure according to claim 5, characterized in that, Along the length of the slide, the continuously curved recessed structure of the anti-leakage groove is constructed as at least two arc-shaped recessed structures; correspondingly, the continuous protrusion is constructed as at least two arc-shaped protrusions.

7. The sliding plate and roller mating structure according to claim 1, characterized in that, The side of the blocking part that contacts the outer circumferential surface of the roller is a sealing arc segment, and the curvature of the sealing arc segment is adapted to the curvature of the outer circumferential surface of the roller.

8. The sliding plate and roller mating structure according to claim 1, characterized in that, The slide plate has a stepped structure on the side near the roller. The lower part of the stepped structure forms the blocking part. There is an open groove structure between the upper and lower parts of the stepped structure. An elastic blocking member is provided in the open groove structure. The elastic blocking member is located on the exhaust chamber side of the rotor compressor and is used to adjust the downward pressure of the slide plate on the roller.

9. The sliding plate and roller mating structure according to claim 8, characterized in that, The elastic blocking member is configured to directly bear the vertically downward flow field resistance and to at least partially detach the flow field resistance from the slider.

10. The sliding plate and roller mating structure according to claim 9, characterized in that, The elastic blocking member includes an elastic element and a guide plate. One end of the guide plate is rotatably connected to the edge of the upper structure of the stepped structure, and the other end of the guide plate is movable within the open groove structure. The elastic element is connected between the upper structure and the guide plate.

11. The sliding plate and roller mating structure according to claim 10, characterized in that, The outer edge of the lower structure has a blocking edge, which is used to prevent the guide plate from moving out of the open groove structure to the outside.

12. The sliding plate and roller mating structure according to claim 10, characterized in that, The guide plate is configured to be inclined in its initial state. One end of the elastic element is connected to the outer side of the upper structure, and the other end of the elastic element is connected to the large surface area of ​​the guide plate.

13. The sliding plate and roller mating structure according to claim 10, characterized in that, The elastic element has an initial spring force and can adjust its expansion and contraction amount according to the pressure changes inside the rotor compressor to adapt to the flow field resistance.

14. A rotary compressor, characterized in that, Includes the sliding plate and roller mating structure as described in any one of claims 1-13.

15. An air conditioner, characterized in that, Including the rotary compressor as described in claim 14.

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