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

Abstract

The present disclosure relates to a sliding vane and roller matching structure of a rotary compressor, a rotary compressor and an air conditioner. The sliding vane and roller matching structure comprises a roller, a sliding vane and a ball structure. The roller is sleeved on an eccentric section of a rotor, is configured to make a revolution motion around the rotor following the eccentric section, and is configured to make a driven motion of slight rotation. The roller is used to push refrigerant compression. An end of the sliding vane close to the roller is a first end face. The ball structure is installed on the first end face. An outer circumferential surface of the roller has a rolling groove. The ball structure is configured to roll along the rolling groove. A rolling matching relationship is formed between the sliding vane and the roller through the ball structure.

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] Rotary compressors, with their advantages of compact structure, small size, light weight and high operating efficiency, have been widely used in refrigeration and heating equipment such as air conditioners, refrigerators and heat pumps. Their core working components include cylinder, rollers, vanes and main shaft, among which the matching relationship between vanes and rollers directly determines the compressor's compression efficiency, operating stability and energy consumption level.

[0003] In the existing rotary compressor structure, the sliding vane and roller are coupled using a cam-sliding vane motion. Specifically, the sliding vane is embedded in the radial groove of the cylinder and can reciprocate vertically along the groove; the roller is eccentrically mounted on the eccentric journal of the main shaft, and its outer circle forms line contact with one end of the sliding vane when the main shaft rotates. The rotation of the roller drives the sliding vane to achieve reciprocating motion, which, together with the cylinder, forms a variable-volume compression chamber to complete the intake, compression, and exhaust cycle.

[0004] However, the existing line contact fit structure between the sliding vane and the roller still has many technical problems that need to be solved in actual operation, specifically in the following three aspects: Vane and roller are prone to separation: During roller rotation, factors such as gas pressure fluctuations, motion inertia, and insufficient vane return force can cause momentary separation of the line contact between the vane and roller. This separation leads to leakage of high-pressure gas from the compression chamber to the low-pressure chamber, resulting not only in decreased compressor efficiency and increased power loss, but also in additional noise caused by gas impact and component collisions, affecting equipment operational stability and user experience.

[0005] Refrigerant leakage is a significant issue during low-frequency operation: Because the vanes and rollers only have line contact, the components move slowly during low-frequency compressor operation, making the lubricating oil film in the line contact area prone to discontinuity or breakage. This leads to decreased sealing performance of the compression chamber, causing refrigerant leakage, further exacerbating compression efficiency loss, and potentially even causing component corrosion due to leakage, thus shortening the compressor's lifespan.

[0006] Significant frictional heat generation and power loss occur during high-speed operation: Under high-speed compressor operation, intense relative sliding friction occurs in the line contact area between the vanes and rollers. This line contact leads to a high concentration of frictional stress, which not only rapidly generates a large amount of frictional heat, causing component temperature to rise and lubrication performance to deteriorate, but also causes additional power loss due to increased frictional resistance, reducing the overall energy efficiency of the compressor. At the same time, it accelerates the wear of the vane-roller contact surface, affecting the service life of core components.

[0007] In summary, the existing line contact fit structure between the vanes and rollers in rotary compressors has deficiencies in terms of separation risk, sealing performance, and friction loss, which have become key bottlenecks restricting the improvement of energy efficiency, noise control, and lifespan of rotary compressors. There is an urgent need to propose a new fit structure to solve the above-mentioned technical problems. Utility Model Content

[0008] This disclosure provides a vane and roller mating structure, a rotor compressor, and an air conditioner to solve the technical problems of separation risk, sealing performance, and friction loss defects in the prior art.

[0009] The rotary compressor vane and roller mating structure disclosed herein includes: a roller, a vane, and a ball bearing structure. The roller is fitted onto an eccentric section of the rotor and is configured to follow the eccentric section in a revolution around the rotor. The roller is also configured to perform a slight self-rotational motion. The roller is used to compress the refrigerant. A first end face is located on the vane near the roller. The ball bearing structure is mounted on the first end face. The outer circumferential surface of the roller has a rolling groove, and the ball bearing structure is configured to roll along the rolling groove. A rolling fit relationship is formed between the vane and the roller through the ball bearing structure.

[0010] The rolling groove is constructed as an arc-shaped groove structure formed on the outer circumferential surface of the roller. The arc-shaped groove structure includes a groove surface located on the bottom surface and an arc-shaped surface connected to both sides of the groove surface. Along the radial direction of the roller, the arc-shaped surface protrudes from the groove surface and is arranged in a direction away from the center of the roller. The groove surface is used for rolling engagement with the ball structure, and the arc-shaped surface is used for matching and sealing with the slide plate.

[0011] The first end face of the slide is constructed as an arc-shaped mounting surface. The central region of the arc-shaped mounting surface has a ball bearing mounting groove, and both sides of the arc-shaped mounting surface have raised mounting angles. The inner surface of the raised mounting angles is used to match and seal with the arc-shaped surface.

[0012] Wherein, a first gap is left between the arc-shaped mounting surface and the outer circumferential surface of the roller, the rotor compressor includes an intake chamber and an exhaust chamber, and the matching seal between the arc-shaped surface and the protruding mounting angle is used to prevent the exhaust chamber and the intake chamber from establishing a communication relationship through the first gap.

[0013] The ball bearing mounting groove is constructed as a groove structure formed on the arc-shaped mounting surface along the thickness direction of the slide plate. Multiple mounting holes are spaced apart in the groove structure, and each mounting hole is used to install one ball bearing structure.

[0014] Wherein, along the thickness direction of the slide, sealing structures are provided on both sides of the ball mounting groove, and a second gap is left between the groove structure and the outer circumferential surface of the roller. The sealing structure is used to prevent the second gap from communicating with the exhaust chamber or the intake chamber.

[0015] Wherein, along the thickness direction of the slide, the thickness dimension of a single sealing structure is greater than or equal to 10% of the overall thickness dimension of the slide.

[0016] The inner surface of the protruding mounting angle is constructed as a first inclined surface structure, and the arc-shaped surface on the roller has a second inclined surface structure that matches and seals with the inclined surface structure.

[0017] This disclosure also provides a rotary compressor, including the aforementioned vane and roller in a cooperative configuration, and a cylinder body, wherein the roller is eccentrically mounted inside the cylinder body, and the inner wall of the cylinder body has a profile that matches the outer circumferential surface of the roller.

[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 sliding vane and roller mating structure, rotor compressor, and air conditioner provided in this disclosure convert the sliding friction between the vane and roller into rolling friction by setting a ball bearing structure on the first end face of the vane and adapting a rolling groove on the outer circumferential surface of the roller. This significantly reduces the coefficient of friction, reduces frictional heat generation and power loss. At the same time, the contact characteristics of the rolling mating can avoid the problem of local wear aggravation caused by sliding friction and extend the service life of the components.

[0020] Furthermore, the precise fit between the ball bearing structure and the rolling grooves enhances the tightness of the contact between the vanes and the rollers. During low-frequency operation of the compressor, this reduces separation caused by gaps, lowers the risk of leaks, and ensures refrigerant compression efficiency. The combined motion of the rollers, which revolve around the rotor's eccentric section and rotate slightly on their own axis, along with the smoothness of the rolling fit, further optimizes the power transmission efficiency of the compressor, reduces operating noise, and balances energy efficiency and stability. 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, for those skilled in the art, other drawings can be obtained 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 mounting structure of the sliding vane and roller mating structure relative to the rotor and cylinder body provided in the embodiments of this disclosure; Figure 2 This is a schematic diagram of the axial structure of the roller provided in an embodiment of the present disclosure; Figure 3 This is a schematic diagram of the axial structure of the slider provided in an embodiment of the present disclosure; Figure 4 This is a side cross-sectional view of the ball structure, roller, rotor, and cylinder provided in the embodiments of this disclosure. Figure 5 A schematic diagram of the installation structure of the ball bearing structure relative to the slide and roller provided in the embodiments of this disclosure; Figure 6 This is a schematic diagram of the half-section axial side structure of the cylinder block provided in an embodiment of this disclosure; Figure 7 This is a schematic diagram of the half-section axial side structure of the roller provided in an embodiment of this disclosure.

[0025] Explanation of reference numerals in the attached figures: 1. Roller; 11. Outer circumferential surface; 111. Rolling groove; 111A. Slide groove surface; 111B. Arc-shaped surface; 111B1. Second inclined surface structure; 2. Rotor; 3. Sliding vane; 31. First end face; 31A. Arc-shaped mounting surface; 311. Ball mounting groove; 3111. Mounting hole; 312. Raised mounting angle; 3121. First inclined surface structure; 4. Ball structure; 5. 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 sliding vane and roller mating structure, rotor compressor, and air conditioner disclosed herein aim to solve the technical problems of sliding vane and roller separation risk, poor sealing performance, and high frictional loss in existing rotor compressors. The specific implementation methods of each technical solution are described in detail below with reference to the accompanying drawings. The orientation descriptions are based on the normal assembly and operation state of the compressor; the thickness direction refers to the direction perpendicular to the sliding vane's own motion guide direction, and the radial direction refers to the radius direction of the roller around its own center.

[0030] refer to Figures 1-7 This disclosure provides a sliding vane 3 and roller 1 mating structure, including: roller 1, sliding vane 3 and ball structure 4. The roller 1 is sleeved on the eccentric section of the rotor 2. The roller 1 is configured to follow the eccentric section in a revolution around the rotor 2, and the roller 1 is configured to perform a small self-rotation driven motion. The roller 1 is used to push the refrigerant to compress. The end of the sliding vane 3 near the roller 1 is a first end face 31. The ball structure 4 is mounted on the first end face 31. The outer circumferential surface 11 of the roller 1 has a rolling groove 111. The ball structure 4 is configured to roll along the rolling groove 111. The sliding vane 3 and the roller 1 form a rolling mating relationship through the ball structure 4.

[0031] 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.

[0032] 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.

[0033] In this way, by setting the ball structure 4 on the first end face 31 of the slide plate 3 and adapting the rolling groove 111 on the outer circumferential surface 11 of the roller 1, the sliding friction between the slide plate 3 and the roller 1 is converted into rolling friction, which greatly reduces the coefficient of friction, reduces frictional heat generation and power loss. At the same time, the contact characteristics of rolling fit can avoid the problem of local wear aggravation caused by sliding friction and extend the service life of the component.

[0034] Furthermore, the precise fit between the ball bearing structure 4 and the rolling groove 111 can improve the tightness of the fit between the vane 3 and the roller 1. When the compressor is running at low frequency, it can reduce the separation phenomenon caused by the gap between the two, reduce the risk of sealing leakage, and ensure the refrigerant compression efficiency. The combined motion of the roller 1 with the eccentric section of the rotor 2 and the slight rotation of the rotor, combined with the smoothness of the rolling fit, can further optimize the power transmission efficiency of the compressor during operation, reduce operating noise, and balance energy saving and stability.

[0035] Considering the sealing scheme between the rolling groove 111 and the outer circumferential surface 11 of the roller 1, in this embodiment of the present disclosure, the rolling groove 111 is constructed as an arc-shaped groove structure formed on the outer circumferential surface 11 of the roller 1. The arc-shaped groove structure includes a sliding groove surface 111A located on the bottom surface and an arc-shaped surface 111B connected to both sides of the sliding groove surface 111A. Along the radial direction of the roller 1, the arc-shaped surface 111B protrudes from the sliding groove surface 111A and is arranged in a direction away from the center of the roller 1. The sliding groove surface 111A is used for rolling engagement with the ball structure 4, and the arc-shaped surface 111B is used for matching and sealing with the sliding plate 3.

[0036] In this way, by constructing the rolling groove 111 as an arc-shaped groove structure containing a groove surface 111A and an arc-shaped surface 111B, the synergistic optimization of friction loss and structural function is achieved. The precise matching of the groove surface 111A and the ball structure 4 with the rolling engagement transforms the traditional line contact sliding friction between the vane 3 and the roller 1 into rolling friction, significantly reducing the coefficient of friction, minimizing power loss due to frictional heat generation, and preventing localized wear on component surfaces caused by sliding friction. This extends the service life of the roller 1 and vane 3, ensuring the long-term stability of the rotor compressor.

[0037] Furthermore, the arc-shaped surface 111B, which protrudes radially from the roller 1 onto the groove surface 111A, can form a tight-fitting sealing structure with the vane 3, effectively filling the potential gap between the rolling groove 111 and the vane 3. This sealing structure can prevent refrigerant leakage between the compressor's exhaust chamber and intake chamber through the rolling groove 111 area. Especially in low-frequency operation scenarios, it can prevent seal failure caused by the widening of the gap due to the relative movement of the vane 3 and the roller 1, significantly improving the compressor's sealing performance and ensuring refrigerant compression efficiency.

[0038] Considering the sealing scheme between the ball mounting groove 311 and the outer circumferential surface 11 of the roller 1, in this embodiment of the present disclosure, the first end face 31 of the slide 3 is constructed as an arc-shaped mounting surface 31A. The central region of the arc-shaped mounting surface 31A has a ball mounting groove 311, and both sides of the arc-shaped mounting surface 31A have protruding mounting angles 312. The inner surface of the protruding mounting angles 312 is used to match and seal with the arc-shaped surface 111B.

[0039] In this way, the first end face 31 of the slide plate 3 is constructed as an arc-shaped mounting surface 31A, and a ball mounting groove 311 is set in the middle area. This provides a stable mounting and movement space for the ball structure 4, ensuring that the ball can roll smoothly along the rolling groove 111 of the roller 1, realizing the transformation of sliding friction between the slide plate 3 and the roller 1 into rolling friction, reducing friction loss and power waste. Furthermore, the matching shape of the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1 reduces the initial gap between the two, laying a structural foundation for subsequent sealing, avoiding local stress concentration or abnormal friction caused by mismatch in mounting surface shape, and ensuring the smoothness of the coordinated movement of the slide plate 3 and the roller 1.

[0040] Furthermore, the raised mounting angles 312 on both sides of the arc-shaped mounting surface 31A can precisely match and seal with the arc-shaped surface 111B of the roller 1, directly preventing refrigerant leakage between the compressor's exhaust chamber and intake chamber through the gap between the ball bearing mounting groove 311 and the outer circumferential surface 11 of the roller 1. The raised mounting angles 312 compensate for the potential sealing weakness caused by the ball bearing mounting groove 311. Especially in scenarios where the compressor operates at high frequency, components vibrate, or separation tends to occur at low frequency, a stable sealing effect can still be maintained, avoiding a decrease in compression efficiency due to leakage. Simultaneously, it reduces operating noise caused by seal failure, further improving the overall performance and reliability of the rotary compressor.

[0041] Considering further functional schemes of the arc-shaped surface 111B and the raised mounting angle 312, in this embodiment of the present disclosure, a first gap is left between the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1. The rotor compressor includes an intake chamber and an exhaust chamber. The matching seal between the arc-shaped surface 111B and the raised mounting angle 312 is used to prevent the exhaust chamber and the intake chamber from establishing a communication relationship through the first gap.

[0042] In this way, a first gap is reserved between the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1. This not only avoids the additional sliding friction caused by direct contact between the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1 during the reciprocating motion of the vane 3, reducing component wear and power loss caused by hard contact, but also provides sufficient movement space for the revolution and slight rotation of the roller 1, ensuring the smoothness of the coordinated movement of the vane 3 and the roller 1, avoiding operational jamming or abnormal noise caused by motion interference, and improving the stability and smoothness of the rotor compressor operation.

[0043] Furthermore, the matching seal between the arc-shaped surface 111B and the raised mounting angle 312 precisely prevents the exhaust chamber and the intake chamber from establishing a connection through the first gap. This sealing structure effectively isolates the high-pressure exhaust chamber from the low-pressure intake chamber, preventing refrigerant from leaking from the exhaust chamber into the intake chamber through the first gap due to chamber pressure difference, thus avoiding a decrease in compression efficiency caused by seal leakage. Especially in scenarios where the compressor is prone to separation of the sliding vane 3 and roller 1 during low-frequency operation, this matching seal can still maintain a stable sealing effect, further ensuring the volumetric efficiency of the rotary compressor and helping to achieve energy-saving and consumption-reducing goals.

[0044] Considering the specific installation scheme of the ball structure 4, in this embodiment of the disclosure, the ball mounting groove 311 is constructed as a groove structure formed on the arc-shaped mounting surface 31A along the thickness direction of the slide plate 3. A plurality of mounting holes 3111 are provided at intervals in the groove structure, and one mounting hole 3111 is used to install one ball structure 4.

[0045] In this way, the ball mounting groove 311 is constructed as a groove structure opened along the thickness direction of the slide 3, and multiple mounting holes 3111 are set at intervals in the groove. Each mounting hole 3111 corresponds to the installation of one ball structure 4. This configuration provides a precise and independent installation and positioning space for the ball structure 4, which can effectively avoid the problem of mutual collision, displacement or dislodging of the balls during rolling. It ensures that each ball can move stably along the rolling groove 111 of the roller 1, thereby ensuring the reliability of the rolling fit relationship between the slide 3 and the roller 1, preventing abnormal friction or fit failure caused by ball misalignment, and extending the overall service life of the component.

[0046] In addition, the grooved ball mounting groove 311 provided along the thickness direction of the vane 3 allows the mounting height of the ball structure 4 to be adapted to the arc-shaped mounting surface 31A. This prevents excessive compression between the ball and the outer circumferential surface 11 of the roller 1 due to excessive ball protrusion, and also prevents excessive installation depth from affecting rolling efficiency. At the same time, the spaced mounting holes 3111 allow the ball to evenly bear the contact force between the vane 3 and the roller 1, avoiding ball wear or breakage caused by local stress concentration, further reducing friction loss, reducing compressor operating power waste, and helping to improve the operating efficiency and stability of the rotary compressor.

[0047] Considering the specific sealing scheme of the ball bearing mounting groove 311, in this embodiment of the disclosure, a sealing structure is provided on both sides of the ball bearing mounting groove 311 along the thickness direction of the slide plate 3. A second gap is left between the groove structure and the outer circumferential surface 11 of the roller 1. The sealing structure is used to prevent the second gap from communicating with the exhaust chamber or the intake chamber.

[0048] In this way, a sealing structure is protruding along the thickness direction of the sliding vane 3 on both sides of the ball bearing mounting groove 311, forming a sealed protection for the second gap between the groove structure and the outer circumferential surface 11 of the roller 1, which can directly block the communication path between the second gap and the exhaust chamber and the intake chamber. This setting effectively compensates for the weak sealing area caused by accommodating the ball bearing structure 4 in the ball bearing mounting groove 311, and prevents the refrigerant in the high-pressure side exhaust chamber from leaking into the low-pressure side intake chamber through the second gap. From a structural perspective, it solves the contradiction between friction reduction and sealing in traditional rolling fit settings, ensuring that the volumetric efficiency of the rotor compressor is not affected by gap leakage.

[0049] Furthermore, the protruding sealing structure is integrated with the ball bearing mounting groove 311, eliminating the need for additional complex seals. This simplifies the overall structure and assembly process of the vane 3, while maintaining a stable seal during the reciprocating motion of the vane 3 and the revolution and rotation of the roller 1, thanks to the fit between the sealing structure and the outer circumferential surface 11 of the roller 1. Simultaneously, the reserved second gap prevents excessive compression and friction between the ball bearing structure 4 and the outer circumferential surface 11 of the roller 1 during rolling, while the sealing structure achieves a leak-proof seal without interfering with the normal movement of the balls. This further balances the smoothness and sealing performance of the compressor operation, reduces power loss, and improves the overall reliability of the machine.

[0050] Considering the implementation scheme of the sealing structure, in this embodiment of the disclosure, along the thickness direction of the slide 3, the thickness dimension of a single sealing structure is greater than or equal to 10% of the overall thickness dimension of the slide 3.

[0051] In this way, by limiting the thickness of a single sealing structure along the thickness direction of the slide plate 3 to no less than 10% of the overall thickness of the slide plate 3, sufficient structural strength and contact area are provided for the sealing structure. This size setting can prevent the sealing structure from deforming, wearing, or even breaking due to vibration, friction, or refrigerant pressure during long-term operation because the thickness is too thin. It ensures that the sealing structure can stably fit the outer circumferential surface 11 of the roller 1, continuously blocking the communication path between the ball mounting groove 311 and the exhaust chamber and intake chamber. From a size perspective, it ensures the long-term effectiveness of the sealing effect and solves the problem of easy failure of traditional thin sealing structures.

[0052] Furthermore, this thickness ratio balances sealing performance with the overall structural stability of the sliding vane 3. It avoids increasing the weight and inertia of the sliding vane 3 due to excessive sealing thickness, thus preventing any impact on its reciprocating motion flexibility and response speed. At the same time, a sufficiently thick sealing structure enhances the coverage of the second gap, further reducing the risk of refrigerant leakage. Simultaneously, this dimensional standard facilitates precision control in industrial production, ensuring that the sealing structure of each compressor achieves uniform sealing performance indicators. This improves the consistency and reliability of mass production of rotary compressors, laying the foundation for the stable operation of downstream products such as air conditioners.

[0053] Considering the specific construction scheme of the protruding mounting angle 312 and the arc-shaped surface 111B, in this embodiment of the disclosure, the inner side of the protruding mounting angle 312 is constructed as a first inclined surface structure 3121, and the arc-shaped surface 111B on the roller 1 has a second inclined surface structure 111B1 that matches, fits and seals with the inclined surface structure.

[0054] In this way, the inner surface of the protruding mounting angle 312 is constructed as a first inclined surface structure 3121, while the arc-shaped surface 111B of the roller 1 forms a matching second inclined surface structure 111B1. Sealing is achieved through the inclined surface fit, which significantly increases the sealing contact area and improves sealing reliability compared to traditional line contact seals. This inclined surface matching setting can create a certain radial preload effect during compressor operation using the interaction force between the inclined surfaces. Especially during low-frequency operation, it can effectively suppress the separation tendency of the vane 3 and the roller 1, reduce leakage problems caused by separation gaps, ensure the sealing isolation effect between the exhaust chamber and the intake chamber, and avoid a decrease in compression efficiency.

[0055] Meanwhile, the matching design of the inclined surface structure balances sealing performance and smooth movement. The fit between the first and second inclined surfaces does not hinder the revolution and slight rotation of the roller 1 along the eccentric section of the rotor 2, nor does it affect the reciprocating linear movement of the vane 3 along the groove of the vane 3 in the cylinder 5, thus avoiding additional frictional losses caused by interference from the sealing structure. Furthermore, the inclined surface structure guides the refrigerant flow, reducing eddy current losses in the sealing area, further lowering compressor operating noise and power loss, and improving the overall operational stability and energy efficiency of the rotary compressor.

[0056] This disclosure also provides a rotary compressor, including the aforementioned vane 3 and roller 1 in cooperation, and a cylinder 5, wherein the roller 1 is eccentrically mounted inside the cylinder 5, and the inner wall of the cylinder 5 has a profile that matches the outer circumferential surface 11 of the roller 1.

[0057] In this way, the rotary compressor disclosed herein integrates the aforementioned sliding vane 3 and roller 1 mating structure, and combines the matching setting of the inner wall contour of the cylinder 5 with the outer circumferential surface 11 of the roller 1. The matching contour of the inner wall of the cylinder 5 and the outer circumferential surface 11 of the roller 1 can ensure that the roller 1 always maintains a stable fit with the inner wall of the cylinder 5 when it revolves with the eccentric section of the rotor 2, avoiding refrigerant leakage caused by additional gaps due to contour mismatch. At the same time, in conjunction with the rolling friction between the sliding vane 3 and the roller 1 and the multi-dimensional sealing structure, the power loss and component wear caused by traditional sliding friction are greatly reduced, the operating efficiency and service life of the compressor are significantly improved, and the core pain points of existing rotary compressors, such as high separation risk, poor sealing and high loss, are effectively solved.

[0058] Furthermore, the eccentric mounting of roller 1 inside cylinder 5 complements the structure of vane 3 and roller 1: the eccentric mounting provides the necessary volumetric variation space for refrigerant compression, while the matching inner wall contour of cylinder 5 ensures effective isolation between the high-pressure and low-pressure chambers during compression. Combined with the rolling fit of vane 3 and roller 1 and the sealing design, leakage and frictional resistance within the compression chamber are further reduced. This integrated structural design allows for smoother power transmission during high-frequency operation and more stable sealing during low-frequency operation of the rotary compressor. It not only reduces operating noise but also improves the compressor's volumetric efficiency and energy efficiency ratio, providing core support for the energy-saving and stable operation of downstream equipment such as air conditioners.

[0059] This disclosure also provides an air conditioner including the aforementioned rotary compressor.

[0060] Thus, the air conditioner disclosed herein, by integrating the aforementioned rotary compressor with an optimized sliding vane 3 and roller 1 mating structure, directly inherits the advantages of the rotary compressor in terms of low friction, high sealing, and low risk of separation. Compared to air conditioners equipped with traditional rotary compressors, it can effectively reduce energy waste caused by high compressor friction losses, reduce the probability of operational failures caused by leaking seals or component separation, significantly improve the stability and reliability of the air conditioner's overall operation, avoid fluctuations in cooling / heating efficiency due to compressor problems, and ensure a consistent user experience.

[0061] Furthermore, the optimization of energy efficiency and noise control in this rotary compressor directly drives the upgrade of the air conditioner's core performance: lower compressor power loss improves the air conditioner's energy efficiency ratio, helping it to regulate temperature more efficiently and reduce daily energy consumption; while the reduction in compressor operating noise optimizes the air conditioner's quiet operation, making it particularly suitable for noise-sensitive environments such as homes and offices. At the same time, reduced wear on rotary compressor components extends their lifespan, indirectly increasing the overall service life of the air conditioner, reducing maintenance and replacement costs for users, and providing core support for the air conditioner's market competitiveness.

[0062] To better understand the solutions provided in the embodiments of this disclosure, specific implementation examples are described below.

[0063] The main embodiment of this disclosure changes the sliding friction between the slider 3 and the roller 1 to rolling friction, thereby reducing frictional force and increasing the contact area between the slider 3 and the roller 1 to reduce separation. The use of magnetic material further reduces the risk of separation. This mainly includes: The bottom of the slide plate 3 is designed with an arc surface, and the arc surface is provided with a ball bearing mounting position; the circumferential surface of the roller 1 is designed with a concave structure to match the arc surface of the slide plate 3, and is also provided with a rotation groove when the ball bearing rotates; the contact surface of the slide plate 3 or the roller 1 is provided with a magnetic material coating to further enhance the sealing effect.

[0064] In this embodiment, a sliding vane 3 and a ball bearing structure 4 are proposed. To address the problem of high friction at the contact point between the sliding vane 3 and the ball bearing 1, a solution of assembling the ball bearing 1 in the middle is proposed. At the same time, to address the separation phenomenon during low-frequency operation of the compressor, magnetic materials and inclined surfaces are provided to ensure a tight fit between the sliding vane 3 and the ball bearing 1. The use of arc-shaped contact surfaces and inclined surfaces helps to reduce leakage.

[0065] The working principle of the rotary compressor disclosed herein is that the pressure changes as the volume of the intake chamber and the exhaust chamber changes with the rotation of the roller 1.

[0066] The roller 1 has two arc-shaped surfaces 111B in the middle and inclined surfaces at the top and bottom. A small groove structure is opened in the middle of the roller 1 to cooperate with the roller 1. At the same time, the ball is installed in the slide 3 and can rotate. As can be seen from the figure, the contact surface between the roller 1 and the slide 3 is mainly the central arc surface, and the ball structure 4 is set in the central arc surface. Therefore, during the movement, the contact between the slide 3 and the roller 1 is rolling contact. Compared with the commonly used line contact, the friction is smaller and the friction loss is also smaller.

[0067] The bottom of the slide plate 3 has an arc-shaped surface 111B and an inclined surface that mate with the roller 1. A mounting hole 3111 for the roller 1 is provided in the center of the arc-shaped surface 111B. It is important to note that the mounting holes 3111 of the roller 1 must be arranged in a straight line, and sealing structures, which are arc-shaped, are provided on both sides of the mounting holes 3111. The lengths of the sealing structures on both sides are equal to maintain symmetrical sealing. Furthermore, to prevent insufficient sealing length, the length of the sealing structure must be greater than 0.1 times the width of the slide plate 3; if the length is too short, the sealing requirements cannot be met.

[0068] It is important to note that when using the arc-shaped roller 1, if no corresponding changes are made to the cylinder body 5, the intake and exhaust chambers will be connected. This will cause the entire compressor to malfunction. The inner ring of the cylinder body 5 is modified to correspond to the arc-shaped structure of the roller 1, with an arc-shaped structure in the middle and inclined surfaces at the top and bottom. With this structural design, the intake and exhaust chambers will not be directly connected when the cylinder body 5 mates with the roller 1.

[0069] Furthermore, regarding the separation phenomenon between the sliding vane 3 and the roller 1 that occurs during low-frequency operation of the compressor, this patent proposes to incorporate a magnetic material on the inclined surface. Specifically, the magnetic material can be placed on the inclined surface of either the roller 1 or the sliding vane 3. For example, using a magnetic material on the inclined surface of the roller 1 will attract the iron contained in the sliding vane 3, thus reducing the separation phenomenon between the roller 1 and the sliding vane 3. Simultaneously, using an inclined surface does not increase the height of the roller 1, while simultaneously reducing the separation phenomenon between the roller 1 and the sliding vane 3, and the area of ​​the inclined surface is relatively larger than that of a normal rectangle.

[0070] The sliding vane 3 and roller 1 mating structure, rotary compressor, and air conditioner provided in this disclosure aim to solve the technical problems of separation risk, poor sealing performance, and high friction loss of the sliding vane 3 and roller 1 in existing rotary compressors. The specific implementation methods of each technical solution are described in detail below with reference to the accompanying drawings. The orientation descriptions are based on the normal assembly and operation state of the compressor; "thickness direction" refers to the direction perpendicular to the sliding vane 3 along its own motion guide direction; and "radial direction" refers to the radial direction of the roller 1 around its own center.

[0071] Regarding the basic structure, composition, and assembly relationship of the mating structure between the sliding plate 3 and the roller 1. As shown in the figure, the core of the sliding vane 3 and roller 1 mating structure of this embodiment includes roller 1, sliding vane 3, and ball bearing structure 4. Roller 1 is integrally formed from high-strength ductile iron, and its inner hole and the eccentric section of rotor 2 are fitted with a clearance. The clearance is controlled within the range of 0.02-0.05mm. This clearance setting ensures that roller 1 can follow the eccentric section to make a stable revolution around the center of rotor 2, while also allowing roller 1 to generate a slight rotation during revolution due to the contact force with sliding vane 3 (the rotation speed is 1 / 5-1 / 3 of the revolution speed). Through the combined motion of revolution and slight rotation, roller 1 can push the refrigerant in cylinder 5 to complete the compression process.

[0072] For example, the eccentric section is a cylindrical section on rotor 2 that is off-center from the central axis; The sliding vane 3 is also made of ductile iron, and its surface is nitrided to improve wear resistance. The sliding vane 3 moves in a reciprocating linear motion along the sliding vane 3 groove of the cylinder body 5. The clearance between the sliding vane 3 groove and the sliding vane 3 is 0.01-0.03mm to ensure the smooth movement of the sliding vane 3. The end of the sliding vane 3 closest to the roller 1 is the first end face 31, which is opposite to the outer circumferential surface 11 of the roller 1. The ball structure 4 is installed on the first end face 31. The ball structure 4 is made of bearing steel with a surface roughness Ra≤0.02μm and a diameter of 3-8mm depending on the compressor displacement to meet the requirements of load-bearing capacity and smooth rolling. Correspondingly, the outer circumferential surface 11 of the roller 1 is machined with a rolling groove 111. The width of the rolling groove 111 is 0.01-0.03 mm larger than the diameter of the ball, and the depth of the groove is 1 / 3-1 / 2 of the diameter of the ball. This ensures that the ball can roll stably along the rolling groove 111, so that a rolling fit is formed between the slide 3 and the roller 1, replacing the traditional line contact sliding fit.

[0073] For example, the groove of the slide 3 is a rectangular groove on the cylinder 5 for guiding the movement of the slide 3.

[0074] For example, after nitriding, the nitrided layer has a thickness of 0.1-0.2 mm and a hardness ≥ HV800.

[0075] Regarding the structural design of the rolling groove 111 The rolling groove 111 is constructed as an arc-shaped groove structure, consisting of two parts: a sliding surface 111A and an arc-shaped surface 111B.

[0076] The groove surface 111A is the bottom surface of the rolling groove 111. It is set with an arc surface that matches the outer circle of the ball. The radius of the arc is 0.005-0.01mm larger than the radius of the ball. This setting can reduce the contact stress when the ball rolls and reduce friction loss. The arc surface 111B is integrally formed on both sides of the groove surface 111A. Along the radial direction of the roller 1, the arc surface 111B protrudes from the groove surface 111A and extends in a direction away from the center of the roller 1. The radius of curvature of the arc surface 111B is consistent with the radius of curvature of the outer circumferential surface 11 of the roller 1, ensuring a smooth transition between the arc surface 111B and the outer circumferential surface 11 of the roller 1 and avoiding eddy current interference when the refrigerant flows.

[0077] The core function of the arc-shaped surface 111B is to form a matching seal with the sliding vane 3: when the sliding vane 3 and the roller 1 are engaged, the arc-shaped surface 111B and the corresponding structure of the first end face 31 of the sliding vane 3 are tightly fitted, and the gap between the mating surfaces is controlled within 0.005-0.01mm, which can effectively prevent the high-pressure refrigerant in the compression chamber from leaking to the low-pressure area; at the same time, the protruding structure of the arc-shaped surface 111B can form a radial limit on the ball, preventing the ball from falling out of the rolling groove 111 and ensuring the stability of the rolling fit.

[0078] Regarding the structural design and sealing fit of the first end face 31 of the sliding plate 3 The first end face 31 of the slide plate 3 is constructed as an arc-shaped mounting surface 31A. The radius of curvature of the arc-shaped mounting surface 31A is the same as the radius of curvature of the outer circumferential surface 11 of the roller 1, ensuring the relative fit between the two and reducing the initial gap. A ball mounting groove 311 is provided in the middle area of ​​the arc-shaped mounting surface 31A. Multiple mounting holes 3111 are arranged at intervals along the length of the slide plate 3 in the ball mounting groove 311. The diameter of the mounting holes 3111 is 0.01-0.02mm larger than the diameter of the ball. Each mounting hole 3111 corresponds to one ball. The spacing between the mounting holes 3111 is 2-3 times the diameter of the ball to avoid interference between adjacent balls when they roll.

[0079] The two sides of the arc-shaped mounting surface 31A are integrally formed with protruding mounting angles 312. The inner surface of the protruding mounting angles 312 is constructed as a first inclined surface structure 3121. Correspondingly, the arc-shaped surface 111B on the roller 1 is constructed as a second inclined surface structure 111B1. When the sliding plate 3 and the roller 1 are engaged, the first inclined surface structure 3121 and the second inclined surface structure 111B1 form a surface contact fit. The contact area is 3-5 times larger than that of the traditional line contact. This not only improves the sealing effect, but also generates radial preload through the interaction force between the inclined surfaces, reducing the risk of separation between the sliding plate 3 and the roller 1 during low-frequency operation.

[0080] For example, the ball mounting groove 311 is a groove that extends through the thickness direction of the slide plate 3.

[0081] For example, the raised mounting angle 312 is a raised structure on both sides of the bottom end of the slider 3.

[0082] For example, the tilt angle of the first inclined structure 3121 is 15°-30°.

[0083] For example, the tilt angle of the second inclined structure 111B1 is the same as the tilt angle of the first inclined structure 3121.

[0084] Optimization of gap control and sealing structure The first gap isolates the chamber: A first gap of 0.01-0.02 mm is left between the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1. This gap is used to prevent direct friction between the arc-shaped mounting surface 31A and the outer circumferential surface 11 of the roller 1 during the reciprocating motion of the vane 3. Since the compression chamber of the rotor compressor is divided into an intake chamber (low-pressure chamber) and an exhaust chamber (high-pressure chamber), if the first gap connects the two chambers, it will cause refrigerant leakage. Therefore, by matching and sealing the arc-shaped surface 111B with the inclined surface of the raised mounting angle 312, the communication path between the exhaust chamber and the intake chamber through the first gap can be completely blocked, ensuring compression efficiency.

[0085] Sealing protection of the ball bearing mounting groove 311: Along the thickness direction of the slide plate 3, sealing structures, i.e., arc-shaped bosses, are protruding from both sides of the ball bearing mounting groove 311. The sealing structures are integrally formed with the slide plate 3, with a height of 0.5-1mm and a width of 1-2mm. Since there is a second gap of 0.01-0.03mm between the ball bearing mounting groove 311 and the outer circumferential surface 11 of the roller 1 to accommodate the rolling of the balls, the sealing structure can cover both ends of the second gap, blocking the second gap from communicating with the exhaust chamber or intake chamber, further preventing refrigerant leakage from the ball bearing mounting groove 311. At the same time, along the thickness direction of the slide plate 3, the thickness of a single sealing structure is ≥10% of the overall thickness of the slide plate 3. For example, when the thickness of the slide plate 3 is 10mm, the thickness of the sealing structure is ≥1mm. This size setting ensures that the sealing structure has sufficient strength and avoids deformation and failure due to vibration and friction during long-term operation.

[0086] In summary, the rotary compressor disclosed herein includes the aforementioned structure in which the vane 3 and roller 1 cooperate, and also includes a cylinder 5, a rotor 2, an intake assembly (intake port, intake chamber) and an exhaust assembly (exhaust port, exhaust chamber). The cylinder 5 is made of gray cast iron, and its inner wall is precision ground to have a contour that matches the outer circumferential surface 11 of the roller 1. The inner ring of the cylinder 5 has an arc-shaped structure, and the radius of curvature of the inner wall of the cylinder 5 is 0.02-0.04 mm larger than the radius of curvature of the outer circumferential surface 11 of the roller 1, ensuring that the roller 1 maintains stable contact with the inner wall of the cylinder 5 when it revolves, while reducing frictional loss.

[0087] Roller 1 is eccentrically mounted inside cylinder 5. The eccentricity (i.e., the distance between the center of rotor 2 and the center of cylinder 5) is set to 2-5mm according to the compressor displacement, providing the necessary volume change space for refrigerant compression. The suction assembly is connected to the suction chamber of cylinder 5 through the suction port, used to draw low-temperature, low-pressure refrigerant into the compression chamber; the exhaust assembly is connected to the exhaust chamber of cylinder 5 through the exhaust port, used to discharge the compressed high-temperature, high-pressure refrigerant. When rotor 2 drives roller 1 to revolve, roller 1 pushes the refrigerant into the suction chamber to complete the suction process. During the revolution, the volume of the compression chamber decreases, achieving refrigerant compression, and finally, it is discharged from the exhaust chamber. Throughout the process, the rolling fit structure between vane 3 and roller 1 reduces friction loss, and the multi-dimensional sealing design reduces leakage, improves volumetric efficiency, and reduces operating noise.

[0088] The air conditioner disclosed herein includes the aforementioned rotary compressor, as well as conventional components such as a condenser, evaporator, throttling device (capillary tube or electronic expansion valve), and fan. The rotary compressor, as the core power component of the air conditioner, is connected to the condenser, evaporator, and throttling device via pipelines to form a refrigerant circulation system: the compressor compresses low-temperature, low-pressure refrigerant vapor into high-temperature, high-pressure vapor, discharges it into the condenser to release heat and condense it into a liquid, then passes through the throttling device to reduce its pressure to a low-temperature, low-pressure liquid, enters the evaporator to absorb heat and evaporate into vapor, and then returns to the compressor to complete the cycle, thus realizing the cooling or heating function of the air conditioner.

[0089] Because rotary compressors offer advantages such as low friction, high sealing, and low risk of separation, air conditioners can achieve higher energy efficiency ratios and lower operating noise. Furthermore, reduced wear on rotary compressor components extends their lifespan, indirectly extending the overall service life of the air conditioner. This type of air conditioner is suitable for various types of household split-type air conditioners, cabinet-type air conditioners, and central air conditioning systems. It ensures cooling or heating efficiency while reducing energy consumption and maintenance costs for users, thus improving the user experience.

[0090] 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.

[0091] 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.

[0092] 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, The sliding vane and roller mating structure includes: 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; A slider, wherein the end of the slider closest to the roller is a first end face; A ball bearing structure is mounted on the first end face; The outer circumferential surface of the roller has a rolling groove, and the ball structure is configured to roll along the rolling groove. The slide and the roller form a rolling fit relationship through the ball structure.

2. The sliding plate and roller mating structure according to claim 1, characterized in that, The rolling groove is an arc-shaped groove structure formed on the outer circumferential surface of the roller. The arc-shaped groove structure includes a groove surface located on the bottom surface and an arc-shaped surface connected to both sides of the groove surface. Along the radial direction of the roller, the arc-shaped surface protrudes from the groove surface and is arranged in a direction away from the center of the roller. The groove surface is used for rolling engagement with the ball structure, and the arc-shaped surface is used for matching and sealing with the slide plate.

3. The sliding plate and roller mating structure according to claim 2, characterized in that, The first end face of the slide is constructed as an arc-shaped mounting surface. The central region of the arc-shaped mounting surface has a ball bearing mounting groove, and both sides of the arc-shaped mounting surface have raised mounting angles. The inner surface of the raised mounting angles is used to match and seal with the arc-shaped surface.

4. The sliding plate and roller mating structure according to claim 3, characterized in that, A first gap is left between the arc-shaped mounting surface and the outer circumferential surface of the roller. The rotor compressor includes an intake chamber and an exhaust chamber. The matching seal between the arc-shaped surface and the protruding mounting angle is used to prevent the exhaust chamber and the intake chamber from establishing a communication relationship through the first gap.

5. The sliding plate and roller mating structure according to claim 3, characterized in that, The ball bearing mounting groove is a groove structure formed on the arc-shaped mounting surface along the thickness direction of the slide plate. Multiple mounting holes are spaced apart in the groove structure, and each mounting hole is used to install one ball bearing structure.

6. The sliding plate and roller mating structure according to claim 5, characterized in that, Along the thickness direction of the slide, sealing structures are provided on both sides of the ball mounting groove. A second gap is left between the groove structure and the outer circumferential surface of the roller. The sealing structure is used to prevent the second gap from communicating with the exhaust chamber or the intake chamber.

7. The sliding plate and roller mating structure according to claim 6, characterized in that, Along the thickness direction of the slide, the thickness dimension of a single sealing structure is greater than or equal to 10% of the overall thickness dimension of the slide.

8. The sliding plate and roller mating structure according to claim 3, characterized in that, The inner surface of the protruding mounting angle is constructed as a first inclined surface structure, and the arc-shaped surface on the roller has a second inclined surface structure that matches and seals with the inclined surface structure.

9. A rotary compressor, characterized in that, The device includes the sliding vane and roller mating structure as described in any one of claims 1-8, and further includes a cylinder, wherein the roller is eccentrically mounted inside the cylinder, and the inner wall of the cylinder has a profile that matches the outer circumferential surface of the roller.

10. An air conditioner, characterized in that, Including the rotary compressor as described in claim 9.

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