Pump body assembly, compressor and refrigeration device

Abstract

This invention discloses a pump body assembly, a compressor, and a refrigeration device, relating to the field of compressor technology. The pump body assembly includes a cylinder body, rollers, and vanes. The cylinder body includes a working chamber and a vane groove. The rollers are housed within the working chamber, and their outer peripheral walls have axially extending mating cavities. The vane body is slidably disposed in the vane groove. The vane head is housed within the mating cavity and forms a surface contact with the cavity. A mating portion is formed at the groove opening of the mating cavity to mate with a transition recess. The vane head includes a second arc segment and first and third arc segments located on either side of the second arc segment. A lubrication channel is formed between the second arc segment and the mating cavity. The rollers drive the vane to perform radial reciprocating motion within the vane groove. The technical solution provided by this invention aims to solve problems such as poor sealing and low reliability in traditional structures, thereby improving the compressor's energy efficiency, lifespan, and operating performance.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a pump assembly, a compressor, and a refrigeration device. Background Technology

[0002] Rotary compressors are widely used in household air conditioners, heat pumps, and refrigeration equipment due to their compact structure, stable operation, and high energy efficiency. Their core working components typically include a cylinder, a piston (also called a roller) eccentrically mounted on a crankshaft, and vanes that slide radially within the cylinder's vane slots. The vanes, in conjunction with the piston, divide the cylinder's internal cavity into an intake chamber and a compression chamber, achieving the intake, compression, and discharge of refrigerant through volume changes.

[0003] In traditional structures, the vane is typically a straight line or a single-segment arc head, and a return spring located at the tail of the vane presses it against the outer surface of the piston to maintain a sealed contact. However, the contact between the vane and the piston is mostly line contact or point contact, with a small contact area. Under long-term operation or high-load conditions, wear and deformation can easily lead to seal failure, causing cross-flow between high and low pressure chambers, reducing volumetric efficiency and system energy efficiency ratio (COP).

[0004] Secondly, the traditional structure uses springs to keep the vane in contact with the rollers: at low frequencies, insufficient spring force can easily cause the vane to disengage from the piston, resulting in impact noise; at high frequencies, the spring response is lagging, which may cause resonance or fatigue fracture, limiting the compressor's wide frequency adaptability. Summary of the Invention

[0005] The main objective of this invention is to propose a pump assembly, a compressor, and a refrigeration device, which aims to solve problems such as poor sealing and low reliability in traditional structures, thereby improving the energy efficiency, lifespan, and operating performance of the compressor.

[0006] To achieve the above objectives, the pump assembly proposed in this invention includes: The cylinder body includes a working chamber and a sliding vane groove that communicates with the working chamber and extends radially along the cylinder body; A roller, housed within the working cavity, has an axially extending mating cavity on its outer peripheral wall; and A slider includes a slider body, a slider head, and a transition recess connecting the slider head and the slider body. The slider body is slidably disposed in the slider groove. The slider head is accommodated in the mating cavity. A mating portion that mates with the transition recess is formed at the groove opening of the mating cavity. The slide head includes a second arc segment and a first arc segment and a third arc segment located on both sides of the second arc segment; a lubrication channel is formed between the second arc segment and the mating cavity; The radius of the first arc segment is r1, the radius of the second arc segment is r2, and the radius of the third arc segment is r3. The angle between the two lines connecting the two ends of the second arc segment to the center of the first or third arc segment is α; satisfying the relationship: ; and .

[0007] In one embodiment, the width of the slider body is T. .

[0008] In one embodiment, the width of the slider body is T. .

[0009] In one implementation, 45° ≤ α < 120°.

[0010] In one implementation, r2>r1, r2>r3.

[0011] In one embodiment, the first arc segment and the third arc segment are symmetrically arranged on both sides of the second arc segment.

[0012] In one embodiment, the first arc segment and the first arc segment have the same radius.

[0013] In one embodiment, the groove width of the mating cavity is t, which satisfies... .

[0014] In one embodiment, the width of the slider body is T, and the minimum thickness of the transition recess is b, satisfying: 0.594≤b / T≤0.642.

[0015] The present invention also proposes a compressor comprising a pump assembly as described in any of the preceding embodiments.

[0016] The present invention also proposes a refrigeration device, including the compressor described above.

[0017] The technical solution of this invention solves the technical problems of traditional rotary compressors, such as poor sealing due to line contact between the vane and the roller, low-frequency disengagement or high-frequency vibration caused by reliance on spring reset, and oil leakage and heat exchange loss caused by free rotation of the roller. It also addresses these problems by setting a composite curved surface composed of a first, second, and third arc segment at the vane head and embedding it into the superior arc-shaped mating cavity of the roller. Simultaneously, a transition recess is provided between the vane head and the vane body, and the mating part formed at the groove of the mating cavity maintains a clearance fit during dynamic operation. Specifically, during compressor operation, the lubrication channel formed between the second arc segment and the mating cavity effectively establishes a hydrodynamic oil film, reducing friction and wear and suppressing mechanical noise caused by dry friction. Meanwhile, the first and third arc segments on either side, constrained by the aforementioned formula, maintain a minimal sealing gap of less than 0.12mm with the mating cavity, effectively preventing refrigerant leakage between the high and low pressure chambers and improving volumetric efficiency. This structure achieves stable sealing and lubrication without relying on additional components such as springs, simplifying the pump assembly structure, reducing manufacturing costs, and expanding the reliable operating range of the compressor under different conditions such as low-speed start-up and high-frequency operation. It also effectively mitigates the risk of jamming caused by thermal deformation or impurity intrusion, ensuring long-term efficient and quiet system operation. More importantly, the rollers are confined within the mating cavity, only allowing limited oscillation and preventing free rotation, effectively isolating the heat conduction path between the high-temperature, high-pressure zone and the low-temperature, low-pressure zone, significantly reducing cooling loss. Simultaneously, it blocks the channel for lubricating oil to surge from the high-pressure side to the low-pressure side, fundamentally suppressing the "oil leakage" phenomenon and ensuring lubrication stability. Even if minor wear occurs on the sliding vane or mating cavity surface due to long-term operation, the system can still maintain smooth movement without jamming because a reasonable dynamic clearance is reserved between the transition recess and the mating part, ensuring reliable operation of the compressor throughout its entire life cycle. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of a pump body assembly according to an embodiment of the present invention; Figure 2 A schematic diagram of the pump body assembly provided by the present invention from another perspective; Figure 3 for Figure 2A magnified view of a section at point A in the middle; Figure 4 for Figure 1 A schematic diagram of the structure of one embodiment of the cylinder body; Figure 5 for Figure 1 A schematic diagram of the structure of an embodiment of the sliding plate; Figure 6 for Figure 5 A schematic diagram of the middle slider from another perspective; Figure 7 for Figure 5 A schematic diagram of the middle slider from another perspective; Figure 8 for Figure 7 A magnified view of the head of the middle slider; Figure 9 This is a graph showing the relationship between the wear of the slide head and the geometric constraint parameters.

[0020] Explanation of icon numbers: 100. Cylinder body; 110. Working chamber; 120. Sliding vane groove; 200, Roller; 210, Mating cavity; 220, Mating part; 230, Lubrication channel; 300, slider; 310, slider body; 320, slider head; 321, second arc segment; 322, first arc segment; 323, third arc segment; 330, transition recess.

[0021] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0022] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0023] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0024] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0025] This invention proposes a pump assembly, a compressor, and a refrigeration device.

[0026] Please see Figures 1 to 8 In one embodiment of the present invention, the pump body assembly includes a cylinder body 100, a roller 200, and a vane 300. The cylinder body 100 includes a working chamber 110 and a vane groove 120 extending radially along the cylinder body 100 and communicating with the working chamber 110. The roller 200 is housed within the working chamber 110, and the outer peripheral wall of the roller 200 is provided with a mating cavity 210 extending axially. The cross-section of the mating cavity 210 is an arc shape with its opening facing the inner wall of the working chamber 110. The vane 300 includes a vane body 310, a vane head 320, and a transition recess 330 connecting the vane head 320 and the vane body 310. The vane body 310 is slidably disposed in the vane groove 120. The groove opening of the mating cavity 210 forms a transition recess 330 with the vane body 300. The mating part 220 mates with the recessed part 330; wherein, the slide head 320 includes a second arc segment 321 located in the radial center region of the slide 300, and a first arc segment 322 and a second arc segment 321 located on both sides of the second arc segment 321; the radius of the first arc segment 322 is r1, the radius of the second arc segment 321 is r2, the radius of the third arc segment 323 is r3, and the center angle of the second arc segment 321 in the slide head 320 is α; during operation, the roller 200 drives the slide 300 to perform radial reciprocating motion within the slide groove 120 through eccentric rotation; and satisfies the relationship ;and .

[0027] The roller 200, which is the eccentric piston in the compressor, is cylindrical and fitted onto the eccentric journal of the crankshaft, housed within the working chamber 110, and moves within the working chamber 110 as the crankshaft rotates. The mating cavity 210 is formed on the outer peripheral wall of the roller 200 (i.e., the cylindrical surface opposite the inner wall of the working chamber 110), axially extending completely through both ends of the roller 200, forming a channel that runs the entire working length. In a cross-section perpendicular to the axis of the roller 200, the profile of the mating cavity 210 is a superior arc, i.e., an arc segment with a central angle greater than 180°. The width of the groove in the mating cavity 210 is the straight-line distance between the two endpoints of the superior arc, i.e., the minimum lateral width at the opening of the mating cavity 210, which is the channel size through which the transition recess 330 of the vane 300 passes. When the roller 200 rotates, the sidewall of the mating cavity 210 directly pushes the vane head 320, driving the vane 300 to reciprocate within the vane groove 120 without the need for a spring. Traditional rollers 200 can rotate freely around their own axis, causing heat conduction between the high-temperature and low-temperature zones through the metal body, and triggering lubricating oil to surge from the high-pressure side to the low-pressure side (oil leakage). In this design, after the sliding vane head 320 is embedded in the mating cavity 210, it physically prevents the roller 200 from rotating circumferentially, allowing it only to oscillate slightly relative to the sliding vane 300, thereby isolating the high and low temperature zones and reducing cold loss; it also blocks the abrupt oil migration path and suppresses oil leakage. Furthermore, the superior arc wrap angle >180° allows the sliding vane head 320 to form a continuous, wide surface contact with the inner wall of the mating cavity 210 (instead of the traditional line contact); and under the action of gas pressure and centrifugal force, the contact surface automatically presses together, and the sealing performance increases with the increase of the pressure difference (self-reinforcing sealing effect).

[0028] The vane body 310 has a rectangular or approximately rectangular cross-section; it is slidably disposed in the radial vane groove 120 of the cylinder body 100; the vane head 320 is located at the front end of the vane 300 and directly contacts the roller 200; its outer contour is an arc shape (wrap angle > 180°), and its radius of curvature matches the mating cavity 210 of the roller 200; the vane head 320 includes a first arc segment 322, a second arc segment 321, and a third arc segment 323, the second arc segment 321 is located at the radial centerline of the vane 300, and its central angle is α; the first arc segment 322 and the third arc segment 323 are distributed on both sides of the second arc segment 321, together forming a complete arc surface. During operation, it is completely contained within the mating cavity 210 of the roller 200, forming a continuous surface contact with the inner wall of the mating cavity 210 to achieve high-pressure sealing and force transmission.

[0029] Reference Figure 3The second arc segment 321 forms a lubrication channel 230 between itself and the mating cavity 210. This design allows the slide head 320 to preferentially contact and bear pressure with the side wall of the mating cavity 210 during the process of embedding into the mating cavity 210 of the roller 200, with the second arc segment 322 and the third arc segment 323 on both sides. The second arc segment 321 serves as a transition zone, gradually conforming to the bottom of the mating cavity 210 during subsequent loading, avoiding local stress concentration or impact damage caused by instantaneous high pressure. The slide head 320 is generally curved, but the curvature of the second arc segment 321 at the bottom is smaller, making it more "flat"; the curvature of the first arc segment 322 and the third arc segment 323 on both sides is larger, making them more "rounded". The center of the second arc segment 322 is between the slide head 320 and the first arc segment 322 or the third arc segment 323. The radius of the second arc segment 322 is larger than that of the first arc segment 321 and the third arc segment 323. That is, through parameter constraints, a small gap is formed between the first arc segment 322 and the third arc segment 323 and the mating cavity 210, while a lubrication channel 230 is formed between the second arc segment 321 and the mating cavity 210.

[0030] Combination Figure 3 and Figure 8 The slide head 320 is formed as a continuous and smooth composite curved surface profile. Its outer edge is formed by connecting the first arc segment 322, the second arc segment 321, and the third arc segment 323 in sequence. At each of the three arc segments, there is a circle with a minimum diameter that is tangent to the outer contour of the slide head 320 and surrounds its entire geometric boundary. This minimum circumscribed circle is shown as a dashed line in the figure (the diameter of the minimum circumscribed circle is approximately the inner diameter of the slide head 320). In other words, the center of curvature of the second arc segment 321 is smaller than that of the minimum circumscribed circle. The centers of the first arc segment 322 and the third arc segment 323 coincide or approximately coincide with the center of the minimum circumscribed circle. Combined with the formula constraints, it is ensured that the slide 300 forms a controllable circumferential gap distribution between itself and the inner wall of the roller 200 in the assembled state, while providing a geometric reference for the subsequent lubrication cavity 230.

[0031] The transition recess 330 is located between the slider head 320 and the slider body 310, and is a concave neck structure. It connects the slider head 320 and the slider body 310 through a smooth curved surface in the direction perpendicular to the movement direction of the slider 300 (i.e., the transverse direction) to relieve stress concentration. Its geometry corresponds to the mating part 220 of the mating cavity 210 of the roller 200. The mating part 220 refers to the edge area of ​​the groove of the mating cavity 210 of the roller 200. In this embodiment, it is composed of two parallel straight sections and inclined flared sections at both ends. During the operation of the compressor, the crankshaft drives the roller 200 to rotate eccentrically. The side wall of the mating cavity 210 of the roller 200 directly pushes the vane head 320. The vane 300 moves radially back and forth in the vane groove 120. During this process, the arc surface of the vane head 320 is tightly fitted with the inner wall of the mating cavity 210 of the roller 200. Under the action of gas pressure and centrifugal force, it is automatically pressed together to form a self-reinforcing surface seal, which effectively blocks the refrigerant leakage between the high and low pressure cavities. Because the slider head 320 is constrained within the mating cavity 210, the roller 200 cannot rotate freely around its own axis, but can only oscillate relative to the slider 300 at a limited angle. During this oscillation, the transition recess 330 and the mating part 220 always maintain a non-contact but adjacent state (dynamic fit) to compensate for manufacturing tolerances and thermal expansion, absorb high-frequency vibrations, and avoid edge stress concentration or fretting wear caused by rigid constraints. Through the constraints of the above formula, the slider 300 and the roller 200 have oscillating freedom, retaining assembly tolerances, while the rotational freedom is suppressed, thus balancing reliability and functionality.

[0032] The technical solution of the present invention solves the technical problems of traditional rotary compressors, such as poor sealing caused by line contact between the vane 300 and the roller 200, low-frequency disengagement or high-frequency vibration caused by reliance on spring reset, and oil leakage and heat exchange loss caused by free rotation of the roller 200, by setting a composite curved surface composed of a first arc segment 322, a second arc segment 321 and a third arc segment 323 in the vane head 320 and embedding it into the superior arc-shaped mating cavity 210. At the same time, a transition recess 330 is set between the vane head 320 and the vane body 310, and the mating part 220 formed at the groove of the mating cavity 210 maintains clearance fit during dynamic operation. At the same time, the geometric relationship between the radius of each arc segment (r1, r2, r3) and the corresponding central angle α of the second arc segment 321 is constrained. Specifically, during compressor operation, the lubrication channel 230 formed between the second arc segment 321 and the mating cavity 210 effectively establishes a hydrodynamic oil film, reducing friction and wear and suppressing mechanical noise caused by dry friction. Meanwhile, the first arc segment 322 and the third arc segment 323, located on both sides, maintain a minimal sealing gap of less than 0.12 mm with the mating cavity 210 under the constraints of the aforementioned formula, effectively preventing refrigerant leakage between the high and low pressure cavities and improving volumetric efficiency. This structure achieves stable sealing and lubrication without relying on additional components such as springs, simplifying the pump assembly structure, reducing manufacturing costs, and expanding the reliable operating range of the compressor under different conditions such as low-speed start-up and high-frequency operation. It also effectively mitigates the risk of jamming caused by thermal deformation or impurity intrusion, ensuring long-term efficient and quiet system operation. Furthermore, because the vane head 320 has a wrap angle greater than 180° and forms continuous surface contact with the mating cavity 210, it maintains stable sealing performance regardless of operating frequency, reducing cross-contamination between high and low pressure cavities and improving volumetric efficiency and system energy efficiency ratio. More importantly, the roller 200 is confined within the mating cavity 210, allowing only limited oscillation and preventing free rotation. This effectively isolates the heat transfer path between the high-temperature, high-pressure zone and the low-temperature, low-pressure zone, significantly reducing cooling loss. Simultaneously, it blocks the path for lubricating oil to surge from the high-pressure side to the low-pressure side, fundamentally suppressing "oil leakage" and ensuring lubrication stability. Even with minor wear on the surfaces of the vane 300 or the mating cavity 210 due to long-term operation, the system maintains smooth operation without jamming because of the reasonable dynamic clearance between the transition recess 330 and the mating part 220, ensuring reliable compressor operation throughout its entire lifespan.

[0033] The above formula is for dimensionless calculations.

[0034] Regarding parameter definition: r1 is the radius of the first arc segment 322 (in mm), and r3 is the radius of the third arc segment 323 (in mm). These values ​​can be obtained by fitting the curvature of the inner wall of the mating cavity 210 using an optical profilometer.

[0035] The radius of the second arc segment 321, r2, can be obtained by fitting the curvature of the inner wall of the mating cavity 210 using an optical profilometer. The smaller r2 is, the larger the volume of the lubrication cavity 230; the larger r2 is, the narrower the cavity.

[0036] α is the central angle corresponding to the second arc segment 321 (in degrees), which can be measured as the angle between the two endpoints of the second arc segment 321 and the center of the slider head 320. The larger α is, the longer the second arc segment 321 is and the wider the opening of the lubrication cavity 230.

[0037] It is to calculate and control the local radial clearance between the junction of the first arc segment 322 and the second arc segment 321 of the slider head 320 and the contour of the mating cavity 210 of the roller 200.

[0038] The second arc segment 321 determines the shape and size of the lubrication channel 230 formed between it and the mating cavity 210, achieving hydrodynamic lubrication. The first arc segment 322 and the third arc segment 323 are located on both sides of the second arc segment 321, forming a sealing pair with the two ends of the mating cavity 210 of the roller 200. They need to fit tightly with the roller 200 to prevent leakage, but they cannot be completely sealed, otherwise they may jam due to thermal expansion or manufacturing errors.

[0039] A clearance greater than 0 ensures a positive clearance, preventing parts from jamming due to thermal expansion or manufacturing tolerances, and providing space for lubricating oil. A clearance less than 0.12 strictly limits the clearance to a very small range to ensure minimal gas leakage and maintain high compressor efficiency.

[0040] When the constraint is in the range of 0-0.12, the lubrication cavity 230 is in the optimal range. It can retain enough refrigerant oil to form a continuous oil film, providing sufficient lubrication for the articulated joint and reducing friction and wear. At the same time, it can allow excess oil to be slowly discharged through the crescent-shaped cavity during compression, without forming a closed cavity that would cause oil compression. Meanwhile, the amount of refrigerant leakage can be controlled, and its impact on volumetric efficiency is negligible.

[0041] Similarly, This is the local radial clearance between the other side of the slide head 320 (the junction of the third arc segment 323 and the second arc segment 321) and the mating cavity 210 of the roller 200.

[0042] A clearance greater than 0 ensures a positive clearance, preventing parts from jamming due to thermal expansion or manufacturing tolerances, and providing space for lubricating oil. A clearance less than 0.12 strictly limits the clearance to a very small range to ensure minimal gas leakage and maintain high compressor efficiency.

[0043] By quantifying the minimum gap of the second arc segment 321, when the sliding head 320 of the sliding vane 300 is embedded in the mating cavity 210, a crescent-shaped lubrication channel 230 is formed between the three arc segments and the mating cavity 210. The oil on the high-pressure side reaches this point through the gap between the sliding head 320 and the mating cavity 210. The dimensional pressure is a medium pressure between high and low pressure, which is still lower than the low pressure on the suction side. The oil in the lubrication channel 230 can still move through the gap between the sliding head 320 and the mating cavity 210 until it moves to the suction side, where the oil circuit participates in lubrication again, improving the lubrication efficiency of the refrigeration oil and solving the oil compression problem at the end of the compression of the articulated structure.

[0044] Figure 9 The graph shows the relationship between the wear of the slider head and the geometric constraint parameter. The graph clearly shows that when the parameter is in the range of 0–0.12 (especially 0.05–0.09 is the optimal range), the wear of the slider remains at a low level (1.0–2.5 μm), demonstrating excellent wear resistance; while when the parameter is >0.12, the wear increases sharply.

[0045] Thus, those skilled in the art can rationally select the material of the vane 300 and design its head geometry parameters (r1, r2, r3 and α) according to the target operating conditions (such as refrigerant type, compressor speed, displacement and working pressure range), and substitute them into the above clearance constraint formula for calculation; as long as the calculated radial clearance value falls within the range of (0, 0.12) mm, it is possible to ensure a stable micro-gap seal and effective hydrodynamic lubrication between the vane 300 and the roller 200 without changing the basic structural form of the vane 300 and the layout of the mating cavity 210 of the roller 200, thereby reducing frictional power consumption and mechanical noise, suppressing start-up jamming and running wear, and improving the compressor's volumetric efficiency, reliability and service life.

[0046] The roller 200 has an axially through-hole 210 on its outer periphery, with a cross-section that is an inwardly opening arc shape. The 210 serves as the receiving space for the slide head 320. The slide 300 consists of a slide body 310, a slide head 320 (including a first arc segment 322 / a third arc segment 323 + a second arc segment 321), and a transition recess 330. The slide head 320 is embedded in the 210 to achieve surface contact. The transition recess 330 is dynamically adapted to the groove 220 of the 210.

[0047] The vane head 320 has an arc greater than 180°, which fits extensively with the inner wall of the mating cavity 210 of the roller 200, forming a surface contact seal. This increases the sealing length and contact area, reduces leakage in the high and low pressure cavities, and solves the problem of poor sealing (air leakage). At the same time, the vane head 320 automatically presses tightly against the mating cavity 210 under the action of gas pressure and centrifugal force, forming a self-reinforcing seal. When the roller 200 rotates eccentrically, it directly pushes the vane head 320 through the side wall of the mating cavity 210, causing the vane 300 to reciprocate in the vane groove 120 without the need for a spring. The vane head 320 is constrained within the mating cavity 210, and the roller 200 can only swing relative to the vane 300 to a limited extent (it cannot rotate freely), suppressing heat exchange and oil leakage. A reasonable gap is maintained between the transition recess 330 and the mating part 220 of the mating cavity 210, allowing the roller 200 to swing slightly without jamming.

[0048] Reference Figures 6 to 8 Furthermore, to achieve lightweight design while ensuring structural strength, the width of the slider body 310 in the radial direction perpendicular to the slider 300 is T. In traditional designs, the width T of the slider body is often selected based on experience, which leads to either redundant strength (T is too large, resulting in material waste) or insufficient strength (T is too small, resulting in decreased reliability).

[0049] The gas pressure and friction force experienced by the slider head 320 within the mating cavity 210 need to be transmitted to the slider body 310 through the transition recess 330. When At this time, the width of the slider body 310 is sufficient to cover the effective load distribution area of ​​the slider head 320, avoiding stress accumulation in local areas. This avoids material waste caused by over-design and achieves lightweighting while meeting strength requirements.

[0050] Reference Figures 6 to 8 Furthermore, the width of the slider body 310 in the radial direction perpendicular to the slider 300 is T. The slider 300 needs to reciprocate at high frequency within the slider groove 120 during operation. If the width T of the slider body 310 is close to or exceeds 2... If r2 is smaller than the projection range of the effective working area of ​​the slider head 320, then its physical size exceeds the projection range of the slider head 320, resulting in material redundancy. The width of the slider body 310 is smaller than the projection of the diameter of the central area (second arc segment 321) of the slider head 320; sufficient clearance is reserved for the slider 300 to swing slightly and thermally expand in the groove, so that the lubricating oil can flow smoothly along both sides of the groove wall to form a complete oil film.

[0051] Specifically, the first arc segment 322 and / or the third arc segment 323 form a surface contact fit with the mating cavity 210.

[0052] The vane 300 is connected to the roller 200 through the mating cavity 210 of the vane head 320. Therefore, there is no need to set a spring hole and spring in the cylinder, which reduces the manufacturing cost and difficulty of the cylinder. In addition, the vane head 320 adopts a multi-segment arc design, which improves the machinability and reduces stress concentration, significantly improving wear resistance. The line contact between the vane 300 and the piston is improved to a surface contact, reducing the possibility of air leakage from the exhaust side to the intake side, which greatly improves the operating efficiency of the compressor. The force for the movement of the vane 300 is ultimately provided by the motor. The force provided by the motor can be varied by the frequency, which solves the risk of the vane 300 detaching from the piston due to high-speed operation. In addition, since the piston and the vane 300 only rotate relative to the mating cavity 210, the mating cavity 210 separates the high-temperature and high-pressure area on the piston surface, solving the problems of decreased cooling capacity, increased intake force, and increased oil discharge caused by piston rotation.

[0053] Combination Figure 3 , Figure 6 as well as Figure 8 Specifically, 45°≤α<120°, the first arc segment 322 and the third arc segment 323 are the contact surfaces of the actual compressor operation and the mating cavity 210 of the roller 200. The second arc segment 322 and the mating cavity 210 form a lubrication channel 230, which can form an oil film to enhance lubrication. If α is too small, the oil film will have limited lubrication effect. If α is too large, it will compress the contact area between the vane head 320 and the mating cavity 210, resulting in increased surface pressure and decreased reliability.

[0054] Specifically, when α < 45°, the wrap angle of the second arc segment 321 is too small, resulting in insufficient length of the lubrication channel 230 (wedge-shaped convergent gap) region formed between it and the mating cavity 210 of the roller 200. This makes it difficult to establish a stable and continuous hydrodynamic oil film during the high-speed reciprocating motion of the slide 300. This weakens the self-lubricating ability, increases the risk of dry friction or boundary lubrication, and thus exacerbates wear and generates mechanical noise, failing to fully utilize the advantages of the composite surface in reducing frictional power consumption.

[0055] Conversely, when α ≥ 120°, although the central lubrication area widens, which is beneficial for oil film formation, it excessively compresses the effective contact arc length of the first arc segment 322 and the third arc segment 323. Since r1 and r3 are the key sealing surfaces that directly contact the roller 200 and bear the load during actual operation, a reduction in their contact area will lead to an increase in local surface pressure (contact stress per unit area). Under high load, high temperature, or impurity conditions, this can easily cause micropitting, galling, or even local plastic deformation, affecting the structural strength and long-term operational reliability of the sliding vane 300 and roller 200 pair.

[0056] Specifically, 45°≤α≤90°. For example, the included angle α can take the following values: , , , , , , , , , Of course, it can also be any other value within the above interval.

[0057] By limiting α to the above range, it is ensured that the second arc segment 321 has sufficient length to form an effective hydrodynamic wedge oil film, achieving low friction and low wear self-lubricating operation; sufficient contact arc length is reserved for the first arc segment 322 and the third arc segment 323 on both sides, effectively dispersing contact stress and avoiding local high pressure failure under the premise of meeting micro-gap sealing (<0.12 mm).

[0058] Specifically, r2>r1, r2>r3. The slider head 320 is composed of three arc-shaped segments, which optimizes the contact and movement trajectory of the slider head 320 within the mating cavity 210. The three arc segments have different radii of curvature, and the second arc segment 321 forms a gradually changing lubrication channel 230 between itself and the inner wall of the mating cavity 210. This forms a principle similar to that of a tilting pad bearing, but transforms the tilting capability into a fixed multi-stage wedge-shaped oil film. When the slider head 320 oscillates within the mating cavity 210, the second arc segment 321 first constructs a large-angle converging wedge in the inlet area, generating a strong pumping effect on the lubricating oil, forcing the lubricating oil into the friction interface, enhancing lubrication, and improving reliability. Oil from the high-pressure side reaches this point through the gap between the vane head 320 and the mating cavity 210. The pressure is medium, between high and low pressure, and still lower than the low pressure on the suction side. Oil in the lubrication channel 230 can still move through the gap between the vane head 320 and the mating cavity 210 until it reaches the suction side. The oil circuit participates in lubrication again, improving the lubrication efficiency of the refrigeration oil and solving the oil compression problem at the end of the compression in the articulated structure.

[0059] Specifically, the first arc segment 322 and the third arc segment 323 have the same radius.

[0060] Specifically, the radial centerline of the vane 300 bisects the second arc segment 321, and the first arc segment 322 and the second arc segment 323 are symmetrical about the radial centerline of the vane 300. This symmetrical arrangement ensures that after the vane head 320 is embedded in the mating cavity 210 of the roller 200, the force is evenly distributed along the radial centerline CL, avoiding unilateral wear or tilting jamming caused by geometric eccentricity. Since the vane 300 is subjected to alternating gas pressure and inertial load during compressor operation, the symmetrical layout effectively balances the stress on both sides, improving motion stability and sealing consistency. Simultaneously, this symmetry provides a technological basis for synchronous grinding with dual contour grinding wheels. Specifically, the first arc segment 322 and the second arc segment 323 are synchronously ground by two symmetrically arranged contour grinding wheels. The two grinding wheels can feed symmetrically along the radial centerline, completing the high-precision forming of the first arc segment 322 and the second arc segment 323 in one pass, improving production efficiency and contour consistency. Simultaneous machining with dual contour grinding wheels not only improves production efficiency but also ensures the symmetry and contour accuracy of the two side arcs, reduces subsequent assembly deviations, and enhances the sealing performance and smoothness of the vane-piston fit.

[0061] It should be noted that, due to factors such as equipment precision limitations, grinding wheel wear, or clamping errors in the actual processing, there may be slight differences in the curvature radii of the first arc segment 322 and the second arc segment 323 within a certain range (for example, the deviation does not exceed ±0.05mm). This difference does not affect the overall function of the slide plate, nor does it damage the dynamic fit performance with the roller mating cavity.

[0062] Furthermore, the width of the slider body 310 is T, and the minimum thickness of the transition recess 330 is b, satisfying: 0.594≤b / T≤0.642.

[0063] In one embodiment, the minimum thickness b of the transition recess 330 and the thickness T of the slider body 310 satisfy (T and b are both in mm): 0.594 ≤ b / T ≤ 0.642. This ensures the structural strength of the slider head 320 and guarantees the bending and fatigue strength of the slider during operation. This ratio can be 0.6, 0.61, 0.62, 0.63, 0.64, etc. In other embodiments, this ratio can also be 0.58, 0.59, 0.65, 0.66, etc.

[0064] In one embodiment, the slot width t of the mating cavity 210 satisfies Specifically, the groove of the mating cavity 210 is located on the outer peripheral wall of the roller 200. The groove width t is the minimum radial dimension at the opening of the mating cavity 210, which directly determines the structural strength of the mating cavity 210 and the stability of the hinged fit. When t < 2.0 mm, the groove of the mating cavity 210 is too narrow, which not only greatly increases the difficulty of CNC machining, but also leads to stress concentration at the groove position of the roller 200, which is prone to cracking failure under long-term high load operation. When t > 5.5 mm, the opening of the mating cavity 210 is too large, and the sliding head 320 of the slide 300 is prone to dislodging from the groove.

[0065] In this embodiment, t is limited to the range of 2.0mm to 5.5mm. Conventional machining dimensions such as t=2.0mm, 3.0mm, 4.0mm, 5.0mm, and 5.5mm can be selected, which can not only ensure the structural strength of the groove of the mating cavity 210 and avoid stress cracking, but also ensure the stable hinge fit between the slider head 320 and the mating cavity 210, preventing the slider 300 from separating from the roller 200. At the same time, it is compatible with the machining process of ordinary lathes and grinding machines, reducing production and manufacturing costs.

[0066] This invention also proposes a compressor, which includes a pump body assembly and other necessary components that work in conjunction with it. The specific structure of the pump body assembly is as described in the above embodiments. Since this compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, and will not be described in detail here. Among them, other necessary components typically include a crankshaft, a motor assembly, a housing, and a lubrication system, etc.

[0067] During operation, the motor drives the crankshaft to rotate, causing the roller 200 to roll eccentrically within the working chamber 110. The roller 200 directly pushes the vane head 320 through the side wall of its mating cavity 210, causing the vane 300 to reciprocate radially within the vane groove 120, rather than being connected by spring force. Therefore, there is no need to install spring holes and springs in the cylinder, reducing the cylinder's manufacturing cost and difficulty. The vane 300 and roller 200 divide the working chamber 110 into an intake chamber and a compression chamber. As the roller 200 rotates, the volume of the compression chamber decreases periodically, realizing the intake, compression, and discharge of refrigerant. Because the vane head 320 and the mating cavity 210 of the roller 200 form surface contact, and the roller 200 is restricted to limited oscillation (cannot rotate freely), the possibility of leakage from the exhaust side to the intake side is reduced, thus improving the compressor's operating efficiency. The force driving the movement of the slide 300 is ultimately provided by the motor. The force provided by the motor can vary with frequency, thus mitigating the risk of the slide 300 detaching from the roller 200 due to high-speed operation. Since the roller 200 and slide 300 only rotate relative to each other within the mating cavity 210, the cavity separates the high-temperature, high-pressure areas on the surface of the roller 200, solving the problems of decreased cooling, increased input force, and increased oil discharge caused by the roller 200's rotation. The slide head 320 adopts a multi-segment arc design, which improves machinability while reducing stress concentration and enhancing wear resistance.

[0068] This compressor can also be used in refrigeration equipment, including but not limited to household / commercial inverter air conditioners, cold chain logistics refrigeration systems, and electric vehicle refrigeration equipment.

[0069] The above are merely exemplary embodiments of the present invention and do not limit the scope of the patent of the present invention. All equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the scope of patent protection of the present invention.

Claims

1. A pump body assembly, characterized in that, include: The cylinder body includes a working chamber and a sliding vane groove that communicates with the working chamber and extends radially along the cylinder body; A roller, housed within the working cavity, has an axially extending mating cavity on its outer peripheral wall; and A slider includes a slider body, a slider head, and a transition recess connecting the slider head and the slider body. The slider body is slidably disposed in the slider groove. The slider head is accommodated in the mating cavity. A mating portion that mates with the transition recess is formed at the groove opening of the mating cavity. The slide head includes a second arc segment and a first arc segment and a third arc segment located on both sides of the second arc segment; a lubrication channel is formed between the second arc segment and the mating cavity; The radius of the first arc segment is r1, the radius of the second arc segment is r2, and the radius of the third arc segment is r3. The angle between the two lines connecting the two ends of the second arc segment to the center of the first or third arc segment is α; satisfying the relationship: ； and .

2. The pump body assembly as claimed in claim 1, characterized in that, The width of the slider body is T. .

3. The pump body assembly as claimed in claim 1, characterized in that, The width of the slider body is T. .

4. The pump body assembly as claimed in claim 1, characterized in that, 45°≤α＜120°。 5. The pump body assembly as claimed in claim 1, characterized in that, 45°≤α≤90°。 6. The pump body assembly as claimed in claim 1, characterized in that, r2>r1，r2>r3。 7. The pump body assembly as claimed in claim 1, characterized in that, The first arc segment and the third arc segment are symmetrically arranged on both sides of the second arc segment; and / or, the first arc segment and the third arc segment have the same radius.

8. The pump body assembly as claimed in claim 1, characterized in that, The groove width of the mating cavity is t, which satisfies... .

9. The pump body assembly as claimed in claim 1, characterized in that, The width of the slider body is T, and the minimum thickness of the transition recess is b, satisfying: 0.594≤b / T≤0.

642.

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

11. A refrigeration device, characterized in that, Includes the compressor as described in claim 10.

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