Pump body assembly, compressor and refrigeration equipment

Abstract

This application discloses a pump assembly, a compressor, and a refrigeration device, relating to the field of compressor technology. The assembly includes a cylinder, rollers, and a vane structure. The cylinder has a working chamber and a vane groove communicating with the working chamber. The rollers are eccentrically rotatable within the working chamber and have a theoretical displacement of V. A receiving groove is provided on the outer periphery of the rollers. The vane structure includes a vane body, a vane head, and a clearance neck, with the clearance neck connecting the vane body and the vane head. The vane body slidably fits in the vane groove, and its thickness is b1. The vane head rolls in the receiving groove. The minimum width of the clearance neck is b2, and its length is L. The height of the vane structure is H. V, b1, b2, L, and H satisfy a preset relationship. This solution allows the clearance neck to achieve a balance between structural strength, motion reliability, and compactness, solving the problem in the prior art where the lack of quantitative benchmarks makes it difficult to guarantee the reliability of the vane structure.

Description

Technical Field

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

[0002] Rotary compressors are widely used in refrigeration equipment such as air conditioners due to their advantages of high efficiency, compact structure, small size, and light weight. The vane, as one of the core moving parts of the rotary compressor, achieves the intake, compression, and discharge of the working medium through the hinged connection between the vane and the roller.

[0003] During compressor operation, the vanes are subjected to the pressure difference between the suction and discharge sides, and their neck area is subjected to significant bending stress and alternating loads. If the neck dimensions of the vanes are not properly designed, problems such as excessive wear and fatigue fracture can easily occur during long-term operation.

[0004] However, the current structural design of vanes lacks a systematic quantitative benchmark. The dimensional proportions of its various parts are often selected based on experience, making it difficult to achieve a good balance between structural strength, motion reliability, and compactness. As a result, the bending resistance and fatigue resistance of vanes under different pressure differentials and different eccentricity conditions cannot be guaranteed, which will shorten the overall service life of the compressor. Summary of the Invention

[0005] The main purpose of this application is to propose a pump body assembly that aims to solve the technical problem that the current structural design of vanes lacks a systematic quantitative benchmark, which easily leads to improper proportions of the vane neck size, making it difficult to guarantee the bending resistance and fatigue resistance of the vane under different working conditions.

[0006] To achieve the above objectives, the pump body assembly proposed in this application includes: The cylinder has a working chamber with a diameter of d1; the cylinder also has a sliding vane groove that communicates with the working chamber. A roller is eccentrically rotatable within the working cavity; the outer diameter of the roller is d2; the outer circumference of the roller is provided with an axially penetrating receiving groove; A sliding structure includes a sliding body, a sliding head, and a clearance neck, wherein the clearance neck connects the sliding body and the sliding head; the sliding body is slidably fitted in the sliding groove, and the thickness of the sliding body is b1; the sliding head is rollably fitted in the receiving groove; the minimum width of the clearance neck is b2, and the length of the clearance neck is L; the height of the sliding structure in the extending direction of the receiving groove is H. The pump body assembly satisfies the following relationship: , , .

[0007] In one embodiment, the length of the arc segment outline of the receiving groove in the cross-section is s0, and the length of the arc segment outline of the slider head in the cross-section is s1. The following conditions must be met between s0 and s1: .

[0008] In one embodiment, the slider head and the avoidance neck are connected by a first rounded transition portion.

[0009] In one embodiment, the radius R1 of the first rounded transition portion and the minimum width b2 of the clearance neck satisfy the following: .

[0010] In one embodiment, the slider body and the avoidance neck are connected by a second rounded transition portion.

[0011] In one embodiment, the radius R2 of the second rounded transition portion and the minimum width b2 of the clearance neck satisfy the following: .

[0012] In one embodiment, the outer periphery of the slider head has a first cylindrical segment, a second cylindrical segment, and a third cylindrical segment connected sequentially in the circumferential direction; the first cylindrical segment, the second cylindrical segment, and the third cylindrical segment are all arc surfaces.

[0013] In one embodiment, the radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness b1 of the slider body satisfy the following relationship: r1 + r3 < b1.

[0014] In one embodiment, the radius r1 of the first cylindrical segment, the radius r2 of the second cylindrical segment, and the radius r3 of the third cylindrical segment satisfy the following relationship: r2 > r1, r2 > r3.

[0015] In one embodiment, the angle between the two ends of the second cylindrical segment and the center of the first cylindrical segment is θ, where 45°≤θ<120°.

[0016] In one embodiment, the sliding plate structure is made of low-alloy high-strength steel.

[0017] In one embodiment, the yield strength of the slider structure is greater than or equal to 800 MPa.

[0018] In one embodiment, the fatigue limit strength of the sliding plate structure is greater than or equal to 350 MPa.

[0019] This application also proposes a compressor that includes a pump assembly as described above.

[0020] This application also proposes a refrigeration device, which includes a compressor as described above.

[0021] The pump body assembly proposed in this application provides a quantitative benchmark for the structural design of the vane structure from different dimensions through three relationships. The neck thickness ratio and neck height ratio limit the dimensional coordination range between various parts of the vane structure, ensuring sufficient bending and fatigue resistance of the neck while maintaining energy efficiency. Furthermore, by establishing a matching relationship between the volume of the neck and the theoretical displacement, the neck size can be constrained within a reasonable range relative to the displacement. This avoids insufficient load-bearing capacity due to an excessively small neck volume, while preventing structural redundancy, increased inertia, and excessive energy consumption due to an excessively large neck volume. By using these three relationships simultaneously as design constraints, a balance can be achieved between structural strength, operational reliability, and compactness in the neck design. This solves the problem in existing technologies where the lack of quantitative benchmarks makes it difficult to guarantee the reliability of the vane structure, enabling the vane structure to possess reliable structural strength, stiffness, and a long service life under high pressure differential and high eccentricity conditions. Attached Figure Description

[0022] To more clearly illustrate the technical solutions in the embodiments of this application 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 this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram of the overall structure of an embodiment of the pump body assembly provided in this application; Figure 2 This is a partial structural schematic diagram of an embodiment of the pump body assembly provided in this application; Figure 3 A schematic diagram of the arcuate outline of the receiving groove and the vane head in one embodiment of the pump body assembly provided in this application; Figure 4 A schematic diagram of the crankshaft structure in one embodiment of the pump body assembly provided in this application; Figure 5 A schematic diagram of the cylinder structure in one embodiment of the pump body assembly provided in this application; Figure 6 A schematic diagram of the overall structure of the roller in one embodiment of the pump body assembly provided in this application; Figure 7 A partial structural schematic diagram of the roller in one embodiment of the pump body assembly provided in this application; Figure 8A first-view overall structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 9 A second-view overall structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 10 A partial structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 11 This is a schematic diagram illustrating the relationship between the neck thickness ratio and the stress reduction effect of the neck avoidance structure (compared to the stress reduction of the existing structure). Figure 12 This is a schematic diagram illustrating the relationship between the neck-to-height ratio and the stress reduction effect of the neck avoidance structure (compared to the stress reduction of the existing structure). Figure 13 A schematic diagram illustrating the relationship between the ratio of the neck volume to the displacement and the stress reduction effect of the neck avoidance structure (compared to the stress reduction of the existing structure).

[0024] Explanation of icon numbers: 1. Cylinder; 11. Working chamber; 12. Sliding vane groove; 2. Crankshaft; 21. Eccentric part; 22. Main shaft; 3. Roller; 31. Receiving groove; 311. Groove opening limiting part; 312. Opening part; 4. Slider structure; 41. Slider body; 42. Slider head; 43. Clearance neck; 44. First rounded corner transition; 45. Second rounded corner transition; 421. First cylindrical segment; 422. Second cylindrical segment; 423. Third cylindrical segment.

[0025] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0026] The technical solutions of the embodiments of this application 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 this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0027] It should be noted that if the embodiments of this application 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.

[0028] Furthermore, if the embodiments of this application 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. Therefore, 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 that simultaneously satisfies A and B. 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 in this application.

[0029] Rotary compressors are widely used in refrigeration equipment such as air conditioners due to their advantages of high efficiency, compact structure, small size, and light weight. The vane, as one of the core moving parts of the rotary compressor, achieves the intake, compression, and discharge of the working medium through the hinged connection between the vane and the roller.

[0030] During compressor operation, the vanes are subjected to the pressure difference between the suction and discharge sides, and their neck area is subjected to significant bending stress and alternating loads. If the neck dimensions of the vanes are not properly designed, problems such as excessive wear and fatigue fracture can easily occur during long-term operation.

[0031] However, the current structural design of vanes lacks a systematic quantitative benchmark. The dimensional proportions of its various parts are often selected based on experience, making it difficult to achieve a good balance between structural strength, motion reliability, and compactness. As a result, the bending resistance and fatigue resistance of vanes under different pressure differentials and different eccentricity conditions cannot be guaranteed, which will shorten the overall service life of the compressor.

[0032] To address the aforementioned issues, this application proposes a pump body assembly that uses three relational formulas simultaneously as design constraints for the clearance neck of the vane structure. This allows the clearance neck to achieve a balance between structural strength, motion reliability, and compactness, thus solving the problem of difficulty in ensuring the reliability of the vane structure due to the lack of quantitative benchmarks.

[0033] In all embodiments of this application, the unit of all dimensional parameters (such as length, width, thickness, height, radius, diameter, eccentricity, etc.) is mm, and will not be repeated in the following description.

[0034] Please see Figures 1 to 9 The pump assembly provided in this application embodiment includes: Cylinder 1 has a working chamber 11 inside, the diameter of the working chamber 11 is d1; cylinder 1 is also provided with a sliding vane groove 12, the sliding vane groove 12 is connected to the working chamber 11; Roller 3 is eccentrically rotatable in working cavity 11; outer diameter of roller 3 is d2; axially penetrating receiving groove 31 is provided on the outer periphery of roller 3; The slider structure 4 includes a slider body 41, a slider head 42, and a clearance neck 43. The clearance neck 43 connects the slider body 41 and the slider head 42. The slider body 41 is slidably fitted in the slider groove 12, and the thickness of the slider body 41 is b1. The slider head 42 is tumbledly fitted in the receiving groove 31. The minimum width of the clearance neck 43 is b2, and the length of the clearance neck 43 is L. The height of the slider structure 4 in the extending direction of the receiving groove 31 is H. The pump body components satisfy the following relationship (the units of b1, b2, H, L, d1, and d2 are all in mm): , , .

[0035] In this embodiment, the pump assembly is applied to the compressor. The compressor may include a sealed housing, a motor, etc.; the pump assembly is disposed within the sealed housing; the motor may be a permanent magnet motor to provide driving force.

[0036] The cylinder 1 is roughly ring-shaped, and the internal space of the cylinder 1 forms a cylindrical working chamber 11 with a diameter of d1. The cylinder 1 is also provided with a sliding vane groove 12, which extends radially along the cylinder 1. One end of the sliding vane groove 12 is connected to the working chamber 11, and the other end of the sliding vane groove 12 faces the outside of the cylinder 1.

[0037] The crankshaft 2 has a main shaft 22 and an eccentric part 21 connected to the main shaft 22. The main shaft 22 is connected to the drive part of the motor. The central axis of the main shaft 22 can be coaxially arranged with the central axis of the working chamber 11. The eccentricity of the eccentric part 21 relative to the main shaft 22 is e.

[0038] The roller 3 can be configured as a ring-shaped structure with an outer diameter of d2. The roller 3 is sleeved on the eccentric part 21 of the crankshaft 2. When the crankshaft 2 is driven to rotate by the motor, the eccentric part 21 of the crankshaft 2 can drive the roller 3 to rotate eccentrically within the working cavity 11, that is, to make the central axis of the roller 3 move in a circular motion around the central axis of the working cavity 11, while ensuring that the outer peripheral surface of the roller 3 always maintains contact with or maintains a very small gap from the inner wall surface of the working cavity 11. A receiving groove 31 is provided on the outer peripheral wall of the roller 3. The receiving groove 31 can extend through the axial direction of the roller 3, and the depth direction of the receiving groove 31 is the radial direction of the roller 3. The cross-sectional shape of the receiving groove 31 is an arc shape with the opening facing the cavity wall of the working cavity 11.

[0039] The sliding vane structure 4 includes a sliding vane body 41, a sliding vane head 42, and a clearance neck 43. The two ends of the clearance neck 43 are connected to the sliding vane body 41 and the sliding vane head 42, respectively. The sliding vane body 41 is generally elongated, and its dimension along the axial direction of the roller 3 (i.e., the extension direction of the receiving groove 31) is called the height of the sliding vane body 41. Since the height is consistent throughout the sliding vane structure 4, the height of the sliding vane body 41 is the height H of the sliding vane structure 4. The dimension of the sliding vane body 41 along the width direction of the sliding vane groove 12 (i.e., along the circumference of the cylinder 1) is called the thickness b1 of the sliding vane body 41. The height of the sliding vane body 41 (i.e., the height H of the sliding vane structure 4) and the thickness b1 of the sliding vane body 41 are matched with the sliding vane groove 12, allowing the sliding vane body 41 to smoothly reciprocate along the extension direction of the sliding vane groove 12 (i.e., the radial direction of the cylinder 1). The end of the sliding vane body 41 facing the roller 3 is connected to the sliding vane head 42 via the clearance neck 43. The slider head 42 has a columnar structure, the axis of which is parallel to the height direction of the slider body 41 and the axis of which is parallel to the axis of the roller 3. The slider head 42 is hinged in the receiving groove 31 so that the slider structure 4 and the roller 3 are connected, and the slider head 42 can roll relative to the receiving groove 31 in its circumferential direction. The length of the clearance neck 43 in the extending direction of the slider groove 12 (i.e., the radial direction of the cylinder 1) is L; the minimum width of the clearance neck 43 is b2, which is less than the thickness b1 of the slider body 41 and the diameter of the slider head 42. Both sides of the groove opening of the receiving groove 31 extend inward to form a groove limiting part 311 that matches the clearance neck 43, so as to prevent the slider head 42 from disengaging from the receiving groove 31. The total length of the slider structure 4 in the extending direction of the slider groove 12 (i.e., the radial direction of the cylinder 1) is Lv.

[0040] Roller 3 and vane structure 4 together divide the working chamber 11 into an intake chamber and a compression chamber. The intake chamber is connected to the intake port on one side of cylinder 1, and the compression chamber is connected to the exhaust port on the other side of cylinder 1. During the process of the motor driving roller 3 to rotate eccentrically within the working chamber 11 via crankshaft 2, vane structure 4 is driven by roller 3 to reciprocate linearly in vane groove 12. During this process, vane head 42 also rolls relative to receiving groove 31 to adapt to changes in the relative angle between roller 3 and vane structure 4. Based on the above-described actions of roller 3 and vane structure 4, the compressor's working medium can enter the intake chamber from the intake port under negative pressure. The working medium entering the intake chamber will gradually transfer to the exhaust chamber as roller 3 rotates. The working medium entering the exhaust chamber can be compressed into a high-temperature, high-pressure gas and finally discharged from the exhaust port, thus completing one working cycle. In one working cycle, the total amount of gas discharged through the eccentric rotation of roller 3 relative to cylinder 1 can be called the theoretical displacement V of the pump assembly. The theoretical displacement V can also be characterized by the gas volume obtained by subtracting the volume occupied by roller 3 from the total volume of working chamber 11. It should be noted that the theoretical displacement V is for a single cylinder 1; when the compressor is a two-cylinder compressor or a multi-cylinder compressor, the theoretical displacement V is the displacement corresponding to one cylinder 1 in the compressor.

[0041] Based on the above structure, in order to quantitatively evaluate the degree of matching between the bending resistance and fatigue resistance of the vane structure 4 and the operating conditions of the compressor, this embodiment further constructs a relational formula for constraining the dimensions of the avoidance neck 43.

[0042] Specifically, the ratio between the minimum width b2 of the clearance neck 43 and the thickness b1 of the slide body 41 (i.e., the neck-to-thickness ratio) has a significant impact on the bending stiffness of the slide structure 4. If b2 is too small relative to b1, the clearance neck 43 is too weak and prone to fatigue fracture under alternating bending stress; if b2 is too large relative to b1, the size of the clearance neck 43 is too large, resulting in an increase in the overall weight of the slide structure 4, an increase in the moment of inertia, and an increase in energy consumption during operation, which will adversely affect the overall energy efficiency of the compressor. Based on the above considerations, experimental verification shows that when the neck-to-thickness ratio satisfies the following relationship, the slide structure 4 can achieve a balance between bending stiffness, stress distribution, and overall energy efficiency:

[0043] Specifically, such as Figure 11 As shown, when the neck thickness ratio satisfies When the stress reduction percentage of the avoidance neck 43 compared to the existing structure is positive, that is, the stress generated at the avoidance neck 43 is reduced compared to the existing structure, and a positive stress reduction effect can be obtained.

[0044] Furthermore, the ratio between the minimum width b2 of the clearance neck 43 and the height H of the sliding structure 4 (i.e., the neck-to-height ratio) affects the torsional resistance of the clearance neck 43 and the moment of inertia of the sliding structure 4. When b2 is too small relative to H, the cross-sectional dimensions of the clearance neck 43 in the height direction are insufficient, making it prone to torsional deformation or fatigue cracks under alternating loads. When b2 is too large relative to H, the size of the clearance neck 43 is too large, increasing the overall weight of the sliding structure 4, increasing the moment of inertia, and increasing energy consumption during operation, thus adversely affecting the overall energy efficiency of the compressor. Based on the above considerations, experimental verification shows that when the neck-to-height ratio satisfies the following relationship, the stress level of the clearance neck 43 can be reduced, and the fatigue life of the sliding structure 4 can be extended:

[0045] Specifically, such as Figure 12 As shown, when the neck-to-height ratio satisfies When the stress reduction percentage of the avoidance neck 43 compared to the existing structure is positive, that is, the stress generated at the avoidance neck 43 is reduced compared to the existing structure, and a positive stress reduction effect can be obtained.

[0046] The compressor's displacement is a key design parameter determining the load-bearing capacity of the vane structure 4. This embodiment further introduces a ratio between the volume of the clearance neck 43 and the theoretical displacement V of the pump assembly to establish a quantitative correlation between the neck size and overall machine performance. Specifically, the volume of the clearance neck 43 can be approximately expressed as the product of the minimum width b2 of the clearance neck 43, the length L of the clearance neck 43, and the height H of the vane structure 4; the theoretical displacement V of the pump assembly can be determined by the diameter d1 of the working chamber 11 and the outer diameter d2 of the roller 3, specifically through… Calculations were performed. Experiments verified that when the ratio of the volume of the clearance neck 43 to the theoretical displacement V satisfies the following relationship, the load-bearing capacity of the sliding vane structure 4 and the displacement requirement of the compressor can achieve optimal matching:

[0047] Specifically, if the ratio of the volume of the clearance neck 43 to the theoretical displacement V is less than 0.08, it indicates that the current neck size is too small relative to the displacement, which may lead to insufficient load-bearing capacity of the clearance neck 43 and overload failure under high pressure differential conditions. Conversely, if the ratio is greater than 0.45, it indicates that the current neck size is too large relative to the displacement, resulting in structural redundancy, material waste, increased inertia, and excessive energy consumption, which is detrimental to ensuring the overall energy efficiency and structural compactness of the compressor. For details... Figure 13 As shown, when the above ratio satisfies When the stress reduction percentage of the avoidance neck 43 compared to the existing structure is positive, that is, the stress generated at the avoidance neck 43 is reduced compared to the existing structure, and a positive stress reduction effect can be obtained.

[0048] Therefore, the three relationships mentioned above provide quantitative benchmarks for the structural design of the sliding structure 4 from different dimensions. Specifically, the neck thickness ratio and neck height ratio limit the dimensional coordination range between various parts of the sliding structure 4, ensuring sufficient bending and fatigue resistance of the clearance neck 43 while maintaining energy efficiency. Furthermore, by establishing a matching relationship between the volume of the clearance neck 43 and the theoretical displacement, the reasonable range of neck dimensions relative to displacement can be constrained. This avoids insufficient load-bearing capacity due to an excessively small neck volume, and also avoids structural redundancy, increased inertia, and excessive energy consumption due to an excessively large neck volume. By using these three relationships simultaneously as design constraints, the clearance neck 43 can achieve a balance between structural strength, motion reliability, and compactness, solving the problem in existing technologies where the lack of quantitative benchmarks makes it difficult to guarantee the reliability of the sliding structure 4. This ensures that the sliding structure 4 possesses reliable structural strength, stiffness, and a long service life under high pressure differential and high eccentricity conditions.

[0049] In one embodiment, refer to Figures 1 to 9 The working cavity 11 is cylindrical and has a diameter of d1; the roller 3 is annular and has an outer diameter of d2. The theoretical displacement V of roller 3 when it rotates eccentrically, the diameter d1 of working cavity 11, the outer diameter d2 of roller 3, and the height H of sliding structure 4 in the extension direction of receiving groove 31 satisfy the following: .

[0050] Specifically, when the roller 3 rotates eccentrically within the working chamber 11, a crescent-shaped region is formed between the outer circumferential surface of the roller 3 and the wall of the working chamber 11. The volume of this crescent-shaped region can characterize the total amount of gas discharged by the pump assembly in one complete working cycle (i.e., the roller 3 rotates eccentrically one revolution relative to the working chamber 11), which is also known as the theoretical displacement V. Thus, the theoretical displacement V can be obtained by calculating the volume of this crescent-shaped region.

[0051] In practical applications, since the height of cylinder 1 (i.e., the height of the cylindrical region corresponding to working cavity 11), the height of roller 3 (i.e., the height of the cylinder corresponding to roller 3), and the height H of sliding structure 4 are basically the same, the volume of the cylindrical region corresponding to working cavity 11 can be directly calculated using the height H of sliding structure 4, and the volume of the cylinder corresponding to roller 3 can also be directly calculated using the height H of sliding structure 4. Specifically, the volume of the cylindrical region corresponding to working cavity 11 is... The volume of the cylinder corresponding to roller 3 is Then, by subtracting the volume of the cylinder corresponding to the roller 3 from the volume of the cylindrical region corresponding to the working cavity 11, the volume of the crescent-shaped region formed between the working cavity 11 and the roller 3 can be obtained. The volume of this crescent-shaped region is the theoretical displacement V, which can then be substituted into the above embodiment. This relationship is used for calculation.

[0052] In one embodiment, refer to Figure 2 and Figure 3 The length of the arc segment U1 of the receiving groove 31 on the cross-section is s0, and the length of the arc segment U2 of the slider head 42 on the cross-section is s1.

[0053] The following conditions must be met between s0 and s1: In this context, the units for s0 and s1 are both mm.

[0054] Specifically, the cross-sections of the receiving groove 31 and the sliding head 42 are both perpendicular to the axial direction. For example... Figure 3 As shown, in the cross-sectional view, the arcuate outline U1 of the receiving groove 31 refers to the complete outline of the receiving groove 31 excluding the groove limiting part 311 and the opening part 312 (the size of the opening part 312 gradually increases from the inside to the outside to form...). Figure 3 The remaining arc portion after the flared shape shown has a length of s0; the arc segment outline U2 of the slider head 42 refers to the complete arc outline of the slider head 42, and the length of U2 is s1.

[0055] In this embodiment, by limiting the length s0 of the arc segment outline U1 of the receiving groove 31 in the cross-section and the length s1 of the arc segment outline U2 of the slider head 42 in the cross-section as described above, it can be ensured that the receiving groove 31 has a sufficient circumferential coverage range, thereby enabling it to fully wrap around the slider head 42, preventing the slider head 42 from loosening or detaching during movement, and thus improving the stability of the hinged fit between the slider head 42 and the receiving groove 31.

[0056] In one embodiment, refer to Figure 8 and Figure 10 The slider head 42 and the avoidance neck 43 are connected by a first rounded transition part 44; this makes the connection between the slider head 42 and the avoidance neck 43 smoother, which helps to eliminate stress concentration at the sharp corner and improve the fatigue strength and reliability of the slider structure 4.

[0057] In one embodiment, refer to Figure 8 and Figure 10 The radius R1 of the first rounded transition portion 44 and the minimum width b2 of the clearance neck 43 satisfy the following: In this context, the units for R1 and b2 are both mm.

[0058] This embodiment limits the proportional relationship between the radius R1 of the first rounded transition portion 44 and the minimum width b2 of the avoidance neck 43. Under the corresponding minimum width b2, the stress concentration factor between the slider head 42 and the avoidance neck 43 can be effectively reduced, and the generation of fatigue cracks can be suppressed. It is especially suitable for high alternating load application scenarios.

[0059] In one embodiment, refer to Figure 8 and Figure 10 The slider body 41 and the clearance neck 43 are connected by a second rounded transition portion 45; this makes the connection between the slider body 41 and the clearance neck 43 smoother, which helps to eliminate stress concentration at the sharp corner and improve the fatigue strength and reliability of the slider structure 4.

[0060] In one embodiment, refer to Figure 8 and Figure 10 The radius R2 of the second rounded transition portion 45 and the minimum width b2 of the clearance neck 43 satisfy the following: In this context, the units for R2 and b2 are both mm.

[0061] This embodiment limits the proportional relationship between the radius R2 of the second rounded transition portion 45 and the minimum width b2 of the avoidance neck 43. Under the corresponding minimum width b2, the stress concentration factor between the slider body 41 and the avoidance neck 43 can be effectively reduced, and the generation of fatigue cracks can be suppressed. It is especially suitable for high alternating load application scenarios.

[0062] In one embodiment, refer to Figure 8 and Figure 10 The outer periphery of the slider head 42 has a first cylindrical section 421, a second cylindrical section 422 and a third cylindrical section 423 connected in sequence along the circumference; the first cylindrical section 421, the second cylindrical section 422 and the third cylindrical section 423 are all arc surfaces.

[0063] Compared to the existing technology where the outer peripheral surface of the vane head 42 is a single arc surface, this embodiment uses a three-cylindrical segment design, which provides more degrees of freedom for adjusting the shape of the outer peripheral surface of the vane head 42. Specifically, designers can flexibly design the radius of curvature or plane angle of each cylindrical segment, as well as the relative position and connection method between the cylindrical segments, according to the compressor's operating parameters, such as the pressure of the working medium, the speed range, and the lubrication conditions. This allows the contact area, contact pressure distribution, and contact gap between the vane head 42 and the receiving groove 31 to be finely configured according to actual needs.

[0064] When the vane head 42 engages with the receiving groove 31, the vane structure 4 can oscillate relative to the roller 3 within a certain angular range. During a complete cycle of compressor operation, the relative position between the roller 3 and the vane structure 4 continuously changes; during this process, multiple cylindrical sections of the vane head 42 can sequentially contact the groove wall of the receiving groove 31. By rationally setting the geometric parameters of each cylindrical section, the contact stress can be distributed more evenly on the surface of the vane head 42, avoiding excessively high local stress peaks. Simultaneously, the naturally formed micro-gaps or oil wedge regions between the multiple cylindrical sections and the groove wall of the receiving groove 31 facilitate the storage and flow of lubricating oil, promoting the formation of a hydrodynamic oil film, thereby reducing the coefficient of friction and wear rate.

[0065] As can be seen, in this embodiment, the outer peripheral surface of the slide head 42 is set to have three cylindrical segments connected in sequence along the circumference. This changes the original single contour shape of the slide head 42, thereby providing a structural basis for the adjustment of the inherent mating relationship and operating parameters. This makes it possible to further improve the contact characteristics, stress distribution, wear degree and lubrication performance, which were originally difficult to optimize in depth due to the single contour shape.

[0066] In one embodiment, refer to Figure 8 and Figure 10 The radius r1 of the first cylindrical segment 421, the radius r3 of the third cylindrical segment 423, and the thickness b1 of the slider body 41 satisfy the following relationship: r1 + r3 < b1; where the units of r1, r3, and b1 are all mm.

[0067] In this embodiment, the first cylindrical segment 421 and the third cylindrical segment 423 can be distributed on both sides of the slider head 42; the sum of the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 can be used to characterize the size of the slider head 42 in the thickness direction of the slider body 41. By limiting r1+r3<b1, the overall machinability of the slider structure 4 can be improved, and the problem of material waste and reduced processing efficiency caused by the need to reserve additional blank material for the slider head 42 due to the size of the slider head 42 being larger than the thickness b1 of the slider body 41 can be avoided.

[0068] In one embodiment, refer to Figure 8 and Figure 10 The radius r1 of the first cylindrical segment 421, the radius r2 of the second cylindrical segment 422, and the radius r3 of the third cylindrical segment 423 satisfy the following relationship: r2 > r1, r2 > r3.

[0069] In this embodiment, the curvature of the second cylindrical segment 422 is less than that of the first cylindrical segment 421 and the third cylindrical segment 423; thus, the gap between the second cylindrical segment 422 and the receiving groove 31 is greater than the gap between the first cylindrical segment 421, the third cylindrical segment 423 and the receiving groove 31. Based on the above structural configuration, when the sliding head 42 moves relative to the receiving groove 31, a gradually changing wedge-shaped gap can be formed between the sliding head 42 and the groove wall of the receiving groove 31; the volume change of this wedge-shaped gap can generate a pumping effect on the lubricating oil, which can force the lubricating oil into the friction interface, thereby building a stable lubricating oil film in the contact area between the sliding head 42 and the receiving groove 31. This can improve the quality of the oil film, thereby enhancing the lubrication effect, reducing friction and wear, and further improving the reliability and service life of the hinged fit between the sliding head 42 and the receiving groove 31.

[0070] In one embodiment, refer to Figure 8 and Figure 10 The angle between the two ends of the second cylindrical segment 422 and the center of the first cylindrical segment 421 is θ, where 45°≤θ<120°.

[0071] like Figure 10 As shown, under the premise that the first cylindrical segment 421 and the third cylindrical segment 423 are concentric and have the same radius, the center of circle A1 where the first cylindrical segment 421 and the third cylindrical segment 423 are located is O1, the center of circle A2 where the second cylindrical segment 422 is located is O2, and the angle formed by the lines connecting the two ends of the second cylindrical segment 422 and the center O1 is θ.

[0072] Specifically, when the included angle θ is too small (θ < 45°), the circumferential extension length of the wedge-shaped gap in the above embodiment will be insufficient, making it difficult to form an effective pumping effect on the lubricating oil. This results in limited establishment and maintenance of the lubricating oil film and insignificant lubrication improvement. Conversely, when the included angle θ is too large (θ ≥ 120°), the second cylindrical section 422 will excessively encroach on the contact area between the slide head 42 and the receiving groove 31, reducing the effective bearing area of ​​the first cylindrical section 421 and the third cylindrical section 423. This increases the contact surface pressure, which in turn exacerbates friction and wear, reducing the reliability of the fit between the slide head 42 and the receiving groove 31. Therefore, this embodiment limits the included angle θ to 45° ≤ θ < 120°, ensuring that the slide head 42 has sufficient bearing area while maintaining good lubrication, thus balancing the lubrication performance and bearing reliability of the hinged part.

[0073] In one embodiment, the slider structure 4 is made of low-alloy high-strength steel; further, the yield strength of the slider structure 4 is greater than or equal to 800 MPa, and the fatigue limit strength of the slider structure 4 is greater than or equal to 350 MPa.

[0074] This embodiment, through the above-mentioned constraints on the mechanical properties of the material, can ensure that the sliding plate structure 4 has sufficient bending resistance and fatigue resistance under high pressure differential conditions, which can make up for the inadequacy of simply constraining the size of the sliding plate structure 4.

[0075] This application also provides a compressor; please refer to [link / reference]. Figures 1 to 10 The compressor includes the pump assembly in any of the above embodiments.

[0076] In this embodiment, the compressor specifically includes a pump body assembly and other necessary components that work in conjunction with it, which are not listed here. For the specific structure of the pump body assembly, please refer to the description of the above embodiments. Since the compressor in this embodiment 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. That is, it provides a quantitative benchmark for the structural design of the vane structure 4 from different dimensions through three relational formulas; among them, the neck thickness ratio and neck height ratio limit the dimensional coordination range between various parts of the vane structure 4, which can ensure that the avoidance neck 43 has sufficient bending and fatigue resistance while ensuring energy efficiency; and by establishing a matching relationship between the volume of the avoidance neck 43 and the theoretical displacement, it can be used to constrain the reasonable range of the neck size relative to the displacement. On the one hand, it can avoid the problem of insufficient load-bearing capacity due to the neck volume being too small, and on the other hand, it can avoid the problems of structural redundancy, increased moment of inertia, and excessive energy consumption due to the neck volume being too large. By using the above three relationships as design constraints, the avoidance neck 43 can achieve a balance between structural strength, motion reliability and compactness, which solves the problem that the reliability of the slider structure 4 is difficult to guarantee due to the lack of quantitative benchmarks in the prior art. This enables the slider structure 4 to have reliable structural strength, stiffness and long service life under high pressure differential and high eccentricity conditions.

[0077] This application also provides a refrigeration device; please refer to [link / reference]. Figures 1 to 10 The refrigeration equipment includes the compressor in any of the above embodiments.

[0078] The refrigeration equipment in this embodiment may include air conditioners, refrigerators, etc., and is not limited here.

[0079] For other specific structural details of the compressor, please refer to the description of the above embodiments. Since the refrigeration equipment in this embodiment employs all the technical solutions of all the above embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the above embodiments, and will not be repeated here.

[0080] The above description is merely an exemplary embodiment of this application and does not limit the patent scope of this application. Any equivalent structural transformations made based on the technical concept of this application and the contents of the specification and drawings of this application, or direct / indirect applications in other related technical fields, are included within the patent protection scope of this application.

Claims

1. A pump body assembly, characterized by, include: The cylinder has a working chamber with a diameter of d1; the cylinder also has a sliding vane groove that communicates with the working chamber. A roller is eccentrically rotatable within the working cavity; the outer diameter of the roller is d2; the outer circumference of the roller is provided with an axially penetrating receiving groove; The slide structure comprises a slide body, a slide head and an avoiding neck connecting the slide body and the slide head; the slide body is slidingly fitted in the slide groove, the thickness of the slide body is b1; the slide head is rollingly fitted in the accommodating groove; the minimum width of the avoiding neck is b2, the length of the avoiding neck is L; the height of the slide structure is H; the pump body assembly satisfies the following relationship: , , .

2. The pump body assembly according to claim 1, characterized in that, The length of the arc segment outline of the receiving groove in the cross-section is s0, and the length of the arc segment outline of the slider head in the cross-section is s1. The following conditions must be met between s0 and s1: .

3. The pump body assembly according to claim 1, characterized in that, The slider head and the avoidance neck are connected by a first rounded transition portion.

4. The pump body assembly according to claim 3, characterized in that, The radius R1 of the first rounded transition portion and the minimum width b2 of the clearance neck satisfy the following: .

5. The pump body assembly according to claim 1, characterized in that, The slider body and the avoidance neck are connected by a second rounded transition portion.

6. The pump body assembly according to claim 5, characterized in that, The radius R2 of the second rounded transition portion and the minimum width b2 of the clearance neck satisfy the following: .

7. The pump body assembly according to claim 1, characterized in that, The outer periphery of the slider head has a first cylindrical section, a second cylindrical section, and a third cylindrical section connected sequentially in the circumferential direction; the first cylindrical section, the second cylindrical section, and the third cylindrical section are all arc surfaces.

8. The pump body assembly according to claim 7, characterized in that, The radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness b1 of the slider body satisfy the following relationship: r1 + r3 < b1.

9. The pump body assembly according to claim 7, characterized in that, The radius r1 of the first cylindrical segment, the radius r2 of the second cylindrical segment, and the radius r3 of the third cylindrical segment satisfy the following relationship: r2 > r1, r2 > r3.

10. The pump body assembly according to claim 9, characterized in that, The angle between the two ends of the second cylindrical segment and the center of the first cylindrical segment is θ, where 45°≤θ<120°.

11. The pump body assembly according to any one of claims 1 to 10, characterized in that, The sliding plate structure is made of low-alloy high-strength steel; And / or, the yield strength of the sliding structure is greater than or equal to 800 MPa; And / or, the fatigue limit strength of the sliding plate structure is greater than or equal to 350 MPa.

12. A compressor, characterized in that, The compressor includes a pump body assembly as described in any one of claims 1 to 11.

13. A refrigeration device, characterized in that, The refrigeration equipment includes the compressor as described in claim 12.

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