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, a crankshaft, rollers, and a vane structure. The cylinder has a working chamber and a vane groove communicating with the working chamber. The crankshaft has an eccentric portion with an eccentricity of e. The rollers rotate eccentrically along the working chamber under the drive of the crankshaft. 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. The vane body slides in the vane groove and has a thickness of t. The vane head rolls in the receiving groove and has a diameter of D1. A groove limiting portion is formed at the opening of the receiving groove to cooperate with the clearance neck, and the minimum width of the clearance neck is d. The total length of the vane structure is Lv. e, t, D1, d, and Lv satisfy a preset relationship. This solution balances the various parameters of the vane structure, thereby enabling the vane structure to possess sufficient structural strength, stiffness, and motion reliability under high pressure differential and high eccentricity conditions.

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 have advantages such as high efficiency, compact structure, small size, and light weight, and are currently widely used in the interior of refrigeration equipment such as air conditioners.

[0003] The vane is one of the core moving parts of a rotary compressor. Through the hinged connection between the vane and the roller, the working medium can be drawn in, compressed, and discharged. However, the current design of vanes lacks a systematic quantitative standard, which can easily lead to improper dimensional proportions of the vanes, making it difficult to meet the reliability requirements of the compressor under high pressure differential and high eccentricity conditions. Summary of the Invention

[0004] The main objective of this application is to propose a pump body assembly that addresses the technical problem that the current design of vanes lacks a systematic quantitative benchmark, which easily leads to improper vane size proportions and makes it difficult to meet the reliability requirements of compressors under high pressure differential and high eccentricity conditions.

[0005] To achieve the above objectives, the pump body assembly proposed in this application includes: A cylinder has a working chamber inside; the cylinder is also provided with a sliding vane groove, which communicates with the working chamber; A crankshaft having an eccentric portion, wherein the eccentricity of the eccentric portion is e; A roller is fitted onto the eccentric portion; the roller is used to rotate eccentrically along the cavity wall of the working chamber under the drive of the crankshaft; the outer circumference of the roller is provided with a receiving groove that runs through the axial direction. 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 t; the sliding head is rollably fitted in the receiving groove, and the diameter of the sliding head is D1; ​​a groove limiting part is formed at the opening of the receiving groove to cooperate with the clearance neck, and the minimum width of the clearance neck is d; the total length of the sliding structure is Lv. The pump body assembly satisfies the following relationship: .

[0006] In one embodiment, the diameter D1 of the slider head and the diameter D2 of the receiving groove satisfy the following relationship: .

[0007] In one embodiment, the minimum width d of the clearance neck and the thickness t of the slider body satisfy the following relationship: .

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

[0009] In one embodiment, the diameter D1 of the slider head and the thickness t of the slider body satisfy the following relationship: .

[0010] In one embodiment, the surface roughness Rz of the slider head is ≤3.2 μm.

[0011] In one embodiment, the eccentricity e of the eccentric portion and the total length Lv of the slider structure satisfy the following relationship: .

[0012] In one embodiment, the pump body assembly satisfies the following relationship: .

[0013] 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.

[0014] In one embodiment, the radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness t of the slider body satisfy the following relationship: r1 + r3 < t.

[0015] In one embodiment, the second cylindrical segment is located between the first cylindrical segment and the third cylindrical segment; the central axis of the first cylindrical segment and the central axis of the third cylindrical segment are collinear, and the radius r1 of the first cylindrical segment is the same as the radius r3 of the third cylindrical segment.

[0016] 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.

[0017] 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°.

[0018] In one embodiment, the material of the sliding plate structure is high-speed steel or stainless steel.

[0019] In one embodiment, the surface hardness of the slider structure is greater than HV700.

[0020] This application also proposes a compressor that includes a pump assembly as described above.

[0021] This application also proposes a refrigeration device, which includes a compressor as described above.

[0022] The pump body assembly proposed in this application establishes a relationship between the load-bearing capacity of the hinge, the bending stiffness of the vane body, and the degree of matching between their motion amplitude, and limits their ratios within a preset range. This ensures that the various parameters of the vane structure are well balanced, avoiding problems such as material waste, increased moment of inertia, and excessive energy consumption caused by excessively large ratios. It also avoids problems such as stress concentration at the avoidance neck, excessive wear of the vane head, and seal failure caused by excessively small ratios. As a result, the vane structure can have sufficient structural strength, stiffness, and motion reliability under high pressure differential and high eccentricity conditions. Attached Figure Description

[0023] 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.

[0024] 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 A schematic diagram of the cylinder structure in one embodiment of the pump body assembly provided in this application; Figure 3 A schematic diagram of the crankshaft structure in one embodiment of the pump body assembly provided in this application; Figure 4 A schematic diagram of the overall structure of the roller in one embodiment of the pump body assembly provided in this application; Figure 5 A partial structural schematic diagram of the roller in one embodiment of the pump body assembly provided in this application; Figure 6 A schematic diagram of the overall structure of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 7 A partial structural schematic diagram of the vane structure in one embodiment of the pump body assembly provided in this application; Figure 8 This is a schematic diagram showing the influence of the ratio X on the oil film thickness at the slider head.

[0025] 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; 4. Slider structure; 41. Slider body; 42. Slider head; 43. Clearance neck; 44. Rounded corner transition; 421. First cylindrical segment; 422. Second cylindrical segment; 423. Third cylindrical segment.

[0026] 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

[0027] 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.

[0028] 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.

[0029] 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.

[0030] Rotary compressors have advantages such as high efficiency, compact structure, small size, and light weight, and are currently widely used in the interior of refrigeration equipment such as air conditioners.

[0031] The vane is one of the core moving parts of a rotary compressor. Through the hinged connection between the vane and the roller, the working medium can be drawn in, compressed, and discharged. However, the current design of vanes lacks a systematic quantitative standard, which can easily lead to improper dimensional proportions of the vanes, making it difficult to meet the reliability requirements of the compressor under high pressure differential and high eccentricity conditions.

[0032] To address the aforementioned issues, this application proposes a pump body assembly. By establishing a relationship between the load-bearing capacity of the hinge, the bending stiffness of the slide body, and the degree of matching between their motion amplitude, and limiting their ratios within a preset range, the various parameters of the slide structure achieve a good balance. This avoids problems such as material waste, increased moment of inertia, and excessive energy consumption caused by excessively large ratios, and also avoids problems such as stress concentration at the avoidance neck, excessive wear of the slide head, and seal failure caused by excessively small ratios. As a result, the slide structure can possess sufficient structural strength, stiffness, and motion reliability under high pressure differential and high eccentricity conditions.

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

[0034] Please see Figures 1 to 6 The pump assembly provided in this application embodiment includes: The cylinder 1 has a working chamber 11 inside; the cylinder 1 is also provided with a sliding vane groove 12, which extends radially along the cylinder 1 and communicates with the working chamber 11. Crankshaft 2 has an eccentric part 21, the eccentricity of which is e; Roller 3 is sleeved on the eccentric part 21; roller 3 is used to rotate eccentrically along the cavity wall of working cavity 11 under the drive of crankshaft 2; the outer periphery of roller 3 is provided with a receiving groove 31 that runs through the axial direction, and the cross-sectional shape of receiving groove 31 can be set as an outward-facing arc shape. 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 t. The slider head 42 is rollably fitted in the receiving groove 31, and the diameter of the slider head 42 is D1. A groove limiting part 311 is formed at the opening of the receiving groove 31 to cooperate with the clearance neck 43, and the minimum width of the clearance neck 43 is d. The total length of the slider structure 4 is Lv. The pump body assembly satisfies the following relationship (D1, d, t, Lv, and e 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 annular in shape, and the internal space of the cylinder 1 forms a cylindrical working chamber 11. 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 D3. The roller 3 is fitted onto the eccentric portion 21 of the crankshaft 2. When the crankshaft 2 is driven to rotate by the motor, the eccentric portion 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 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 along 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. The diameter of the receiving groove 31 is D2, and the center distance between the receiving groove 31 and the inner ring of the roller 3 (i.e., the shortest straight-line distance between the central axis of the receiving groove 31 and the central axis of the inner ring of the roller 3) is L.

[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. The dimension of the sliding vane body 41 along the axial direction of the roller 3 is called the height of the sliding vane body 41, and 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 t of the sliding vane body 41. The height and thickness t 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. 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 diameter of the slider head 42 is D1; ​​specifically, D1 is the minimum outer circle diameter of the slider head 42. The minimum width of the clearance neck 43 is d, which is less than the thickness t of the slider body 41 and the diameter D1 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.

[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. The unit of theoretical displacement V is CC (cubic centimeters). It should be noted that the theoretical displacement V is for a single cylinder 1; when the compressor is a twin-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 strength, stiffness and motion reliability of the slider structure 4 under different thicknesses and eccentricities, this embodiment constructs the following relationship (the units of D1, d, t, Lv, and e are all mm):

[0042] In the above relationship, the numerator part It can be used to characterize the load-bearing cross-sectional characteristics of hinged joints. A larger value indicates a larger effective area resisting shear and bending loads, and a stronger load-bearing capacity. In the denominator... It can be used to characterize the bending stiffness of the slider body 41; among which, the thickness t of the slider body 41 is a key parameter affecting its bending section modulus (section modulus and...). (Proportional to thickness t) The greater the thickness t of the vane body 41, the stronger its ability to resist bending deformation caused by gas pressure difference and lateral force. In compressor design, using a vane body 41 with a larger thickness t usually corresponds to operating conditions that need to withstand higher loads. At this time, the overall shear stress and bending stress borne by the vane body 41 are also correspondingly larger. Therefore, it is necessary to simultaneously increase the diameter D1 of the vane head 42 and the minimum width d of the clearance neck 43, so that... Matching within a reasonable range is essential to ensure the overall structural strength of the slider structure 4.

[0043] In addition, for In this context, the eccentricity *e* of crankshaft 2 determines the stroke of roller 3 and the range of motion of vane structure 4. When the eccentricity *e* increases, the oscillation amplitude of vane head 42 within receiving groove 31 increases accordingly. At this point, a longer total length *Lv* of vane structure 4 is required to avoid motion interference or disengagement, thereby ensuring connection reliability and smooth movement. In the above formula... It can characterize the maximum stroke of roller 3 and the maximum reciprocating range of slide structure 4. The overall ratio X comprehensively reflects the matching degree between the load-bearing capacity of the hinge, the bending stiffness of slide body 41, and motion adaptability.

[0044] Experiments have verified that when the ratio X is within the range of 0.08 to 0.27, it meets the requirements for structural strength, stiffness, and motion reliability when the slider head 42 and the receiving groove 31 are hinged together, thereby improving the durability and stability of the slider structure 4 under high pressure differential and high eccentricity conditions. Specifically, when the ratio X is greater than 0.27, the hinged part is too large or the eccentricity is too small, which can easily lead to material waste, increased inertia, and excessive energy consumption. When the ratio X is less than 0.08, the hinged part is relatively weak, making the avoidance neck 43 prone to stress concentration and shear fracture under high load and high eccentricity conditions. Furthermore, the slider head 42 is prone to excessive wear, crushing deformation, and sealing failure under high load and high eccentricity conditions. Therefore, by limiting X to between 0.08 and 0.27, structural compactness and manufacturing economy can be considered while ensuring the structural strength, rigidity, and operational reliability of the sliding vane structure 4, thereby improving the overall performance of the compressor and extending its service life. Furthermore, as... Figure 8 As shown, when X is 0.08~0.27, the oil film thickness formed at the slider head 42 is at a relatively high level, which can ensure the lubrication performance between the slider head 42 and the receiving groove 31 and improve the reliability and stability of the hinge fit.

[0045] In one embodiment, refer to Figures 1 to 6 The diameter D1 of the slider head 42 and the diameter D2 of the receiving groove 31 satisfy the following: ; where D1 and D2 are both in mm.

[0046] In this embodiment, This can be used to characterize the fit clearance between the vane head 42 and the receiving groove 31. By controlling this fit clearance to be above 0.01mm, it can be ensured that the vane head 42 can roll or swing freely within the receiving groove 31, avoiding movement jamming or increased friction due to excessively small clearance. At the same time, controlling this fit clearance to be below 0.08mm can prevent the sealing performance between the vane head 42 and the receiving groove 31 from decreasing due to excessive clearance, thereby causing gas leakage and reducing compressor energy efficiency.

[0047] Therefore, by limiting the gap range between the receiving groove 31 and the vane head 42, this embodiment can ensure the smooth movement of the vane structure 4 and reduce friction while effectively maintaining the sealing performance of the hinge, thereby taking into account both the operational reliability and energy efficiency of the compressor.

[0048] In one embodiment, refer to Figure 6 The minimum width d of the neck 43 and the thickness t of the slider body 41 satisfy the following: ; where d and t are both in mm.

[0049] Specifically, if If the value is too small (less than 0.5), the clearance neck 43 will be relatively narrow. In this case, the clearance neck 43 is prone to stress concentration under high pressure differential and high eccentricity conditions, which may lead to shear fracture and plastic deformation of the clearance neck 43. If the size is too large (greater than 0.73), the clearance neck 43 will be too wide, which will encroach on the space of the slot limit part 311 of the receiving groove 31, reduce the swing flexibility of the slider head 42 in the receiving groove 31, and lead to an increase in material costs.

[0050] Based on the above considerations, this embodiment will By controlling the value between 0.5 and 0.73, it is possible to ensure that the neck 43 has sufficient shear strength while also taking into account the smoothness of movement and manufacturing economy of the sliding structure 4.

[0051] In one embodiment, refer to Figure 6 and Figure 7 The slider head 42 and the clearance neck 43 are connected by a rounded transition part 44; this makes the connection between the slider head 42 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.

[0052] In one embodiment, refer to Figure 6 and Figure 7 The radius of the rounded transition part 44 is 0.1mm~0.5mm, which can ensure stress dispersion effect and facilitate processing and forming.

[0053] In one embodiment, refer to Figure 6 and Figure 7 The diameter D1 of the slider head 42 and the thickness t of the slider body 41 satisfy the following relationship: ; where D1 and t are both in mm.

[0054] Based on the above numerical limitations, it can be ensured that the slider head 42 has sufficient bearing area, avoiding the situation where the slider head 42 is too small (i.e., This can lead to problems such as insufficient load-bearing capacity and decreased sealing performance, while also preventing issues caused by an excessively large sliding vane head size (i.e., ...). This can lead to problems such as motion interference, excessive wear, and material waste, thus ensuring the reliability of the hinged parts while maintaining structural compactness.

[0055] In one embodiment, refer to Figure 6 and Figure 7 The surface roughness Rz of the slider head 42 is ≤3.2um, which can further reduce the friction and wear between the slider head 42 and the receiving groove 31.

[0056] In one embodiment, refer to Figures 1 to 6 The eccentricity e of the eccentric part 21 and the total length Lv of the slider structure 4 satisfy the following: ; where e and Lv are both in mm.

[0057] Specifically, by By controlling the eccentricity to below 0.51, the eccentricity can be effectively controlled, avoiding excessive oscillation of the roller 3 relative to the slide head 42 due to excessive eccentricity. This can prevent the slide head 42 from derailing or causing motion interference, thereby ensuring the motion reliability of the hinge structure.

[0058] In one embodiment, refer to Figures 1 to 6 The pump body components satisfy the following relationship (the units of D1, d, t, Lv, and e are all mm): .

[0059] This embodiment, based on the above embodiment, further limits the ratio X to... Experiments have verified that when the ratio X is within this optimal range, the structural strength, stiffness, and motion reliability of the slider structure 4 under high pressure differential and high eccentricity conditions can be further improved. Furthermore, as... Figure 8 As shown, when X is 0.13~0.2, the oil film thickness formed at the slider head 42 is at a higher level, which can ensure the lubrication performance between the slider head 42 and the receiving groove 31, and further improve the reliability and stability of the hinge fit.

[0060] In one embodiment, refer to Figure 6 and Figure 7 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.

[0061] 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.

[0062] 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.

[0063] 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.

[0064] In one embodiment, refer to Figure 6 and Figure 7 The radius r1 of the first cylindrical segment 421, the radius r3 of the third cylindrical segment 423, and the thickness t of the slider body 41 satisfy the following relationship: r1 + r3 < t; where the units of r1, r3, and t are all mm.

[0065] 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<t, 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 t of the slider body 41 can be avoided.

[0066] In one embodiment, refer to Figure 6 and Figure 7 The second cylindrical segment 422 is located between the first cylindrical segment 421 and the third cylindrical segment 423; the central axis of the first cylindrical segment 421 and the central axis of the third cylindrical segment 423 are collinear, and the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 are the same; where r1, r2 and r3 are all in 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; in such cases... Figure 6 and Figure 7 In the cross-sectional view shown, when the center of the first cylindrical segment 421 and the center of the third cylindrical segment 423 are set concentrically, the center of both the first cylindrical segment 421 and the third cylindrical segment 423 can be the center of the slider head 42.

[0068] Based on the concentric arrangement and equal radius of the first cylindrical segment 421 and the third cylindrical segment 423, the two arc-shaped cylindrical segments form symmetrical bearing areas on the outer circumference of the slider head 42. When the slider head 42 rolls into the receiving groove 31, the first cylindrical segment 421 and the third cylindrical segment 423 can respectively contact the two side walls of the receiving groove 31, thus providing a balanced support force and helping to form a stable and uniform support area in the receiving groove 31. This is beneficial to improving the positioning stability and smooth movement of the slider head 42 in the receiving groove 31.

[0069] It should be noted that the requirement that the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 be the same allows for manufacturing tolerances, and does not require that the radius r1 of the first cylindrical segment 421 and the radius r3 of the third cylindrical segment 423 be exactly equal in actual value; specifically, r1 and r3 can have a tolerance of ±0.008mm.

[0070] Furthermore, based on the above structural configuration, in calculating the above embodiments... When this ratio X is used, the diameter D1 of the slider head 42 can be calculated as the diameter of the circle corresponding to the first cylindrical segment 421 or the third cylindrical segment 423 of the main bearing surface (i.e., 2*r1 or 2*r3).

[0071] In one embodiment, refer to Figure 6 and Figure 7 The radii r1 of the first cylindrical segment 421, r2 of the second cylindrical segment 422, and r3 of the third cylindrical segment 423 satisfy the following relationship: r2 > r1, r2 > r3. Here, the units of r1, r2, and r3 are all mm.

[0072] 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.

[0073] In one embodiment, refer to Figure 6 and Figure 7 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°.

[0074] like Figure 7 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.

[0075] 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.

[0076] In one embodiment, the sliding structure 4 is made of high-speed steel or stainless steel; furthermore, the surface hardness of the sliding structure 4 is greater than HV700. This can further improve the wear resistance and structural strength of the sliding structure 4.

[0077] This application also provides a compressor; please refer to [link / reference]. Figures 1 to 7 The compressor includes the pump assembly in any of the above embodiments.

[0078] 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, by establishing a relationship between the load-bearing capacity of the hinge part, the bending stiffness of the vane body 41 and the degree of matching between the movement amplitude, and limiting their ratio within a preset value range, the various parameters of the vane structure 4 can achieve a good balance. This avoids problems such as material waste, increased moment of inertia and excessive energy consumption caused by an excessively large ratio, and also avoids problems such as stress concentration in the avoidance neck 43, excessive wear of the vane head 42 and seal failure caused by an excessively small ratio. Thus, the vane structure 4 can have sufficient structural strength, stiffness and movement reliability under high pressure differential and high eccentricity conditions.

[0079] This application also provides a refrigeration device; please refer to [link / reference]. Figures 1 to 7 The refrigeration equipment includes the compressor in any of the above embodiments.

[0080] The refrigeration equipment in this embodiment may include air conditioners, refrigerators, etc., and is not limited here.

[0081] 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.

[0082] 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 in that, include: A cylinder has a working chamber inside; the cylinder is also provided with a sliding vane groove, which communicates with the working chamber; A crankshaft having an eccentric portion, wherein the eccentricity of the eccentric portion is e; A roller is fitted onto the eccentric portion; the roller is used to rotate eccentrically along the cavity wall of the working chamber under the drive of the crankshaft; the outer circumference of the roller is provided with a receiving groove that runs through the axial direction. 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 t; the sliding head is rollably fitted in the receiving groove, and the diameter of the sliding head is D1; ​​a groove limiting part is formed at the opening of the receiving groove to cooperate with the clearance neck, and the minimum width of the clearance neck is d; the total length of the sliding structure is Lv. The pump body assembly satisfies the following relationship: 。 2. The pump body assembly according to claim 1, characterized in that, The diameter D1 of the sliding head and the diameter D2 of the receiving groove satisfy the following relationship: .

3. The pump body assembly according to claim 1, characterized in that, The minimum width d of the clearance neck and the thickness t of the slider body satisfy the following: .

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

5. The pump body assembly according to claim 1, characterized in that, The diameter D1 of the slider head and the thickness t of the slider body satisfy the following relationship: .

6. The pump body assembly according to claim 1, characterized in that, The surface roughness Rz of the slider head is ≤3.2um.

7. The pump body assembly according to claim 1, characterized in that, The eccentricity e of the eccentric portion and the total length Lv of the sliding structure satisfy the following: .

8. The pump body assembly according to claim 1, characterized in that, The pump body assembly satisfies the following relationship: 。 9. 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.

10. The pump body assembly according to claim 9, characterized in that, The radius r1 of the first cylindrical segment, the radius r3 of the third cylindrical segment, and the thickness t of the slider body satisfy the following relationship: r1 + r3 < t.

11. The pump body assembly according to claim 9, characterized in that, The second cylindrical segment is located between the first cylindrical segment and the third cylindrical segment; the central axis of the first cylindrical segment and the central axis of the third cylindrical segment are collinear, and the radius r1 of the first cylindrical segment and the radius r3 of the third cylindrical segment are the same.

12. The pump body assembly according to claim 11, 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.

13. The pump body assembly according to claim 12, 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°.

14. The pump body assembly according to any one of claims 1 to 13, characterized in that, The material of the sliding plate structure is high-speed steel or stainless steel; And / or, the surface hardness of the sliding structure is greater than HV700.

15. A compressor, characterized in that, The compressor includes a pump body assembly as described in any one of claims 1 to 14.

16. A refrigeration device, characterized in that, The refrigeration equipment includes the compressor as described in claim 15.

Images