Pump body assembly, compressor and refrigeration device

Abstract

This application discloses a pump body assembly, a compressor, and a refrigeration device. The pump body assembly includes a cylinder, a roller, and a vane. The cylinder has a working chamber and a groove communicating with the working chamber. The outer peripheral wall of the roller is provided with a groove, which includes a circular arc groove and a clearance groove communicating with each other. The vane includes a vane body, a transition part, a clearance part, and a vane head connected in sequence. The minimum thickness of the clearance part is B2, and the angle between the transition part and the thickness direction of the vane is β. The distance between the center of the inner wall of the circular arc and the edge of the maximum groove opening of the groove along a first direction is L1. The minimum distance between the center of the transition part and the center of the outer wall of the circular arc is L2. The diameter of the circular arc groove is d3, the width of the maximum groove opening of the groove is B4, the eccentricity of the crankshaft is e, the distance between the central axis of the roller and the center of the inner wall of the circular arc is L, and the maximum swing angle of the roller around the vane is α, where α = arcsin(e / L), and the value of α is in the range of 1 to 3.

Description

Technical Field

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

[0002] In related technologies, the compressor pump assembly is the core component for gas compression. The pump assembly typically includes a cylinder, rollers eccentrically mounted on a crankshaft, and vanes that slide radially within grooves on the cylinder. The vanes and rollers work together to divide the cylinder cavity into an intake chamber and a compression chamber, achieving refrigerant intake, compression, and discharge through volume changes. Existing designs for the roller-vane fit are flawed, affecting not only the sealing between them but also causing motion interference, thus impacting the compressor's energy efficiency and reliability. Summary of the Invention

[0003] The main objective of this invention is to provide a pump assembly, compressor, and refrigeration equipment that improves the sealing between the vane and the roller and avoids motion interference between the vane and the roller, thereby improving the energy efficiency and reliability of the compressor.

[0004] To achieve the above objectives, this application proposes a pump body assembly, which includes: A cylinder having a working chamber and a groove communicating with the working chamber; A roller is used to be driven by a crankshaft to oscillate eccentrically within the working cavity. The outer peripheral wall of the roller is provided with a groove, the groove including a connected arc groove and a clearance groove. The clearance groove is located on the side of the arc groove close to the outer peripheral wall of the roller, and the arc groove has an arc inner wall surface. A sliding vane includes a vane body, a transition portion, a clearance portion, and a vane head connected in sequence. The vane body is slidably disposed in the groove along the radial direction of the cylinder. At least a portion of the clearance portion is disposed in the clearance groove. The vane head has an arcuate outer wall surface and is rotatably connected to the arcuate groove. The minimum thickness of the clearance portion is B2. The thickness of the transition portion gradually decreases along the direction from the vane body to the vane head. The angle between the transition portion and the thickness direction of the vane is β. The central axis of the roller extends from the arcuate groove to the inner edge of the groove. The direction of the center of the wall surface is the first direction, and the distance between the center of the inner arc wall surface along the first direction and the edge of the largest groove of the groove is L1; the minimum distance between the transition part and the center of the outer arc wall surface is L2, the diameter of the arc groove is d3, the width of the largest groove of the groove is B4, the eccentricity of the crankshaft is e, the distance between the central axis of the roller and the center of the inner arc wall surface is L, and the maximum swing angle of the roller around the slide is α, where α = arcsin(e / L). satisfy: .

[0005] In some embodiments, α and β satisfy: .

[0006] In some embodiments, the minimum opening width of the groove is B3, where B3 satisfies: .

[0007] In some embodiments, B3 and d3 satisfy: .

[0008] In some embodiments, B2 and d3 satisfy: ,and .

[0009] In some embodiments, the thickness of the slider body is T, and T and B2 satisfy: .

[0010] In some embodiments, the thickness of the slider body is T, and T and d3 satisfy: .

[0011] In some embodiments, the slider head has a first arc segment, a second arc segment, and a third arc segment arranged and connected sequentially along the thickness direction of the slider. The radius of curvature of the first arc segment and the radius of curvature of the third arc segment are both smaller than the radius of curvature of the second arc segment. The center of the second arc segment is located between the center of the first arc segment and the slider body. The included angle between the two lines connecting the two ends of the second arc segment to the center of the first arc segment or the third arc segment is γ, where γ satisfies: .

[0012] In some embodiments, the direction from the slider body to the slider head is a second direction, the first arc segment and the third arc segment are located on both sides of the second arc segment along the second direction, the radius of curvature of the first arc segment and the radius of curvature of the third arc segment are the same, and the sum of the radius of curvature of the first arc surface and the radius of curvature of the second arc surface is d4, wherein d4 and d3 satisfy: .

[0013] This application also proposes a compressor, which includes a motor and a pump assembly as described above, the pump assembly including a crankshaft, the piston being sleeved around the crankshaft, and the motor being drivenly connected to the crankshaft.

[0014] This application also proposes a refrigeration device, which includes a compressor as described above.

[0015] In the technical solution of this application, the outer peripheral wall of the roller is provided with a groove, the groove including a connected arc groove and a clearance groove, the slide includes a slide body, a transition part, a clearance part and a slide head connected in sequence, at least part of the clearance part is provided in the clearance groove, during the movement of the slide, the clearance groove can make way for the structure between the slide body and the slide head; the slide head has an arc outer wall surface and is rotatably connected to the arc groove, so that the slide head and the arc groove form a continuous surface contact fit, which is beneficial to the high pressure sealing and force transmission between the slide and the roller; and, by limiting The value of is within the range of 1 to 3, ensuring that when the roller oscillates eccentrically within the working chamber, the groove opening will not collide or wear with the structure between the vane body and the vane head. Furthermore, it can reduce the clearance volume between the vane and the roller, suppressing high-pressure gas leakage, thereby improving the compressor's refrigeration efficiency. Therefore, the technical solution of this application optimizes the structure and geometric parameters of the vane and roller mating, which is beneficial for improving the sealing performance between the vane and the roller, and can also avoid motion interference between the vane and the roller, thereby improving the compressor's energy efficiency and reliability. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of a pump body assembly according to an embodiment of the present invention; Figure 2 for Figure 1 A structural diagram of part of the structure from another perspective; Figure 3 for Figure 2 A schematic diagram of the structure when the roller swings around the slider at the maximum angle α; Figure 4 for Figure 3 Enlarged view of some of the structures in the image; Figure 5 for Figure 2 A schematic diagram of the roller structure in the middle; Figure 6 for Figure 5 Enlarged view of some of the structures in the image; Figure 7 This is a schematic diagram of the slider in Figure 2; Figure 8 for Figure 7 A structural diagram from another perspective; Figure 9 for Figure 8 Enlarged view of some of the structures in the image; Figure 10 for Figure 2 Enlarged view of some of the structures in the image; Figure 11 for Figure 3 Enlarged view of some of the structures.

[0018] Explanation of icon numbers: 10. Pump body assembly; 100. Cylinder; 110. Working chamber; 120. Slide groove; 200. Roller; 210. Groove; 211. Arc groove; 212. Clearance groove; 300, slider; 310, slider body; 320, transition section; 330, clearance section; 340, slider head; 341, first arc segment; 342, second arc segment; 343, third arc segment; 400. Crankshaft.

[0019] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0020] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0021] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0022] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0023] In related technologies, the compressor pump assembly is the core component for gas compression. The pump assembly typically includes a cylinder, rollers eccentrically mounted on a crankshaft, and vanes that slide radially within grooves on the cylinder. The vanes and rollers work together to divide the cylinder cavity into an intake chamber and a compression chamber, achieving refrigerant intake, compression, and discharge through volume changes. Existing designs for the roller-vane fit are flawed, affecting not only the sealing between them but also causing motion interference, thus impacting the compressor's energy efficiency and reliability.

[0024] Based on this, this application proposes a pump body assembly. By optimizing the structure and geometric parameters of the sliding vane and roller mating, the pump body assembly can improve the sealing performance between the sliding vane and roller and avoid motion interference between the sliding vane and roller, thereby improving the energy efficiency and reliability of the compressor.

[0025] Please see Figures 1 to 11In one embodiment of the present invention, the pump body assembly 10 includes a cylinder 100, a roller 200, and a vane 300. The cylinder 100 has a working chamber 110 and a groove 120 communicating with the working chamber 110. The roller 200 is driven by the crankshaft 400 to eccentrically swing within the working chamber 110. A groove 210 is provided on the outer peripheral wall of the roller 200. The groove 210 includes a circular arc groove 211 and a clearance groove 212 communicating with each other. The clearance groove 212 is located on the side of the circular arc groove 211 near the outer peripheral wall of the roller 200. The circular arc groove 211 has a circular arc inner wall surface. The vane 300 includes a vane body 310, a transition portion 320, a clearance portion 330, and a vane head 340 connected in sequence. The vane body 310 is slidably disposed in the groove 120 along the radial direction of the cylinder 100. At least part of the clearance portion 330 is disposed in the clearance groove 212. The vane head 340 has a circular arc inner wall surface. The outer wall surface is rotatably connected to the arc groove 211. The minimum thickness of the clearance part 330 is B2. The thickness of the transition part 320 is gradually reduced along the direction from the slide body 310 to the slide head 340. The angle between the thickness direction of the transition part 320 and the slide 300 is β. The direction from the central axis of the roller 200 to the center of the arc inner wall surface is the first direction. The distance between the center of the arc inner wall surface and the edge of the maximum groove of the groove 210 along the first direction is L1. The minimum distance between the transition part 320 and the center of the arc outer wall surface is L2. The diameter of the arc groove 211 is d3. The width of the maximum groove of the groove 210 is B4. The eccentricity of the crankshaft 400 is e. The distance between the central axis of the roller 200 and the center of the arc inner wall surface is L. The maximum swing angle of the roller 200 around the slide 300 is α, where α = arcsin(e / L). satisfy: .

[0026] It is understood that the pump body assembly 10 can be applied to a rotary compressor. The compressor includes a housing, a motor, and the pump body assembly 10, both of which are housed within the housing. Wherein, as... Figure 1 As shown, the pump body assembly 10 includes a cylinder 100, a roller 200, a vane 300, and a crankshaft 400. The pump body assembly 10 may also include an elastic element (not shown), which is mounted on the cylinder 100 and abuts against the end of the vane 300 away from the roller 200. The roller 200 is eccentrically and oscillatingly positioned within the working chamber 110 of the cylinder 100, and is sleeved around the eccentric portion of the crankshaft 400. One end of the crankshaft 400 is connected to the motor. The output shaft is driven and connected; the slide body 310 is reciprocally slidably disposed in the slide groove 120 of the cylinder 100, the slide head 340 has an arc outer wall surface and is rotatably connected to the arc groove 211, and the working chamber 110 of the cylinder 100 can be divided into an intake chamber and an exhaust chamber by the slide 300 and the roller 200; the cylinder 100 is also provided with an air inlet and an air outlet communicating with the working chamber 110, the air inlet communicating with the intake chamber and the air outlet communicating with the exhaust chamber.

[0027] When the compressor is working, the crankshaft 400 is driven to rotate by the motor. The crankshaft 400 drives the roller 200 to swing eccentrically in the cylinder 100. The vane 300 and the roller 200 divide the working chamber 110 into an intake chamber and an exhaust chamber. As the roller 200 rotates continuously, the volume of the intake chamber and the exhaust chamber changes continuously, so that atmospheric or low-pressure gas enters the intake chamber and is compressed to form high-pressure gas that is discharged from the exhaust chamber, thereby realizing the compression function.

[0028] The cylinder 100 has an annular structure, and the inner circumferential surface of the cylinder 100 forms a working cavity 110 for accommodating the roller 200. The cylinder wall of the cylinder 100 is provided with a sliding groove 120 for accommodating the sliding vane 300. The sliding groove 120 extends radially along the cylinder 100 and communicates with the working cavity 110. The sliding groove 120 passes through both axial end faces of the cylinder 100.

[0029] The roller 200 has an annular structure, and its central axis is offset from the central axis of the working cavity 110. A crankshaft 400 passes through the inner cavity of the roller 200. Rotation of the crankshaft 400 can drive the roller 200 to eccentrically oscillate within the working cavity 110. A groove 210 is provided on the outer peripheral wall of the roller 200. The groove 210 includes a connected arc groove 211 and a clearance groove 212. The arc groove 211 has an arc inner wall surface. The clearance groove 212 is located on the side of the arc groove 211 closer to the outer peripheral wall of the roller 200, that is, one end of the clearance groove 212 is connected to the arc groove 211. The outermost groove formed at the other end of the clearance groove 212 is the outermost groove of the groove 210. For example, the largest groove at the end of the clearance groove 212 away from the arc groove 211 is the largest groove of the groove 210. The shape and size of the clearance groove 212 are not limited. At least a portion of the clearance portion 330 is provided within the clearance groove 212. The clearance groove 212 is used to avoid the structure between the slide body 310 and the slide head 340. Exemplarily, the clearance groove 212 is used to avoid at least a portion of the clearance portion 330. Furthermore, as the slide 300 slides, the clearance groove 212 is also used to avoid the transition portion 320. This arrangement ensures that the roller 200 does not interfere with the movement of the slide 300 when it eccentrically oscillates within the working cavity 110. Exemplarily, the width of the groove opening of at least a portion of the clearance groove 212 gradually widens from the central axis of the roller 200 toward the outer peripheral wall of the roller 200.

[0030] The slider 300 includes a slider body 310, a transition portion 320, a clearance portion 330, and a slider head 340 connected in sequence. The slider body 310 has a rectangular structure. The thickness of the transition portion 320 is gradually reduced along the direction from the slider body 310 to the slider head 340, forming a gradually changing cross section. The gradually reduced transition portion 320 acts as a flexible hinge. The transition portion 320 can more smoothly transmit and redistribute the uneven load from the slider body 310 to the slider head 340, which helps to reduce stress concentration and the risk of fatigue fracture of the slider 300 under alternating loads. The clearance portion 330 has an inwardly recessed necked structure to provide additional degrees of freedom of movement for the slide 300; the slide head 340 has an arc-shaped outer wall surface to form a rotating pair. The slide head 340 is disposed in the arc groove 211 and rotatably connected to the arc groove 211. The arc-shaped outer wall surface of the slide head 340 can form a continuous surface contact fit with the arc-shaped inner wall surface of the arc groove 211, which is beneficial to the high-pressure sealing and force transmission between the slide 300 and the roller 200.

[0031] like Figure 9 As shown, the minimum thickness of the clearance portion 330 is B2, that is, the minimum material thickness of the clearance portion 330 on the cross section along the thickness direction of the slider 300 is B2; the angle between the transition portion 320 and the thickness direction of the slider 300 is β, that is, the inclination of the transition portion 320 relative to the thickness direction of the slider 300 is β, the transition portion 320 and the clearance portion 330 are connected by an arc transition, and the outline of the transition portion 320 can be a straight line, that is, the acute angle formed by the generatrix of the outline of the straight transition portion 320 and the reference line of the thickness direction of the slider 300 is β.

[0032] like Figure 6 As shown, the direction from the central axis of roller 200 to the center of the inner wall of the arc is the first direction X. The distance between the center of the inner wall of the arc and the edge of the largest groove of the groove 210 along the first direction is L1. The first direction X is the radial direction pointing from the central axis of roller 200 as the origin to the center of the inner wall of the arc groove 211. Along the first direction, the straight-line distance from the center of the arc groove 211 to the outermost edge point of the overall contour of the groove 210 in this direction is L1. L1 represents the degree of outward expansion of the groove 210 in the radial direction of roller 200.

[0033] like Figure 9 As shown, the minimum distance between the transition portion 320 and the center of the arc outer wall is L2, that is, the shortest straight-line distance between the outline of the transition portion 320 and the center of the arc outer wall of the slider head 340 is L2. L2 represents the shortest distance from the transition portion 320 to the rotation center of the slider head 340. By limiting the lower limit value of L2, it is ensured that the slider head 340 has an interference-free rotation space within the required rotation angle range.

[0034] like Figure 6As shown, the diameter of the arc groove 211 is d3, meaning the outline diameter of the arc groove 211 on the roller 200 used to accommodate the slider head 340 is d3. d3 defines the radius of curvature of the outer arc wall surface of the slider head 340 that it is adapted to. The maximum width of the groove 210 is B4, meaning the maximum width of the outermost groove of the groove 210 is B4, that is, the width of the groove formed by the clearance groove 212 away from the outermost end of the arc groove 211 is B4.

[0035] like Figure 4 As shown, the eccentricity of the crankshaft 400 is e, which is the straight-line distance between the rotation center of the crankshaft 400 that drives the roller 200 and the geometric center of the roller 200 itself. The roller 200 is sleeved on the eccentric part of the crankshaft 400. When the crankshaft 400 rotates, the geometric center of the roller 200 will make a circular motion with a radius of e around the rotation center of the crankshaft 400. The roller 200 will make a combined translational and rolling motion in the working cavity 110, that is, eccentric oscillation.

[0036] like Figure 3 and 4 As shown in the diagram, the position of roller 200 is the leftmost position of roller 200 swinging around slider 300 to the working cavity 110. Of course, roller 200 also has the potential to swing around slider 300 to the rightmost position of working cavity 110 (not shown). When roller 200 swings to the leftmost or rightmost position of working cavity 110, the angle of swing of roller 200 is α, which refers to the maximum relative swing angle that the central axis of roller 200 can form around the rotation center of slider head 340. In a triangle, the included angle is α, the length of the hypotenuse is L, and the length of the opposite side is e. According to the sine formula, α = arcsin(e / L).

[0037] like Figure 10 As shown, with the center of the inner arc of the circular arc groove 211 as the origin and the height of the edge of the largest groove opening of the groove 210 as L2, an xy coordinate system is established. In this xy coordinate system, the outline of the transition part 320 is defined as a straight line LP. The equation of the straight line LP is y=-tanβ+C, where β is an acute angle and C=L2-tanβ*B2 / 2. From this, we can obtain: tanβx+y+tanβ*B2 / 2-L2=0. like Figure 11 As shown, Figure 11 The roller 200 in the middle is relative to Figure 10 The roller 200 in the middle swung to the left, with a maximum swing angle of α. Figure 4It can be seen that sinα=e / L; the outline of the transition part 320 is defined as the straight line LP. The center of the inner wall of the circular arc groove 211 is taken as the origin. The xy coordinate system and the x'y' coordinate system are established. The x'y' coordinate system is rotated by an angle α relative to the xy coordinate system in the clockwise direction.

[0038] In the xy coordinate system, the equation of line LP is: Ax + By + C = 0; The xy coordinate system is rotated clockwise by α to obtain the x'y' coordinate system. In the x'y' coordinate system, the equation of the line LP is: (Acosα-Bsinα)x'+(Asinα+Bcosα)y'+C=0; As mentioned above, tanβx+y+tanβ*B2 / 2-L2=0; that is, A=tanβ, B=1, C=tanβ*B2 / 2-L2; Therefore, in the x'y' coordinate system, the equation of line LP is: (tanβcosα-sinα)x'+ (tanβsinα+cosα)y'+tanβ*B2 / 2-L2=0; The width of the maximum opening of groove 210 is B4. Let point K be the left edge point of the maximum opening of groove 210. In the x'y' coordinate system, the coordinates of point K are (-B4 / 2, L1). Substituting the coordinates of K (-B4 / 2, L1) into the formula (tanβcosα-sinα)x'+(tanβsinα+cosα)y'+tanβ*B2 / 2-L2=0, we can obtain: (tanβcosα-sinα)*(-B4 / 2)+(tanβsinα+cosα)L1+tanβ*B2 / 2-L2=0; We further obtain: 2L1(tanβsinα+cosα)+B2tanβ=B4(tanβcosα-sinα)+2L2; The position of the roller 200 at the maximum swing angle α is the limit position of the roller 200 swing. When the roller 200 is at the limit position, point K must always be below the outline line LP of the transition part 320 to avoid interference between the groove of the groove 210 and the slider 300, that is, (tanβcosα-sinα)*(-B4 / 2)+(tanβsinα+cosα)L1+tanβ*B2 / 2-L2<0; Furthermore, we can obtain: Furthermore, in order to enable the vane 300 and roller 200 to accommodate pump body assemblies 10 of different sizes to adapt to different models of compressors, the following limitations are specified: This improves the applicability of the pump body assembly. For example, The value can be: 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, 2.0, 2.1, 2.2, 2.3, 2.4, 2.5, 2.6, 2.7, 2.8 or 2.9, or any other value within the above range.

[0039] In the technical solution of this application, the outer peripheral wall of the roller 200 is provided with a groove 210, the groove 210 including a connected arc groove 211 and a clearance groove 212, the slide 300 includes a slide body 310, a transition portion 320, a clearance portion 330 and a slide head 340 connected in sequence, at least part of the clearance portion 330 is provided in the clearance groove 212, during the movement of the slide 300, the clearance groove 212 can make way for the structure between the slide body 310 and the slide head 340; the slide head 340 has an arc outer wall surface and is rotatably connected to the arc groove 211, so that the slide head 340 and the arc groove 211 form a continuous surface contact fit, which is beneficial to the high pressure sealing and force transmission between the slide 300 and the roller 200; and, by limiting The value of is within the range of 1 to 3, ensuring that when the roller 200 oscillates eccentrically within the working chamber 110, the groove opening of the groove 210 will not collide or wear with the structure between the vane body 310 and the vane head 340. Furthermore, it can reduce the clearance volume between the vane 300 and the roller 200, suppressing high-pressure gas leakage, thereby improving the compressor's refrigeration efficiency. Therefore, the technical solution of this application optimizes the structure and geometric parameters of the cooperation between the vane 300 and the roller 200, which is beneficial to improving the sealing performance between the vane 300 and the roller 200, and can also avoid motion interference between the vane 300 and the roller 200, thereby improving the compressor's energy efficiency and reliability.

[0040] In one embodiment, α and β satisfy: This setting further restricts... The value ranges from 1.5 to 2.5, ensuring that when the roller 200 oscillates eccentrically within the working chamber 110, the groove 210 will not collide or wear with the structure between the vane body 310 and the vane head 340. Furthermore, it reduces the clearance volume between the vane 300 and the roller 200, suppressing high-pressure gas leakage and thus improving the compressor's refrigeration efficiency. Therefore, the technical solution of this application optimizes the structure and geometric parameters of the cooperation between the vane 300 and the roller 200, which improves the sealing performance between them and avoids motion interference, thereby improving the compressor's energy efficiency and reliability.

[0041] For example, The value can be 1.6, 1.7, 1.8, 1.9, 2.0, 2.1, 2.2, 2.3 or 2.4, or any other value within the above range.

[0042] In one embodiment, the minimum opening width of the groove is B3, where B3 satisfies: .

[0043] like Figure 6 As shown, the minimum width of the groove 210 is B3, that is, the minimum width of the groove at the connection between the arc groove 211 and the clearance groove 212 is B3, which means that the minimum width of the transition area between the arc groove 211 and the clearance groove 212 in the groove 210 on the outer peripheral wall of the roller 200 is B3.

[0044] For example, the groove at the connection between the arc groove 211 and the clearance groove 212 is formed by two parallel straight sections and two inclined flared sections. During the operation of the compressor, the crankshaft 400 drives the roller 200 to rotate eccentrically. The straight section of the groove directly pushes the vane head 340. The vane 300 makes radial reciprocating motion in the slide groove 120. During this process, the vane head 340 is closely attached to the arc inner wall of the arc groove 211. Under the action of gas pressure and centrifugal force, it is automatically pressed together to form a self-reinforcing surface seal effect, which effectively blocks the refrigerant leakage between the high and low pressure chambers. Because the slider head 340 is confined within the arc groove 211, the roller 200 cannot rotate freely around its own axis and can only oscillate relative to the slider 300 at a limited angle. During this oscillation, the clearance portion 330 and the groove openings at the junctions of the arc groove 211 and the clearance groove 212 always remain in a non-contact but adjacent state to compensate for manufacturing tolerances and absorb high-frequency vibrations, avoiding edge stress concentration or fretting wear caused by rigid constraints. This allows the slider 300 and the roller 200 to have oscillation freedom, retaining assembly tolerances, while suppressing rotational freedom, thus balancing reliability and functionality. The difference between B3 and B2 represents the total clearance between the two sides of the clearance portion 330 of the slider 300 and the groove openings at the junctions of the arc groove 211 and the clearance groove 212. The clearance on one side is approximately equal to (B3-B2) / 2.

[0045] The clearance ratio reflects the balance between relative motion degrees of freedom and structural compactness, ensuring that the slider head 340 has sufficient swing space within the slot where the arc groove 211 and the clearance groove 212 connect. If the value is too small, such as less than 0.2, the gap will be too narrow. During high-frequency reciprocating motion, the slider 300 is prone to interference or jamming with the groove edge where it connects to the arc groove 211 and the clearance groove 212. The roller 200 will be unable to achieve the necessary micro-oscillation, leading to stress concentration or abnormal wear due to forced constraint. This solution limits... This ensures that the groove opening at the junction of the arc groove 211 and the clearance groove 212 has sufficient clearance to allow the sliding head 340 to automatically adjust its posture under centrifugal force and gas pressure, so that the arc outer wall surface of the sliding head 340 can tightly fit the arc inner wall surface of the arc groove 211 to form a dynamic seal. For example, The value can be 0.21, 0.23, 0.25, 0.28, 0.29, 0.30, 0.32, 0.34, 0.35, 0.38, 0.40, 0.45, 0.5, etc., and the specific value is not limited here.

[0046] This solution limits the minimum opening width of the groove 210 to B3, and satisfies... The geometric relationship is optimized to solve the problems of poor sealing caused by line contact between the vane 300 and the roller 200 in traditional rotary compressors, as well as low-frequency disengagement or high-frequency vibration caused by reliance on spring reset. Under low-frequency operating conditions, the eccentric force of the roller 200 is small, but the vane head 340 can still be reliably driven through mechanical engagement with the slot at the connection point between the arc groove 211 and the clearance groove 212, avoiding vane 300 disengagement and impact noise caused by insufficient force in traditional springs. Under high-frequency operating conditions, the vane 300 moves synchronously with the motor, without spring response lag, suppressing the risk of resonance and fatigue fracture. This design ensures the assembly clearance between the clearance portion 330 of the slide vane 300 and the groove 210 of the roller 200, as well as the space for lubricating oil to flow into the arc groove 211 from this clearance. Furthermore, the wrap angle of the slide vane head 340 is greater than 180° and forms continuous surface contact with the arc groove 211, maintaining stable sealing performance regardless of operating frequency, reducing cross-contamination between high and low pressure chambers, and improving volumetric efficiency and energy efficiency ratio. Moreover, the roller 200 is confined within the groove 210, only allowing limited oscillation and preventing free rotation, effectively isolating the heat conduction path between the high-temperature, high-pressure zone and the low-temperature, low-pressure zone, significantly reducing cold loss; it also blocks the channel for lubricating oil to surge from the high-pressure side to the low-pressure side, fundamentally suppressing oil leakage and ensuring lubrication stability. Even if minor wear occurs on the surface of the slide vane 300 and the groove wall of the groove 210 during long-term operation, due to… This design ensures that a reasonable dynamic gap is reserved between the clearance part 330 and the groove 210, allowing the vane 300 and roller 200 to maintain smooth movement without jamming, thus ensuring the reliable operation of the compressor throughout its entire life cycle.

[0047] In one embodiment, B3 and d3 satisfy: It is understandable that the ratio of the minimum width B3 of the groove at the connection between the arc groove 211 and the clearance groove 212 to the diameter d3 of the arc groove 211 directly affects the sealing angle, structural strength, and movement clearance. If B3 is too large, the opening at the connection between the arc groove 211 and the clearance groove 212 will be too wide, weakening the embedding depth of the sliding head 340 and reducing the effective sealing arc length; conversely, if B3 is too small, it may restrict the passage of the clearance part 330, causing assembly difficulties or dynamic interference. By limiting... The opening at the junction of the arc groove 211 and the clearance groove 212 is ensured to be not too wide, so that the embedding depth of the sliding vane head 340 in the groove 210 is sufficient, and the effective sealing arc length is maintained. This prevents the sliding vane head 340 from being pushed out of the groove 210 by gas pressure under high-pressure conditions, thereby improving the isolation capability of the high and low pressure chambers and reducing internal leakage. For example, the value of B3 / d3 can be 0.8, 0.82, 0.84, 0.86, 0.88, 0.9, 0.92, 0.94, 0.96, 0.98, or 1.0, or any other value within the above range.

[0048] In one embodiment, B2 and d3 satisfy: ,and .

[0049] Understandable, >0.5 ensures that the clearance part 330 has sufficient thickness relative to the arc groove 211, so that it has sufficient bending and shear resistance when subjected to high frequency alternating loads, and avoids early fatigue fracture caused by the clearance part 330 being too thin. This allows the clearance portion 330 to be arranged in a constricted shape relative to the slider head 340, so as to guide the load to smoothly transition from the slider body 310 to the slider head 340 and prevent stress from abruptly concentrating at the connection. This ensures that even in a small compressor, the gap between the clearance portion 330 and the groove openings of the arc grooves 211 and 212 still has a reasonable thickness of solid material. This prevents the clearance portion 330 of the vane 300 from breaking due to its small size, and also avoids insufficient wall thickness and plastic deformation at the groove openings of the arc grooves 211 and 212 due to excessive B2. For example, The value can be 0.52, 0.55, 0.6, 0.65, 0.7, 0.75, 0.8, 0.85, etc., or any other value within the above range; The value can be 0.52, 0.55, 0.6, 0.65, 0.7, 0.75, 0.8, 0.85, etc., and the specific value is not limited here.

[0050] In one embodiment, the thickness of the slider body is T, and T and B2 satisfy: .

[0051] like Figure 9 As shown, the thickness of the slider body 310 is T, that is, the thickness dimension of the slider 300 that mates with the groove 120 of the cylinder 100 is T. The minimum thickness of the clearance part 330 is B2. This ensures that the clearance portion 330 of the slider 300 has sufficient thickness relative to the slider body 310 of the slider 300, thereby ensuring that the clearance portion 330 of the slider 300 has sufficient structural strength and manufacturability, and avoiding fatigue fracture caused by the clearance portion 330 being too thin. For example, The value can be 0.4, 0.45, 0.5, 0.55, 0.6, 0.65, 0.7, 0.75 or 0.8, or any other value within the above range.

[0052] In one embodiment, the thickness of the slider body 310 is T, and T and d3 satisfy: .

[0053] like Figure 9 As shown, the thickness of the slider body 310 is T, that is, the thickness dimension of the slider 300 that mates with the groove 120 of the cylinder 100 is T. The diameter of the arc groove 211 is d3, and the size of d3 limits the size of the slider head 340. This design ensures that the size of the vane head 340 is approximately equal to the thickness of the vane body 310. This results in a smoother load transfer from the vane body 310 to the vane head 340, reducing the risk of stress concentration and improving the structural reliability of the vane head 340. Furthermore, the approximate equality of the size of the vane head 340 to the thickness of the vane body 310 ensures sufficient contact area between the vane head 340 and the arc groove 211, facilitating the formation of a stable high-pressure sealing surface and force transmission, thus improving the reliability of the pump assembly 10. For example, The value can be 0.91, 0.92, 0.93, 0.94, 0.95, 0.96, 0.97, 0.98 or 0.99, or any other value within the above range.

[0054] Please see Figure 9 In one embodiment, the slider head 340 has a first arc segment 341, a second arc segment 342, and a third arc segment 343 arranged and connected sequentially along the thickness direction of the slider. The radius of curvature of the first arc segment 341 and the radius of curvature of the third arc segment 343 are both smaller than the radius of curvature of the second arc segment 342. The center of the second arc segment 342 is located between the center of the first arc segment 341 and the slider body 310. The included angle between the two lines connecting the two ends of the second arc segment 342 to the center of the first arc segment 341 or the center of the third arc segment 343 is γ, and γ satisfies: .

[0055] It is understandable that the first arc segment 341, the second arc segment 342, and the third arc segment 343 can form a continuous surface contact fit with the inner arc wall surface of the arc groove 211, which is beneficial to the high-pressure sealing and force transmission between the sliding plate 300 and the roller 200. The radius of curvature of the second arc segment 342 is greater than that of the first arc segment 341. Of course, the radius of curvature of the second arc segment 342 can also be greater than that of the third arc segment 343, and so on. Figure 9 As shown, the center of the first arc segment 341 is point O1, and the center of the second arc segment 342 is point O2. The center O2 of the second arc segment 342 is located between the center O1 of the first arc segment 341 and the slider body 310. The outer wall surface of the slider head 340 is generally arc-shaped. The radius of curvature of the second arc segment 342 is larger, and the curvature of the second arc segment 342 is flatter. The radii of curvature of the first arc segment 341 and the third arc segment 343 on both sides are smaller, and the curvature of the first arc segment 341 and the third arc segment 343 is more rounded. This configuration ensures that during the insertion of the slider head 340 into the arc groove 211, the first and third arc segments 341 on both sides preferentially contact and bear pressure with the inner arc wall of the arc groove 211, while the second arc segment 342 acts as a transition section, gradually conforming to the bottom of the arc groove 211 during subsequent movements. This avoids localized stress concentration or impact damage caused by instantaneous high pressure, and helps improve the uniformity of force distribution and wear. This arrangement allows the second arc segment 342 to occupy a wider central area of ​​the vane head 340, which helps increase the effective contact area between the vane head 340 and the arc groove 211, enhancing sealing performance and contact stability. Especially under high pressure or high exhaust temperature conditions, this helps maintain continuous and uniform surface contact, reducing localized leakage and improving volumetric efficiency. An angle γ that is too large will result in the widths of the first arc segment 341 and the third arc segment 343 being too narrow, reducing the stiffness of the fit between the slider head 340 and the arc groove 211, and making it difficult for the minimum thickness B2 of the clearance portion 330 to meet the strength requirements. For example, the value of the included angle γ can be: , , , , , , , , , , , , , Or 115 Of course, it can also be any other value within the above interval.

[0056] In one embodiment, the direction from the slider body 310 to the slider head 340 is the second direction. The first arc segment 341 and the third arc segment 343 are located on both sides of the second arc segment 342 along the second direction. The radius of curvature of the first arc segment 341 and the radius of curvature of the third arc segment 343 are the same. The sum of the radius of curvature of the first arc surface and the radius of curvature of the second arc surface is d4. d4 and d3 satisfy: .

[0057] It is understandable that the radius of curvature of the first arc segment 331 is the same as that of the third arc segment 333, that is, the radius of curvature of the first arc segment 331 and the radius of curvature of the third arc segment 333 can be the same. Of course, the radius of curvature of the first arc segment 331 and the radius of curvature of the third arc segment 333 can also have a certain difference, which can be the manufacturing tolerance of the first arc segment 331 and the third arc segment 333.

[0058] The radius of curvature of the first arc segment 341 and the third arc segment 343 are the same, making them symmetrically arranged along the axial direction on the slide head 340. Furthermore, the first and third arc segments 341 and 343 are located on either side of the second arc segment 342, ensuring symmetrical and balanced contact between the first and third arc segments 341 and the arc groove 211. This improves the sealing performance and contact stability between the slide head 340 and the arc groove 211. Since d4 is less than d3, a gap is formed between the first and second arc surfaces and the groove wall of the arc groove 211. This gap facilitates the flow of lubricating oil, reducing frictional power consumption and wear between the slide 300 and the roller 200.

[0059] The present invention also proposes a compressor, which includes a motor and a pump body assembly 10. The pump body assembly 10 includes a crankshaft 400, rollers 200 sleeved around the crankshaft 400, and the motor is drivenly connected to the crankshaft 400. The specific structure of the pump body assembly 10 is as described in the above embodiments. Since this compressor adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought about by the technical solutions of the above embodiments, which will not be described in detail here.

[0060] The compressor can be a rotating roller compressor 200, including but not limited to a single-cylinder rotating rotor compressor and a double-cylinder rotating rotor compressor. The output end of the motor is connected to the crankshaft 400. When the compressor is working, the motor drives the crankshaft 400 to rotate, and the crankshaft 400 drives the rollers 200 to rotate eccentrically within the cylinder 100. The vanes 300 and the rollers 200 divide the working chamber 110 into an intake chamber and an exhaust chamber. As the rollers 200 rotate continuously, the volume of the intake chamber and the exhaust chamber changes continuously, allowing atmospheric or low-pressure gas to enter the intake chamber and be compressed into high-pressure gas, which is then discharged from the exhaust chamber, thus achieving the compression function. By optimizing the structure and geometric parameters of the groove 210 where the rollers 200 and the vanes 300 mate, the pump body assembly 10 can ensure the structural strength of the connection between the vanes 300 and the rollers 200, and also reduce the frictional power consumption between the vanes 300 and the rollers 200, thereby improving the energy efficiency of the compressor.

[0061] This invention also proposes a refrigeration device, including a compressor. The specific structure of the compressor is as described in the above embodiments. Since this refrigeration device adopts 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, which will not be elaborated upon here. The refrigeration device includes, but is not limited to, air conditioners, refrigerators, etc.

[0062] The above description is merely an exemplary embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made using the contents of the present invention specification and drawings under the technical concept of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A pump body assembly, characterized in that, include: A cylinder having a working chamber and a groove communicating with the working chamber; A roller is used to be driven by a crankshaft to oscillate eccentrically within the working cavity. The outer peripheral wall of the roller is provided with a groove, the groove including a connected arc groove and a clearance groove. The clearance groove is located on the side of the arc groove close to the outer peripheral wall of the roller, and the arc groove has an arc inner wall surface. A sliding vane includes a vane body, a transition portion, a clearance portion, and a vane head connected in sequence. The vane body is slidably disposed in the groove along the radial direction of the cylinder. At least a portion of the clearance portion is disposed in the clearance groove. The vane head has an arcuate outer wall surface and is rotatably connected to the arcuate groove. The minimum thickness of the clearance portion is B2. The thickness of the transition portion gradually decreases along the direction from the vane body to the vane head. The angle between the transition portion and the thickness direction of the vane is β. The central axis of the roller extends from the arcuate groove to the inner edge of the groove. The direction of the center of the wall surface is the first direction, and the distance between the center of the inner arc wall surface along the first direction and the edge of the largest groove of the groove is L1; the minimum distance between the transition part and the center of the outer arc wall surface is L2, the diameter of the arc groove is d3, the width of the largest groove of the groove is B4, the eccentricity of the crankshaft is e, the distance between the central axis of the roller and the center of the inner arc wall surface is L, and the maximum swing angle of the roller around the slide is α, where α = arcsin(e / L). satisfy: .

2. The pump body assembly as claimed in claim 1, characterized in that, The α and β satisfy: .

3. The pump body assembly as claimed in claim 1, characterized in that, The minimum opening width of the groove is B3, and B3 satisfies: .

4. The pump body assembly as claimed in claim 3, characterized in that, B3 and d3 satisfy: .

5. The pump body assembly as claimed in claim 3, characterized in that, B2 and d3 satisfy: ,and .

6. The pump body assembly as claimed in claim 1, characterized in that, The thickness of the slider body is T, and T and B2 satisfy: .

7. The pump body assembly as claimed in claim 1, characterized in that, The thickness of the slider body is T, and T and d3 satisfy: .

8. The pump body assembly as claimed in any one of claims 1 to 7, characterized in that, The slider head has a first arc segment, a second arc segment, and a third arc segment arranged and connected sequentially along the thickness direction of the slider. The radius of curvature of the first arc segment and the radius of curvature of the third arc segment are both smaller than the radius of curvature of the second arc segment. The center of the second arc segment is located between the center of the first arc segment and the slider body. The included angle between the two lines connecting the two ends of the second arc segment to the center of the first arc segment or the third arc segment is γ, where γ satisfies: .

9. The pump body assembly as claimed in claim 8, characterized in that, The direction from the slider body to the slider head is the second direction. The first arc segment and the third arc segment are located on both sides of the second arc segment along the second direction. The radius of curvature of the first arc segment and the radius of curvature of the third arc segment are the same. The sum of the radius of curvature of the first arc surface and the radius of curvature of the second arc surface is d4. The d4 and d3 satisfy: .

10. A compressor, characterized in that, include: Electric motor; as well as The pump body assembly according to any one of claims 1 to 9, the pump body assembly includes a crankshaft, the rollers are sleeved around the crankshaft, and the motor is drivenly connected to the crankshaft.

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

Images