Pump components, compressors and refrigeration equipment

Abstract

The present invention relates to the technical field of compressors, and discloses a pump body assembly, a compressor and a refrigeration device, wherein the pump body assembly includes a cylinder, a piston and a vane, the cylinder is provided with a compression chamber, the side wall of the compression chamber is provided with an intake hole, a vane groove and an exhaust hole, the vane groove is arranged along the radial direction of the compression chamber and is located between the intake hole and the exhaust hole; the piston is located in the compression chamber and can rotate eccentrically; the vane is arranged in the vane groove, the inner end of the vane abuts the piston, and the outer end of the vane is connected to a spring, on the axial cross-section of the compression chamber, the contour line of the inner end is a first curve, the position where the first curve contacts the piston is a first contact point, the first contact point deviates from the thickness midline of the vane and is close to the exhaust hole, so that the area of ​​the inner end of the vane contacting the high-pressure zone is reduced, the thrust exerted on the inner end of the vane is reduced, the pressure difference between the inner and outer ends of the vane is increased, so that the inner end of the vane maintains contact with the outer surface of the piston, and the vane is prevented from separating from the piston.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a pump assembly, a compressor and a refrigeration device. Background Art

[0002] The compressor is a crucial power component in refrigeration equipment and typically consists of a housing, motor, pump assembly, and liquid reservoir. The pump assembly of a rotary compressor includes a cylinder, piston, and vane. The vane maintains contact with the piston due to the pressure differential and spring force. However, under certain operating conditions, the pressure differential between the inner and outer ends of the vane is low due to the small difference between the suction and discharge pressures. This pressure differential and spring force are insufficient to offset the inertia and friction of the vane's reciprocating motion, causing the vane to separate from the piston, resulting in air leakage and reduced exhaust, which in turn degrades compressor performance. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a pump assembly that increases the pressure difference between the two ends of the sliding vane by designing the shape of the sliding vane, so that the sliding vane and the piston are kept in contact.

[0004] The present invention also provides a compressor having the pump body assembly.

[0005] The present invention also provides a refrigeration device using the compressor.

[0006] According to an embodiment of the first aspect of the present invention, a pump body assembly includes a cylinder, a piston and a vane, the cylinder is provided with a compression chamber, the side wall of the compression chamber is provided with an intake hole, a vane groove and an exhaust hole, the vane groove is arranged along the radial direction of the compression chamber and is located between the intake hole and the exhaust hole; the piston is located in the compression chamber and can rotate eccentrically; the vane is arranged in the vane groove, the inner end of the vane abuts the piston, and the outer end of the vane is connected to a spring, and on the axial cross-section of the compression chamber, the contour line of the inner end is a first curve, and the position where the first curve contacts the piston is a first contact point, and the first contact point deviates from the thickness midline of the vane and is close to the exhaust hole.

[0007] The pump assembly according to the first embodiment of the present invention has at least the following beneficial effects:

[0008] When the pump body assembly is running, the inner end of the slide is in contact with the piston, and the piston and the slide divide the compression chamber into a low-pressure area and a high-pressure area. The low-pressure area is connected to the suction hole, and the high-pressure area is connected to the exhaust hole. The contour line of the inner end of the slide is set to a first curve, and the first contact point of the first curve contacting the piston deviates from the center line of the slide, and the first contact point is close to the exhaust hole, so that the area of ​​the inner end of the slide contacting the high-pressure area is reduced, thereby reducing the thrust exerted on the inner end of the slide, increasing the pressure difference between the inner and outer ends of the slide, and making the inner end of the slide keep in contact with the outer surface of the piston, preventing the slide from separating from the piston, avoiding air leakage, and helping to improve the performance of the compressor.

[0009] According to some embodiments of the first aspect of the present invention, the first curve is an arc line, and the center of the arc line deviates from the thickness midline of the sliding sheet.

[0010] According to some embodiments of the first aspect of the present invention, the distance between the first contact point and the midline of the thickness of the sliding sheet is L1, and the thickness of the sliding sheet is T f , meet: 0.05T f ≤L1≤0.2T f .

[0011] According to some embodiments of the first aspect of the present invention, the first contact point is located at the connection between the side surface of the sliding sheet close to the exhaust hole and the inner end.

[0012] According to some embodiments of the first aspect of the present invention, the cylinder is provided with a first back-pressure hole and a second back-pressure hole arranged axially, the first back-pressure hole is connected to the end of the sliding vane groove facing away from the compression chamber, the second back-pressure hole is connected to the first back-pressure hole, and the sliding vane can enter the second back-pressure hole.

[0013] According to some embodiments of the first aspect of the present invention, the vane groove has a first wall and a second wall facing each other, the first wall is located on the side of the vane groove close to the suction hole, the extended surface of the first wall intersects with the side wall of the first back pressure hole, and the extended surface of the second wall intersects with the side wall of the second back pressure hole.

[0014] According to some embodiments of the first aspect of the present invention, the outer end includes a protrusion, the protrusion forms a step with the outer end, and the protrusion can enter the second back pressure hole.

[0015] According to some embodiments of the first aspect of the present invention, the thickness of the sliding sheet is T f , the thickness of the protrusion is T b , satisfying: T b >0.5T f .

[0016] According to some embodiments of the first aspect of the present invention, a first intersection and a second intersection are formed at the connection between the first back pressure hole and the second back pressure hole, the first intersection is close to the air intake hole, the second intersection is close to the air exhaust hole, and the distance between the first intersection and the second wall surface is L2, satisfying: T b <L2<T f .

[0017] According to some embodiments of the first aspect of the present invention, the distance between the second intersection point and the first wall is L3, satisfying: T f <L3.

[0018] A compressor according to an embodiment of the second aspect of the present invention includes the pump body assembly described in the embodiment of the first aspect.

[0019] A refrigeration device according to an embodiment of the second aspect of the present invention includes the compressor described in the embodiment of the second aspect.

[0020] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Additional aspects and advantages of the present invention will become apparent and readily understood from the following description of embodiments with reference to the accompanying drawings, in which:

[0022] Figure 1 A schematic structural diagram of a pump assembly according to an embodiment of the first aspect of the present invention;

[0023] Figure 2 A schematic diagram of the structure of the connection between the slide and the piston in the current pump assembly;

[0024] Figure 3 This is a schematic structural diagram of the connection between the slide and the piston in the pump assembly according to the first aspect of the present invention;

[0025] Figure 4 for Figure 3 Schematic diagram of the pressure area distribution of the pump body assembly;

[0026] Figure 5 for Figure 4 A local enlarged schematic diagram of point A;

[0027] Figure 6 Schematic diagram of the structure of the cylinder in the embodiment of the first aspect of the present invention;

[0028] Figure 7 Schematic diagram of the structure of the sliding plate in the embodiment of the first aspect of the present invention.

[0029] The accompanying figures are as follows:

[0030] Cylinder 100, compression chamber 101, low-pressure area 1011, high-pressure area 1012, suction hole 102, vane groove 103, exhaust hole 104, first back-pressure hole 105, second back-pressure hole 106, first intersection 107, second intersection 108, upper bearing 110, lower bearing 120;

[0031] Piston 200, crankshaft 210;

[0032] Sliding piece 300 , inner end 310 , first curve 311 , outer end 320 , protrusion 321 , spring 330 . DETAILED DESCRIPTION

[0033] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0034] In the description of the present invention, it should be understood that descriptions involving orientations, such as up, down, front, back, left, right, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on the present invention.

[0035] In the description of the present invention, if there is a description of first and second, it is only for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the order of the indicated technical features.

[0036] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, and connecting should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention based on the specific content of the technical solution.

[0037] Refrigeration equipment relies on a refrigeration system to produce cold air to achieve the purpose of cooling. The compressor is the power component of the refrigeration system. It drives the refrigerant to circulate through the compressor to achieve continuous refrigeration. The compressor is generally composed of a shell, a motor fixed inside the shell to provide rotational power, and a pump body assembly for compressing the refrigerant. The pump body assembly of the rotary compressor includes an upper bearing, a lower bearing, a cylinder, a crankshaft, a piston, and a vane. The upper bearing, lower bearing, and cylinder form an independent refrigerant compression working space. In the compression working space, the piston rotates eccentrically, and the vane reciprocates along the vane groove. The inner end of the vane maintains contact with the piston. The piston and the vane divide the compression working space into two areas. The area near the suction port is a low-pressure area, and the area near the exhaust port is a high-pressure area. The motor drives the crankshaft to rotate, and the crankshaft drives the piston to rotate eccentrically to complete the compression of the refrigerant. When the pressure in the high-pressure area reaches the set threshold, the exhaust port opened by the upper bearing opens to output the high-pressure refrigerant.

[0038] During the operation of the rotary compressor, the inner end of the vane is subjected to the support force of the piston and the pressure of the refrigerant gas, while the outer end of the vane is subjected to the back pressure force and the spring force. Under the combined action of all these forces, the vane reciprocates in the vane groove. Since the pump body assembly as a whole is in a high-temperature and high-pressure environment inside the compressor, the back pressure force applied to the outer end of the vane is the pressure of the high-pressure refrigerant. During the reciprocating motion, the vane is also subjected to the friction force of the side wall of the vane groove. Under certain working conditions, such as when the compressor is running at a low frequency, the pressure difference between the suction pressure and the exhaust pressure is small, which will lead to a small pressure difference at both ends of the vane. The gas force formed by the pressure difference and the elastic force generated by the spring are insufficient to offset the inertia force of the reciprocating motion of the vane and the friction between the vane and the vane groove, and the vane cannot maintain the contact between the vane and the piston, resulting in the inner end of the vane and the outer surface of the piston separating at certain moments, and the high-pressure refrigerant in the high-pressure area leaking to the low-pressure area, resulting in a reduction in the exhaust volume of the compressor and a decline in the performance of the compressor. As the piston continues to rotate, when the piston contacts the vane again, collision and mechanical noise will occur, and even damage the inner end of the vane will be caused, affecting its service life.

[0039] To this end, an embodiment of the first aspect of the present invention proposes a pump body assembly, which increases the pressure difference at both ends of the sliding vane by changing the shape of the sliding vane, so that the sliding vane maintains contact with the piston, which is beneficial to improving the performance of the compressor.

[0040] like Figure 1 and Figures 3 to 7As shown, an embodiment of the first aspect of the present invention provides a pump body assembly, which is applied to a rotary compressor. The pump body assembly includes a cylinder 100, an upper bearing 110, a lower bearing 120, a piston 200, a crankshaft 210 and a vane 300. The cylinder 100 is provided with a compression chamber 101. The upper bearing 110 and the lower bearing 120 are distributed on the upper and lower sides of the cylinder 100 and close the compression chamber 101 from the upper and lower sides. The crankshaft 210 is rotated and supported by the upper bearing 110 and the lower bearing 120. The piston 200 is fixedly mounted on the crankshaft 210 and rotates with the crankshaft 210. The piston 200 is eccentrically arranged in the compression chamber 101, and part of the outer peripheral wall of the piston 200 abuts against the inner wall of the compression chamber 101. The cylinder 100 is also provided with an intake hole 102, a vane groove 103 and an exhaust hole 104. The vane groove 103 is located between the intake hole 102 and the exhaust hole The air holes 104 are connected, and the intake hole 102, the vane groove 103 and the exhaust hole 104 are all connected to the compression chamber 101, wherein the vane groove 103 is arranged along the radial direction of the compression chamber 101, the vane 300 is set in the vane groove 103, and the vane 300 can slide in the vane groove 103, the outer end 320 of the vane 300 is connected to the spring 330, and the inner end 310 of the vane 300 abuts the piston 200, and the piston 200 and the vane 300 divide the compression chamber 101 into two areas. The low-pressure area 1011 is connected to the intake hole 102, and the high-pressure area 1012 is connected to the exhaust hole 104. Due to the eccentric rotation of the piston 200, the volume of the low-pressure area 1011 and the high-pressure area 1012 is changed, and the refrigerant is sucked in from the intake hole 102. The piston 200 completes the compression of the refrigerant once it rotates one circle, and the high-pressure refrigerant is discharged from the exhaust hole 104. The spring 330 is located at the outer periphery of the cylinder 100. Since the pump body assembly as a whole is in a high-pressure environment inside the compressor, the outer end 320 of the slide 300 is also subjected to the force of the high-pressure refrigerant. The pressure of the high-pressure refrigerant here is consistent with the pressure of the refrigerant discharged from the exhaust hole 104.

[0041] Reference Figure 2It can be understood that the inner end of the current slide 300 is set to a circular arc surface, and the center of the circular arc surface is located on the midline of the thickness of the slide 300. Therefore, the position where the inner end of the slide 300 contacts the piston 200 is close to the midline of the thickness of the slide 300. Under certain working conditions (such as low-frequency operation of the compressor), due to the low exhaust pressure, the refrigerant forces acting on the inner and outer ends of the vane 300 are relatively close. The elastic force of the spring alone is not enough to offset the inertia force of the reciprocating motion of the vane 300 and the friction between the vane 300 and the vane groove 103, and the vane 300 cannot be kept in contact with the piston 200, resulting in the inner end of the vane 300 and the outer surface of the piston 200 being separated at certain moments, and the high-pressure gas in the high-pressure area 1012 leaking to the low-pressure area 1011, which reduces the exhaust volume of the compressor and reduces the performance of the compressor. As the piston 200 continues to rotate, when the piston 200 contacts the vane 300 again, collision and mechanical noise will be generated, and even the inner end of the vane 300 will be damaged, affecting its use.

[0042] Therefore, if Figure 3 As shown, on the axial cross-section of the compression chamber 101, the contour line of the inner end 310 is defined as a first curve 311, and the position where the first curve 311 contacts the piston 200 is defined as a first contact point. By changing the shape of the first curve 311, the first contact point is deviated from the thickness midline of the sliding plate 300 (as shown in FIG. Figure 7 The first contact point is adjusted to the side close to the exhaust hole 104, so that the area of ​​the inner end 310 contacting the high-pressure refrigerant is reduced, thereby reducing the force of the refrigerant on the inner end 310.

[0043] It can be understood that since the piston 200 rotates eccentrically, the contact point between the piston 200 and the slide 300 will shift, wherein the first contact point refers to the contact point between the piston 200 and the slide 300 when the center of the circle of the piston 200 is located on the midline of the thickness of the slide 300 (that is, the piston 200 is at 0 degrees or 180 degrees).

[0044] Reference Figure 4 and Figure 5Therefore, when the pump body assembly is running, by setting the contour line of the inner end 310 of the slide 300 to the first curve 311, and the first contact point of the first curve 311 with the piston 200 is offset to be close to the exhaust hole 104, the area of ​​the inner end 310 of the slide 300 contacting the refrigerant in the high-pressure area 1012 is reduced, thereby reducing the thrust exerted on the inner end 310 of the slide 300, increasing the pressure difference between the inner end 310 and the outer end 320 of the slide 300, and cooperating with the force of the spring 330, the inner end 310 of the slide 300 maintains contact with the outer surface of the piston 200, preventing the slide 300 from separating from the piston 200 and preventing air leakage, which helps to improve the performance of the compressor, and eliminates the collision and mechanical noise generated by the piston 200 and the slide 300, which is beneficial to protecting the slide 300 and extending the service life of the slide 300.

[0045] It is understandable that if Figure 7 As shown, the sliding vane 300 is usually a metal sheet with uniform thickness. The thickness direction of the sliding vane 300 is between the two side surfaces of the sliding vane 300 contacting the side walls of the sliding vane groove 103. Correspondingly, the thickness midpoint of the sliding vane 300 is the middle of the two side surfaces. The intersection line of the thickness midpoint of the sliding vane 300 and the axial cross-section of the compression chamber 101 is the thickness midpoint line of the sliding vane 300.

[0046] Reference Figure 7 In some embodiments of the first aspect of the present invention, the first curve 311 is configured as an arc, and the center of the arc is offset from the midline of the thickness of the vane 300. Due to the arc's shape, the location of the inner end 310 of the vane 300 closest to the piston 200 is the first contact point, and the line connecting the first contact point and the center of the arc is parallel to the midline of the thickness of the vane 300. Therefore, by adjusting the distance that the center of the arc deviates from the midline of the thickness of the vane 300, the area of ​​the inner end 310 contacting the high-pressure refrigerant can be adjusted, thereby reducing the force exerted by the high-pressure refrigerant on the inner end 310. Furthermore, configuring the first curve 311 as an arc facilitates machining of the inner end 310, reducing machining costs.

[0047] In addition, it can be understood that, on the axial cross-section of the compression chamber 101, the contour line of the inner end 310 can also be set to other forms of curves, such as a parabola, an involute, etc., as long as the area of ​​the inner end 310 contacting the high-pressure refrigerant can be reduced.

[0048] It is understandable that if Figure 7 As shown, the distance between the first contact point and the thickness midline of the slide 300 is defined as L1, and the thickness of the slide 300 is defined as T f , designed to meet: 0.05T f ≤L1≤0.2T f , control the arc center offset range to 0.05Tf Up to 0.2T f The thrust on the inner end 310 of the sliding piece 300 can be effectively reduced.

[0049] It is understandable that, in other embodiments, the first contact point is set on the side of the slide 300 close to the exhaust hole 104, that is, the position of the inner end 310 of the slide 300 closest to the piston 200 is close to the edge of the exhaust hole 104, so that the area of ​​the inner end 310 contacting the high-pressure refrigerant is zero, so that the refrigerant force acting on the inner end 310 is greatly reduced, which is conducive to increasing the pressure difference between the inner end 310 and the outer end 320 of the slide 300, so that the inner end 310 of the slide 300 maintains contact with the outer surface of the piston 200.

[0050] Reference Figure 6 In some embodiments of the first aspect of the present invention, the cylinder 100 is further provided with a first back-pressure hole 105 and a second back-pressure hole 106, both of which are distributed along the axial direction of the compression chamber 101, and can be through the cylinder 100 or countersunk holes, wherein the first back-pressure hole 105 is connected to the end of the slide groove 103 away from the compression chamber 101, and the second back-pressure hole 106 is connected to the first back-pressure hole 105, and the slide 300 can enter the second back-pressure hole 106. By providing the first back-pressure hole 105 and the second back-pressure hole 106, the activity space of the outer end 320 of the slide 300 is increased, and more high-pressure refrigerant can be accommodated, and the refrigerant pressure contacted by the outer end 320 is stabilized, which helps to stabilize the force acting on the outer end 320, so that the reciprocating motion of the slide 300 in the slide groove 103 is more stable and reliable, which helps to improve the operating stability of the compressor.

[0051] Reference Figure 6 It can be understood that the vane groove 103 includes a first wall surface and a second wall surface relative to each other, wherein the first wall surface is located on the side of the vane groove 103 close to the air intake hole 102, and the second wall surface is located on the side close to the air exhaust hole 104, and the extended surface of the first wall surface intersects with the side wall of the first back-pressure hole 105, and the extended surface of the second wall surface intersects with the side wall of the second back-pressure hole 106, that is, the first back-pressure hole 105 and the second back-pressure hole 106 are offset in the direction away from the air intake hole 102, so that the high-pressure refrigerant in the first back-pressure hole 105 and the second back-pressure hole 106 is offset to a position away from the air intake hole 102, and the refrigerant force on the outer end 320 of the vane 300 will also be offset, which is conducive to more stable reciprocating motion of the vane 300 in the vane groove 103.

[0052] Reference Figure 3 and Figure 7In some embodiments of the first aspect of the present invention, the outer end 320 of the slide 300 is provided with a protrusion 321. The protrusion 321 forms a step with the outer end 320, and the protrusion 320 can enter the second backpressure hole 106. Because the first backpressure hole 105 and the second backpressure hole 106 are offset away from the air intake hole 102, the protrusion 320 is located on the side away from the air intake hole 102. During assembly, because the first backpressure hole 105 and the second backpressure hole 106 are offset away from the air intake hole 102, the slide 300 can only be installed into the slide slot 103 and the first and second backpressure holes 105, 106 only if the protrusion 321 is located on the side away from the air intake hole 102, thus preventing misalignment. By utilizing the cooperation between the protrusion 320 and the first back pressure hole 105 and the second back pressure hole 106, the first contact point is offset to be close to the exhaust hole 104, so that the area of ​​the inner end 310 of the slide 300 contacting the refrigerant in the high pressure area 1012 is reduced, thereby reducing the thrust exerted on the inner end 310 of the slide 300.

[0053] It is understood that the first backpressure hole 105 and the second backpressure hole 106 can also be offset in a direction away from the exhaust hole 104. Accordingly, the protrusion 320 is located on the side away from the exhaust hole 104. During assembly, the slide 300 can only be installed into the slide slot 103 and the first and second backpressure holes 105, 106 when the protrusion 321 is located on the side away from the exhaust hole 104, thus preventing misalignment. The cooperation between the protrusion 320 and the first and second backpressure holes 105, 106 shifts the first contact point closer to the exhaust hole 104, reducing the area of ​​the inner end 310 of the slide 300 contacting the refrigerant in the high-pressure area 1012, thereby reducing the thrust applied to the inner end 310 of the slide 300.

[0054] It is understood that the thickness of the slide 300 is T f , the thickness of the protrusion 321 is T b , designed to meet: T b >0.5T f By limiting the thickness of the protrusion 321, the protrusion 321 can enter the second back pressure hole 106, and the end face of the protrusion 321 is set to a smooth curved surface. When the slide 300 reciprocates in the slide groove 103, the protrusion 321 can enter the second back pressure hole 106 more smoothly.

[0055] Reference Figure 6 and Figure 7 The connection between the first back pressure hole 105 and the second back pressure hole 106 forms a first intersection 107 and a second intersection 108, wherein the first intersection 107 is close to the air intake hole 102, and the second intersection 108 is close to the air exhaust hole 104. The distance between the first intersection 107 and the second wall is positioned as L2, which satisfies the following design: Tb <L2<T f , due to T b <L2, so that when the slide 300 reciprocates in the slide slot 103, the protrusion 321 will not collide with the first intersection 107, and the protrusion 321 can smoothly enter the second back pressure hole 106; In addition, the distance between the second intersection 108 and the first wall is defined as L3, which satisfies the following design: T f < L3, so that when the sliding vane 300 reciprocates in the sliding vane slot 103, the protrusion 321 will not collide with the second intersection 108, and the protrusion 321 can smoothly enter the second back pressure hole 106.

[0056] An embodiment of the second aspect of the present invention proposes a compressor, which includes a shell, a rotor, a stator, a liquid reservoir and a pump body assembly of the first aspect embodiment. The stator and the pump body assembly are fixed in the inner cavity of the shell, the rotor is arranged inside the stator, and the rotor is fixedly connected to the crankshaft 210 of the pump body assembly. The rotor drives the crankshaft 210 to rotate, and the liquid reservoir is connected to the suction hole 102 of the pump body assembly to input refrigerant. The cylinder 100 of the pump body assembly is provided with a compression chamber 101. The upper bearing 110 and the lower bearing 120 are distributed on the upper and lower sides of the cylinder 100 and close the compression chamber 101 from the upper and lower sides. The crankshaft 210 is rotated and supported by the upper bearing 110 and the lower bearing 120. The piston 200 is fixedly mounted on the crankshaft 210 and rotates with the crankshaft 210. The piston 200 is eccentrically arranged in the compression chamber 101. Part of the outer peripheral wall of the piston 200 abuts against the inner wall of the compression chamber 101. The cylinder 100 is also provided with an intake hole 102, a slide groove 103 and an exhaust hole 104. The slide groove 103 is located between the intake hole 102 and the exhaust hole 104, and the intake hole 102, the slide groove 103 and the exhaust hole 104 are all connected to the compression chamber 1 01, wherein the vane groove 103 is arranged along the radial direction of the compression chamber 101, the vane 300 is set in the vane groove 103, and the vane 300 can slide in the vane groove 103, the inner end 310 of the vane 300 abuts the piston 200, and the outer end 320 of the vane 300 is connected to the spring 330, the piston 200 and the vane 300 divide the compression chamber 101 into two areas, the low-pressure area 1011 connected to the intake hole 102, and the high-pressure area 1012 connected to the exhaust hole 104. Due to the eccentric rotation of the piston 200, the volume of the low-pressure area 1011 and the high-pressure area 1012 is changed, and the refrigerant is sucked in from the intake hole 102. The piston 200 rotates one circle to complete the compression of the refrigerant, and the high-pressure refrigerant is discharged from the exhaust hole 104.

[0057] Therefore, if Figure 3As shown, on the axial cross-section of the compression chamber 101, the contour line of the inner end 310 is defined as a first curve 311, and the position where the first curve 311 contacts the piston 200 is defined as a first contact point. By changing the shape of the first curve 311, the first contact point is deviated from the thickness midline of the slide 300, and the first contact point is adjusted to the side close to the exhaust hole 104, so that the area of ​​the inner end 310 contacting the high-pressure refrigerant is reduced, and the force of the refrigerant on the inner end 310 is reduced, thereby increasing the pressure difference between the inner end 310 and the outer end 320 of the slide 300. Combined with the force of the spring 330, the inner end 310 of the slide 300 maintains contact with the outer surface of the piston 200, preventing the slide 300 from separating from the piston 200 and preventing air leakage, which helps to improve the performance of the compressor, eliminates collision and mechanical noise between the piston 200 and the slide 300, and is beneficial to protecting the slide 300 and increasing the service life of the slide 300.

[0058] The embodiment of the third aspect of the present invention proposes a refrigeration device, the refrigeration system of the refrigeration device includes the compressor of the embodiment of the second aspect, the compressor includes the pump body assembly of the embodiment of the first aspect, and has all the technical effects of the pump body assembly, which will not be repeated.

[0059] The embodiments of the present invention are described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Various changes can be made within the scope of knowledge possessed by ordinary technicians in the relevant technical field without departing from the spirit of the present invention.

Claims

1. Pump body assembly, characterized in that, include: A cylinder is provided with a compression chamber, wherein a side wall of the compression chamber is provided with an air intake hole, a sliding vane groove and an air exhaust hole, wherein the sliding vane groove is arranged along the radial direction of the compression chamber and is located between the air intake hole and the air exhaust hole; a piston located in the compression chamber and capable of eccentric rotation; a sliding vane disposed in the sliding vane groove, wherein an inner end of the sliding vane abuts against the piston, and an outer end of the sliding vane is connected to a spring; in an axial cross-section of the compression chamber, a contour line of the inner end is a first curve; a position where the first curve contacts the piston is a first contact point; the first contact point is offset from a thickness midline of the sliding vane and is close to the exhaust hole; The cylinder is provided with a first back-pressure hole and a second back-pressure hole arranged axially, the first back-pressure hole being connected to an end of the sliding vane groove facing away from the compression chamber, the second back-pressure hole being connected to the first back-pressure hole, and the sliding vane can enter the second back-pressure hole; The sliding vane groove has a first wall surface and a second wall surface opposite to each other, the first wall surface is located on a side of the sliding vane groove close to the air suction hole, an extension surface of the first wall surface intersects with a side wall of the first back pressure hole, and an extension surface of the second wall surface intersects with a side wall of the second back pressure hole; The outer end includes a protrusion, the protrusion forms a step with the outer end, and the protrusion can enter the second back pressure hole.

2. The pump assembly according to claim 1, characterized in that The first curve is an arc line, and the center of the arc line deviates from the thickness midline of the sliding plate.

3. The pump assembly according to claim 2, characterized in that: The distance between the first contact point and the thickness midline of the slide is , the thickness of the slide is , meet: 0.05 ≤ ≤0.2 .

4. The pump assembly according to claim 2, characterized in that The first contact point is located at the connection between the side surface of the sliding plate close to the exhaust hole and the inner end.

5. The pump assembly according to claim 1, characterized in that The thickness of the slide is , the thickness of the protrusion is ,satisfy: >0.5 .

6. The pump assembly according to claim 5, characterized in that The connection between the first back pressure hole and the second back pressure hole forms a first intersection and a second intersection, the first intersection is close to the air intake hole, the second intersection is close to the air exhaust hole, and the distance between the first intersection and the second wall surface is ,satisfy: < < .

7. The pump assembly according to claim 6, characterized in that The distance between the second intersection point and the first wall is ,satisfy: < .

8. A compressor, characterized in that The invention comprises a pump body assembly according to any one of claims 1 to 7.

9. Refrigeration equipment, characterized in that Comprising the compressor of claim 8.

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