Pump body assembly of rotary compressor, rotary compressor and air conditioner

Abstract

The present invention provides a pump body assembly of a rotary compressor, a rotary compressor and an air conditioner. The pump body assembly of the rotary compressor comprises: a cylinder structure; a piston, the piston is arranged in the cylinder structure, an installation space is arranged on the piston, and the first end face of the piston has an opening of the installation space; a balancing block, the balancing block is arranged in the installation space; and a crankshaft, the crankshaft is connected to the first end face of the piston. The technical solution of the present invention effectively solves the problem that the crankshaft is prone to deflection and deformation due to the eccentric setting of the center of mass of the pump body assembly in the prior art.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a pump body assembly of a rotary compressor, a rotary compressor and an air conditioner. Background Art

[0002] In recent years, within the rotary compressor industry, compressor models have been increasingly developing in the direction of miniaturization and high frequency. New product research and development has been carried out to cover from small displacement to large displacement, and from low energy efficiency to high energy efficiency. By reducing the material cost of compressors, the core competitiveness of air-conditioning products in the domestic and foreign markets has been improved.

[0003] The pump body structure of the rolling rotor compressor is mainly composed of a cylinder, a rolling piston, a crankshaft, a vane, a spring, and flanges mounted on both ends of the cylinder. For the development of traditional single-cylinder rolling rotor compressors in the high-speed field, there is a serious problem of crankshaft deflection and deformation: due to the eccentric part on the crankshaft, when the crankshaft rotates at a high speed of about 120rps, the eccentric part and the rolling piston sleeved on the outer circle of the eccentric part have a large centrifugal force, which makes the eccentric part of the crankshaft and the part of the crankshaft long axis at the cantilever end of the crankshaft protruding from the flange on the cylinder produce a large deflection deformation, causing the compressor friction power consumption to increase, the air gap between the motor stator and rotor to decrease, and the compressor vibration effect to increase, resulting in increased compressor power consumption, reduced motor efficiency, and worse vibration and noise levels of the compressor. Summary of the invention

[0004] The main purpose of the present invention is to provide a pump body assembly of a rotary compressor, a rotary compressor and an air conditioner, so as to solve the problem that the crankshaft is prone to deflection and deformation due to the eccentric setting of the center of mass of the pump body assembly in the prior art.

[0005] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a pump body assembly of a rotary compressor is provided, including: a cylinder structure; a piston, the piston is arranged in the cylinder structure, an installation space is arranged on the piston, and the first end face of the piston has an opening for the installation space; a balancing block, the balancing block is arranged in the installation space; and a crankshaft, the crankshaft is connected to the first end face of the piston.

[0006] Furthermore, the balancing weight is lower than the first end surface of the piston, so that a kinetic energy dissipation cavity is formed between the first end surface of the balancing weight and the first end surface of the piston.

[0007] Furthermore, the first end surface of the balancing weight is a non-planar surface.

[0008] Furthermore, the first end surface of the balancing weight has a groove.

[0009] Furthermore, the width of the groove of the balancing weight in the radial direction of the piston is b0, wherein the value range of b0 is between 0.3 mm and 0.5 mm.

[0010] Further, the kinetic energy dissipation cavity cut in a cross section perpendicular to the end surface of the piston is in a T-shape, a triangular rectangle or a rectangle.

[0011] Further, when the kinetic energy dissipation cavity cut by a cross section perpendicular to the end face of the piston is T-shaped or triangularly rectangular, the width of the end face of the first end face of the balance block in the radial direction close to the central axis of the piston is b3, the width of the end face away from the central axis of the piston is b1, and the width between the end face close to the central axis of the piston and the end face away from the central axis of the piston is b2, and the following relationship is satisfied: b1+b2+b3=b, b1=b2=b3.

[0012] Furthermore, when the kinetic energy dissipation cavity cut by a cross section perpendicular to the end face of the piston is T-shaped, the maximum depth of the kinetic energy dissipation cavity is H, and the minimum depth of the kinetic energy dissipation cavity is h, wherein the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 2.5 times of h.

[0013] Furthermore, when the kinetic energy dissipation cavity cut by a cross section perpendicular to the end face of the piston is a triangular rectangle, the side length of the triangular cross-sectional portion of the kinetic energy dissipation cavity close to the central axis of the piston is L1, and the side length of the triangular cross-sectional portion of the kinetic energy dissipation cavity away from the central axis of the piston is L2, and the angle between L1 and L2 is D, where the value range of D is 20°~47°.

[0014] Furthermore, the maximum depth of the kinetic energy dissipation cavity is H, and the minimum depth thereof is h1, wherein H and h1 satisfy that the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 3 times that of h1.

[0015] Further, in the radial direction along the second end surface of the piston, the width of the kinetic energy dissipation cavity close to the central axis of the piston is B1, and the width of the end surface away from the central axis of the piston is B2, satisfying the following relationship: B1=B2.

[0016] Furthermore, the cylinder structure includes a cylinder, an upper flange and a lower flange, the first end face of the piston is adjacent to and parallel to the end face of the upper flange, the distance between the first end face of the piston and the upper flange is δ, the deepest depth of the kinetic energy dissipation cavity is H, and H / δ is between 1.5 and 2.25.

[0017] Further, the installation space is a mounting through hole penetrating the first end surface of the piston and the second end surface of the piston; or the installation space is a mounting groove arranged at the first end of the piston.

[0018] Further, when the installation space is an installation through-hole, the second end surface of the balance weight and the second end surface of the piston are located on the same plane.

[0019] Further, there are a plurality of installation through-holes, and the plurality of installation through-holes are arranged at intervals along the circumferential direction of the piston to form an annular installation through-hole.

[0020] Further, the number of installation through-holes in one annular installation through-hole is Z, where Z is a positive integer between 18 and 36.

[0021] Further, the circumferential angle corresponding to the arc length of the installation through-hole is d1, and the circumferential angle of the distance between two adjacent installation through-holes on the same circumference is d2. d1 and d2 satisfy: 3° < d2 < 5°, and d1 / d2 is between 3 and 5.

[0022] Further, there are a plurality of annular installation through-holes, and the plurality of annular installation through-holes are arranged at intervals along the radial direction of the piston.

[0023] Further, the annular installation through-holes with different radial positions are arranged at a certain angle offset in the circumferential direction of the second end surface of the piston.

[0024] Further, the offset angle between the annular installation through-holes on two adjacent circumferences is d3, and d1 / d3 is equal to 3.

[0025] Further, the minimum distance between adjacent annular installation through-holes along the radial direction of the piston is ∆r, and the value range of ∆r is between 0.4 mm and 1.0 mm.

[0026] Further, the distance between the outer edge of the installation through-hole on the outermost circumference of the first end surface of the piston and the outer edge of the first end surface of the piston is E1, and the distance between the inner edge of the installation through-hole on the innermost circumference of the first end surface of the piston and the inner edge of the first end surface of the piston is E2. E1 = E2 = E, and E / ∆r is between 2 and 3.

[0027] Further, the number of the plurality of annular installation through-holes is Y, where Y is a positive integer between 3 and 5.

[0028] Further, the number of installation through-holes in each annular installation through-hole is the same, or the number of installation through-holes included in each annular installation through-hole is different.

[0029] Further, the width of the installation through-hole in the radial direction of the second end surface of the piston is b, where the value range of b is between 0.9 mm and 1.5 mm.

[0030] Further, both the piston and the balance weight are made of ceramic materials.

[0031] According to another aspect of the present invention, a rotary compressor is provided, comprising a compressor body and a pump body assembly mounted on the compressor body, wherein the pump body assembly is the above-mentioned pump body assembly.

[0032] According to another aspect of the present invention, an air conditioner is provided, comprising a compressor, wherein the compressor is the above-mentioned rotary compressor.

[0033] By applying the technical solution of the present invention, the piston itself is provided with an installation space, and the balancing block is arranged in the installation space. By arranging the balancing block, the center of mass of the pump body assembly can be located on the crankshaft, which greatly reduces the large deflection deformation of the crankshaft caused by the eccentricity of the pump body assembly. The technical solution of the present invention effectively solves the problem in the prior art that the crankshaft is prone to deflection deformation due to the eccentricity of the center of mass of the pump body assembly. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0035] Figure 1 A schematic cross-sectional view of an embodiment of a pump assembly according to the present invention is shown;

[0036] Figure 2 Shows Figure 1 An enlarged schematic diagram of the pump assembly at point E;

[0037] Figure 3 Shows Figure 1 Schematic diagram of the compression process of the pump assembly;

[0038] Figure 4 Shows Figure 1 A schematic diagram of the end surface structure of the piston of the pump body assembly;

[0039] Figure 5 Shows Figure 4 A schematic cross-sectional view of the piston at AA;

[0040] Figure 6 Shows Figure 1 A schematic diagram of the matching structure of the piston and the balance block of the pump assembly;

[0041] Figure 7 Shows Figure 1 Gas leakage test data of the pump body assembly.

[0042] The above drawings include the following reference numerals:

[0043] 10. Cylinder structure; 11. Cylinder; 12. Upper flange; 13. Lower flange; 20. Piston; 30. Balance block; 40. Crankshaft; 100. Kinetic energy dissipation cavity. DETAILED DESCRIPTION

[0044] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0045] like Figures 1 to 6 As shown, the pump body assembly of the rotary compressor of this embodiment includes: a cylinder structure 10, a piston 20, a balancing block 30 and a crankshaft 40. The piston 20 is arranged in the cylinder structure 10, and an installation space is arranged on the piston 20. The first end surface of the piston 20 has an opening of the installation space. The balancing block 30 is arranged in the installation space. The crankshaft 40 is connected to the first end surface of the piston 20.

[0046] like Figure 2 and Figure 6 As shown, in the technical solution of this embodiment, the balancing block 30 is lower than the first end face of the piston 20, so that a kinetic energy dissipation cavity 100 is formed between the first end face of the balancing block 30 and the first end face of the piston 20. The setting of the kinetic energy dissipation cavity 100 converts the kinetic energy of the gas in the pump body assembly into pressure energy, which greatly reduces the leakage of the gas in the compression chamber in the pump body assembly. When the gas is sucked into the suction chamber in the pump body assembly, a vortex is formed. The kinetic energy dissipation cavity 100 can convert the kinetic energy of the gas vortex into pressure energy, thereby better isolating the compression chamber and the exhaust chamber.

[0047] Specifically, in order to better convert the kinetic energy of the gas into pressure energy, the first end face of the balance weight 30 is a non-plane. The non-plane may be a curved surface, a groove or other structures. Taking the groove as an example, the width of the groove of the balance weight 30 in the radial direction of the piston 20 is b0, wherein the value range of b0 is between 0.3 mm and 0.5 mm. It should be noted that b0 is the width of the groove at its widest point, and the effect is better when the value range of b0 is between 0.3 mm and 0.5 mm. The two side walls of the groove may be vertical surfaces or inclined surfaces.

[0048] like Figure 2 and Figure 6 As shown, in the technical solution of this embodiment, the kinetic energy dissipation cavity 100 cut in a cross section perpendicular to the end surface of the piston 20 is T-shaped, triangular rectangular or rectangular. Figure 2 The kinetic energy dissipation cavity 100 is T-shaped, Figure 6 The kinetic energy dissipation cavity 100 is a triangular rectangular shaped cavity. The triangular rectangular shaped cavity is interpreted as a combination of a triangle at the bottom and a rectangle at the top. The sides of the triangle at the top are the sides of the rectangle at the bottom. The gas leakage test data of the above three kinetic energy dissipation cavities 100 are shown in Figure 7 ,Depend on Figure 7 It can be seen that the T-shaped cross-section kinetic energy dissipation cavity 100 has the best sealing effect. Figure 2 As shown, in the technical solution of this embodiment, when the kinetic energy dissipation cavity 100 cut by a cross section perpendicular to the end face of the piston 20 is T-shaped or triangular, the width of the end face close to the central axis of the piston 20 in the radial direction of the first end face of the balancing weight 30 is b3, the width of the end face away from the central axis of the piston 20 is b1, and the width between the end face close to the central axis of the piston 20 and the end face away from the central axis of the piston 20 is b2, and the following relationship is satisfied: b1+b2+b3=b, b1=b2=b3. The above structure has a low processing cost, and the balancing weight 30 is relatively strong and has a long service life.

[0049] like Figure 2 As shown, in the technical solution of this embodiment, when the kinetic energy dissipation cavity 100 cut by the cross section perpendicular to the end face of the piston 20 is T-shaped, the maximum depth of the kinetic energy dissipation cavity 100 is H, and the minimum depth of the kinetic energy dissipation cavity 100 is h, wherein the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 2.5 times of h. The above structure of the kinetic energy dissipation cavity 100 can also ensure the strength of the piston 20. When the structural form of the kinetic energy dissipation cavity 100 of this embodiment is T-shaped, the above values ​​of H and h have a better sealing effect on the gas.

[0050] like Figure 6 As shown, as another structural form of the kinetic energy dissipation cavity 100 of this embodiment, when the kinetic energy dissipation cavity 100 cut in a cross section perpendicular to the end face of the piston 20 is a triangular rectangle, the side length of the triangular cross-section portion of the kinetic energy dissipation cavity 100 close to the central axis of the piston 20 is L1, and the side length away from the central axis of the piston 20 is L2, and the angle between L1 and L2 is D, wherein the value range of D is 20°~47°. The above structure has a low processing cost, and the structure of the balancing block 30 is relatively strong.

[0051] Specifically, when the kinetic energy dissipation cavity 100 is a triangular rectangular cross-section, the maximum depth of the kinetic energy dissipation cavity 100 is H, and the minimum depth is h1, wherein H and h1 satisfy that the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 3 times that of h1. The above values ​​ensure the sealing effect while making the balancing block 30 relatively strong. In the radial direction along the second end face of the piston 20, the width of the end face of the kinetic energy dissipation cavity 100 close to the center axis of the piston 20 is B1, and the width of the end face away from the center axis of the piston 20 is B2, satisfying the following relationship: B1=B2. The above equal widths make the strength of the balancing block 30 the same, thereby extending the service life of the balancing block 30.

[0052] like Figure 2As shown in the figure, in the technical solution of this embodiment, the cylinder structure 10 includes a cylinder 11, an upper flange 12, and a lower flange 13. The first end face of the piston 20 is adjacent to and parallel to the end face of the upper flange 12. The distance between the first end face of the piston 20 and the upper flange 12 is δ, and the deepest depth of the kinetic energy dissipation cavity 100 is H. H / δ is between 1.5 and 2.25. The above-mentioned kinetic energy dissipation cavity 100 has a good sealing effect.

[0053] As Figures 1 to 6 shown in the figure, in the technical solution of this embodiment, the installation space is an installation through-hole penetrating the first end face and the second end face of the piston 20; or the installation space is an installation groove provided at the first end of the piston 20. The above structure makes the structure of the pump body assembly compact, and there is no need to additionally attach a balance weight structure to the pump body assembly.

[0054] As Figures 1 to 6 shown in the figure, in the technical solution of this embodiment, when the installation space is an installation through-hole, the second end face of the balance weight 30 and the second end face of the piston 20 are on the same plane. According to the characteristics of the pump body assembly, the lower flange and the piston can be sealed by an oil film. Therefore, the second end face of the balance weight 30 and the second end face of the piston 20 are on the same plane.

[0055] As Figure 3 shown in the figure, in the technical solution of this embodiment, there are multiple installation through-holes, and the multiple installation through-holes are arranged at intervals along the circumferential direction of the piston 20 to form an annular installation through-hole. The installation through-holes with the above structure have strong regularity and are convenient for arranging the balance weight 30.

[0056] As Figure 3 shown in the figure, in the technical solution of this embodiment, the number of installation through-holes in one annular installation through-hole is Z, where Z is a positive integer between 18 and 36. The above-mentioned installation through-holes are relatively easy to process and have strong regularity.

[0057] As Figure 4 shown in the figure, in the technical solution of this embodiment, the circumferential angle corresponding to the arc length of the installation through-hole is d1, and the circumferential angle of the distance between two adjacent installation through-holes on the same circumference is d2. d1 and d2 satisfy: 3° < d2 < 5°, and d1 / d2 is between 3 and 5. The above-mentioned installation through-holes not only ensure the strength of the piston 20 but also can cooperate well with the balance weight 30 to prevent gas from leaking from the high-pressure area to the low-pressure area.

[0058] As Figure 4As shown, in the technical solution of this embodiment, the annular mounting through hole includes a plurality of annular mounting through holes, and the plurality of annular mounting through holes are arranged at intervals along the radial direction of the piston 20. The kinetic energy dissipation cavity formed by assembling the balance block 30 and the mounting through hole together acts together with the throttling gap to seal the gas. The arrangement of the mounting through holes is designed for the final sealing structure (kinetic energy dissipation cavity + throttling gap). The kinetic energy dissipation cavities 100 of the above structure are arranged alternately so that the gas flowing through the leakage channel can dissipate kinetic energy in as many kinetic energy dissipation cavities as possible, and reduce the adjacent pressure difference as much as possible, so as to obtain the effect of minimum leakage, and the higher the speed of the pump body, the more significant the sealing effect. Multiple groups of the sealing structures (kinetic energy dissipation cavity + throttling gap) form multi-layer isolation for gas leakage, which is beneficial to gas sealing.

[0059] like Figure 4 As shown, in the technical solution of this embodiment, the annular mounting through holes in different radial directions are arranged at a certain angle along the circumferential direction of the second end surface of the piston 20. The above structure avoids the gaps between the mounting through holes of different circular rings being opposite to each other. When the gaps between the mounting through holes of different circular rings are opposite to each other, the strength of the structure is greater.

[0060] like Figure 4 As shown, in the technical solution of this embodiment, the staggered angle of the annular mounting holes on two adjacent circles is d3, and d1 / d3 is equal to 3. The overlapping amount between the mounting holes of different circular rings of the above structure is large, which is conducive to avoiding gas leakage.

[0061] like Figure 6 As shown, in the technical solution of this embodiment, the minimum distance between adjacent annular mounting through holes along the radial direction of the piston 20 is ∆r, and the value range of ∆r is between 0.4mm and 1.0mm. The above structure ensures that the structure of the piston 20 is relatively strong and has a long service life.

[0062] like Figure 6 As shown, in the technical solution of this embodiment, the distance between the outer edge of the mounting through hole on the outermost circumference of the first end face of the piston 20 and the outer edge of the first end face of the piston 20 is E1, and the distance between the inner edge of the mounting through hole on the innermost circumference of the first end face of the piston 20 and the inner edge of the first end face of the piston 20 is E2, satisfying E1=E2=E, and E / ∆r is between 2 and 3. The outermost and innermost parts of the piston 20 are subjected to greater forces, and the above structure ensures that the piston 20 is relatively strong.

[0063] like Figure 4 and Figure 5As shown, in the technical solution of this embodiment, the number of the plurality of annular mounting through holes is Y, wherein the value of Y is a positive integer between 3 and 5. The above structure ensures that the piston 20 is relatively strong on the one hand, and ensures a good sealing effect of the pump body assembly on the other hand.

[0064] like Figure 4 As shown, in the technical solution of this embodiment, the number of mounting through holes of each annular mounting through hole is the same, or the number of mounting through holes included in each annular mounting through hole is different. The annular mounting through hole can be arranged as required.

[0065] like Figure 2 As shown, in the technical solution of this embodiment, the width of the mounting through hole in the radial direction along the second end surface of the piston 20 is b, wherein the value range of b is between 0.9 mm and 1.5 mm. The above structure ensures that the piston 20 is relatively strong and the balancing block 30 is easier to cooperate with the piston 20.

[0066] like Figures 1 to 6 As shown, in the technical solution of this embodiment, the piston 20 and the balancing weight 30 are both made of ceramic material. The above material makes the pump body assembly lighter and reduces the centrifugal force of the crankshaft 40 when rotating at high speed. Specifically, the piston 20 and the balancing weight 30 are both processed by high-temperature sintering and sandblasting, so that the piston 20 and the balancing weight 30 are more firmly matched.

[0067] The pump body assembly of the present application has multiple annular kinetic energy dissipation cavities on the end surface where the piston 20 and the upper flange 12 cooperate, which greatly enhances the sealing between the piston 20 and the upper flange 12, and solves the sealing problem of the largest leakage part of the rolling rotor compressor pump body, thereby improving the sealing and volumetric efficiency of the rolling rotor compressor pump body. The piston 20 of the present application has multiple annular kinetic energy dissipation cavities 100 on the end surface where the piston 20 and the upper flange 12 cooperate, which reduces the contact area between the end surface of the piston 20 and the end surface of the upper flange 12, reduces the friction and wear of the friction pair, and reduces the power consumption of the compressor. The multiple kinetic energy dissipation cavities 100 on the end surface where the piston 20 and the upper flange 12 cooperate increase the oil storage capacity of the refrigeration oil in the matching gap between the piston and the upper flange, which is conducive to the formation of an oil film on the matching surfaces, enhances the lubrication between the matching surfaces, and reduces the friction power consumption of the compressor. The density of the piston material in this application is about one-half of the density of conventional piston materials, and a plurality of annular kinetic energy dissipation cavities 100 are provided on the piston end surface, so that the mass of the piston 20 is reduced by at least 50%, so that the centrifugal force generated by the eccentric part when the crankshaft 40 rotates at ultra-high speed can be effectively reduced, and the vibration and noise problems of the compressor can be improved. At the same time, the mass of the balancing blocks installed at both ends of the rotor is reduced, and the production cost of the compressor is reduced. In addition, the surface friction coefficient of the piston material of this application is small and the surface finish is good, which can effectively reduce the wear of the roller friction pair and reduce the power consumption of the compressor. The piston material has a large hardness and good wear resistance, which can greatly improve the reliability of the compressor running under ultra-high speed conditions for a long time.

[0068] From the above, we can know that the development of traditional single-cylinder rolling rotor compressors in the high-speed field mainly has two bottleneck problems. First, the crankshaft has serious deflection deformation: because there is an eccentric part on the crankshaft, when the crankshaft rotates at a higher speed (about 120rps), the eccentric part and the rolling piston sleeved on the outer circle of the eccentric part have a large centrifugal force, which causes the eccentric part of the crankshaft and the cantilever end of the crankshaft (the part of the crankshaft long axis extending out of the flange on the cylinder) to have a large deflection deformation, causing the compressor friction power consumption to increase, the air gap between the motor stator and rotor to decrease, and the compressor vibration effect to increase, resulting in increased power consumption of the compressor, reduced motor efficiency, and worse vibration and noise levels of the compressor. Second, large gas leakage: because there is a certain assembly gap between the pump body parts of the rolling rotor compressor, when there is a large pressure difference on both sides of the assembly gap, it will cause a large amount of gas refrigerant to leak from the high-pressure area through the pump body assembly gap to the low-pressure area, resulting in reduced volumetric efficiency and energy efficiency of the compressor. However, in order to achieve the development of miniaturization and high speed of the rotary compressor, that is, the motor speed of the single-cylinder rolling rotor compressor is increased from 120rps to an ultra-high speed of 200rps or even 240rps, which will further aggravate and worsen the above two problems, causing serious wear of the compressor pump parts, a sharp increase in the total amount of gas leakage per unit time, collision and boring between the motor rotor and the stator, and excessive vibration and noise levels of the compressor. In severe cases, the compressor pump body will be stuck and shut down. The technical solution of the present application effectively solves the above two problems that occur when the motor speed is higher than 120rps.

[0069] The present application also provides a rotary compressor, comprising a compressor body and a pump body assembly mounted on the compressor body. The pump body assembly is the above-mentioned pump body assembly.

[0070] The present application also provides an air conditioner, comprising a compressor, wherein the compressor is the above-mentioned rotary compressor.

[0071] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A pump body assembly of a rotary compressor, characterized in that: include: Cylinder structure (10); A piston (20), the piston (20) being arranged in the cylinder structure (10), an installation space being arranged on the piston (20), and a first end surface of the piston (20) having an opening of the installation space; A balancing weight (30), the balancing weight (30) being arranged in the installation space; A crankshaft (40), wherein the piston (20) is sleeved on the crankshaft (40); The balancing block (30) is lower than the first end surface of the piston (20), so that a kinetic energy dissipation cavity (100) is formed between the first end surface of the balancing block (30) and the first end surface of the piston (20).

2. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The first end surface of the balancing block (30) is a non-planar surface.

3. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The first end surface of the balancing weight (30) has a groove.

4. The pump body assembly of the rotary compressor according to claim 3, characterized in that: The width of the groove of the balancing block (30) in the radial direction of the piston (20) is b0, wherein the value range of b0 is between 0.3 mm and 0.5 mm.

5. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The kinetic energy dissipation cavity (100) cut in a cross section perpendicular to the end surface of the piston (20) is T-shaped, triangular rectangular or rectangular, the lower part of the triangular rectangle is a triangle, the upper part is a rectangle, and the sides of the upper part of the triangle are the sides of the lower part of the rectangle.

6. The pump body assembly of the rotary compressor according to claim 5, characterized in that: When the kinetic energy dissipation cavity (100) cut in a cross section perpendicular to the end face of the piston (20) is T-shaped or triangularly rectangular, the width of the end face of the first end face of the balancing block (30) close to the central axis of the piston (20) in the radial direction is b3, the width of the end face away from the central axis of the piston (20) is b1, the width between the end face close to the central axis of the piston (20) and the end face away from the central axis of the piston (20) is b2, and the following relationship is satisfied: b1+b2+b3=b, b1=b2=b3.

7. The pump body assembly of the rotary compressor according to claim 5, characterized in that: When the kinetic energy dissipation cavity (100) cut in a cross section perpendicular to the end surface of the piston (20) is T-shaped, the maximum depth of the kinetic energy dissipation cavity (100) is H, and the minimum depth of the kinetic energy dissipation cavity (100) is h, wherein the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 2.5 times of h.

8. The pump body assembly of the rotary compressor according to claim 5, characterized in that: When the kinetic energy dissipation cavity (100) cut in a cross section perpendicular to the end face of the piston (20) is a triangular rectangle, the side length of the triangular cross-section portion of the kinetic energy dissipation cavity (100) close to the central axis of the piston (20) is L1, and the side length of the side away from the central axis of the piston (20) is L2, and the angle between L1 and L2 is D, wherein the value range of D is 20°~47°.

9. The pump body assembly of the rotary compressor according to claim 2, characterized in that: The maximum depth of the kinetic energy dissipation cavity (100) is H, and the minimum depth thereof is h1, wherein H and h1 satisfy that the value of H is between 0.3 mm and 0.8 mm, and the value of H is 2 to 3 times that of h1.

10. The pump body assembly of the rotary compressor according to claim 8, characterized in that: The kinetic energy dissipation cavity (100) has a width B1 at the end surface close to the central axis of the piston (20) and a width B2 at the end surface away from the central axis of the piston (20) in the radial direction along the second end surface of the piston (20), satisfying the following relationship: B1=B2.

11. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The cylinder structure (10) includes a cylinder (11), an upper flange (12) and a lower flange (13). The first end face of the piston (20) is adjacent to and parallel to the end face of the upper flange (12). The distance between the first end face of the piston (20) and the upper flange (12) is δ. The deepest depth of the kinetic energy dissipation cavity (100) is H, and H / δ is between 1.5 and 2.

25.

12. The pump body assembly of the rotary compressor according to claim 1, characterized in that: The installation space is an installation through hole penetrating the first end face and the second end face of the piston (20); or the installation space is an installation groove provided at the first end of the piston (20).

13. The pump body assembly of the rotary compressor according to claim 12, characterized in that: When the installation space is an installation through hole, the second end face of the balance weight (30) and the second end face of the piston (20) are in the same plane.

14. The pump body assembly of the rotary compressor according to claim 13, characterized in that: There are a plurality of the installation through holes, and the plurality of installation through holes are arranged at intervals along the circumferential direction of the piston (20) to form an annular installation through hole.

15. The pump body assembly of the rotary compressor according to claim 14, characterized in that: The number of installation through holes in one annular installation through hole is Z, where Z is a positive integer between 18 and 36.

16. The pump body assembly of the rotary compressor according to claim 15, characterized in that: The circumferential angle corresponding to the arc length of the installation through hole is d1, and the circumferential angle of the distance between two adjacent installation through holes on the same circumference is d2. The d1 and d2 satisfy: 3° < d2 < 5°, and d1 / d2 is between 3 and 5.

17. The pump body assembly of the rotary compressor according to claim 16, characterized in that: There are a plurality of the annular installation through holes, and the plurality of annular installation through holes are arranged at intervals along the radial direction of the piston (20).

18. The pump body assembly of the rotary compressor according to claim 17, characterized in that: The annular installation through holes at different radial positions are arranged at a certain angle offset in the circumferential direction along the second end face of the piston (20).

19. The pump body assembly of the rotary compressor according to claim 17, characterized in that: The offset angle between the annular installation through holes on two adjacent circumferences is d3, and d1 / d3 is equal to 3.

20. The pump body assembly of the rotary compressor according to claim 17, characterized in that: The minimum distance between adjacent annular installation through holes along the radial direction of the piston (20) is ∆r, and the value range of ∆r is between 0.4 mm and 1.0 mm.

21. The pump body assembly of the rotary compressor according to claim 20, characterized in that: The outer edge of the installation through hole on the outermost circumference of the first end face of the piston (20) is at a distance E1 from the outer edge of the first end face of the piston (20). The inner edge of the installation through hole on the innermost circumference of the first end face of the piston (20) is at a distance E2 from the inner edge of the first end face of the piston (20). It satisfies E1 = E2 = E, and E / ∆r is between 2 and 3.

22. The pump body assembly of the rotary compressor according to claim 17, characterized in that: The number of the plurality of annular installation through holes is Y, where Y is a positive integer between 3 and 5.

23. The pump body assembly of the rotary compressor according to claim 14, characterized in that: The number of installation through holes in each annular installation through hole is the same, or the number of installation through holes included in each annular installation through hole is different.

24. The pump body assembly of the rotary compressor according to claim 13, characterized in that: The width of the installation through hole in the radial direction along the second end face of the piston (20) is b, where the value range of b is between 0.9 mm and 1.5 mm.

25. The pump body assembly of the rotary compressor according to claim 1, characterized in that: Both the piston (20) and the balance weight (30) are made of ceramic materials.

26. A rotary compressor, comprising a compressor body and a pump assembly mounted on the compressor body, characterized in that: The pump body assembly is the pump body assembly according to any one of claims 1 to 25.

27. An air conditioner, comprising a compressor, characterized in that: The compressor is the rotary compressor according to claim 26.

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