CN211819906U

CN211819906U - Pump body assembly of rotor compressor, rotor compressor and air conditioner

Info

Publication number: CN211819906U
Application number: CN201922055507.8U
Authority: CN
Inventors: 闫鹏举; 王珺; 吴健; 张心爱; 孙成龙
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai; Zhuhai Gree Energy Saving Environmental Protection Refrigeration Technology Research Center Co Ltd
Priority date: 2019-11-22
Filing date: 2019-11-22
Publication date: 2020-10-30
Anticipated expiration: 2029-11-22

Abstract

The utility model provides a rotor compressor's pump body subassembly, rotor compressor and air conditioner, rotor compressor's pump body subassembly includes: a cylinder structure; the piston is arranged in the cylinder structure, an installation space is arranged on the piston, and an opening of the installation space is formed in the first end face of the piston; the balance block is arranged in the mounting space; and the crankshaft is connected with the first end surface of the piston. The technical scheme of the utility model the pump body subassembly among the prior art has been solved effectively because the eccentric settings of barycenter, the bent axle produces the problem that the amount of deflection warp easily.

Description

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

Technical Field

The utility model relates to a technical field of compressor particularly, relates to a rotor compressor's pump body subassembly, rotor compressor and air conditioner.

Background

In the industry of rotor compressors in recent years, the models of the compressors are gradually miniaturized and high-frequency is taken as the main development direction, new products are researched and developed aiming at the conditions from small discharge capacity to large discharge capacity and from low energy efficiency to high energy efficiency, and the core competitiveness of air conditioner products in domestic and foreign markets is improved by reducing the material cost of the compressors.

The pump body structure of the rolling rotor compressor mainly comprises an air cylinder, a rolling piston, a crankshaft, a slip sheet, a spring and flanges assembled at two ends of the air cylinder. For the development of the traditional single-cylinder rolling rotor compressor in the high-speed field, the problem of serious deflection deformation of a crankshaft mainly exists: because the crankshaft is provided with the eccentric part, when the crankshaft rotates at a high rotating speed of about 120rps, the eccentric part and the rolling piston sleeved on the excircle of the eccentric part have larger centrifugal force, so that the eccentric part of the crankshaft and the part of the crankshaft long shaft at the cantilever end of the crankshaft, which extends out of the flange on the cylinder, generate larger deflection deformation, and the friction power consumption of the compressor is increased, the air gap between the stator and the rotor of the motor is reduced, the vibration effect of the compressor is increased, and the power consumption of the compressor, the efficiency of the motor and the vibration and noise level of the compressor are increased.

SUMMERY OF THE UTILITY MODEL

The utility model discloses a main aim at provides a rotor compressor's pump body subassembly, rotor compressor and air conditioner to solve the pump body subassembly among the prior art because the eccentric settings of barycenter, the bent axle produces the problem that the amount of deflection warp easily.

In order to achieve the above object, according to an aspect of the present invention, there is provided a pump body assembly of a rotary compressor including: a cylinder structure; the piston is arranged in the cylinder structure, an installation space is arranged on the piston, and an opening of the installation space is formed in the first end face of the piston; the balance block is arranged in the mounting space; and the crankshaft is connected with the first end surface of the piston.

Further, the balance 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 balance weight and the first end surface of the piston.

Further, the first end surface of the balance weight is non-planar.

Further, the first end of the weight has a groove.

Further, the width of the groove of the weight in the radial direction of the piston is b0, wherein b0 ranges from 0.3mm to 0.5 mm.

Further, the kinetic energy dissipating cavities cut perpendicular to the cross section of the end face of the piston are T-shaped, triangular rectangular, or rectangular.

Further, when the kinetic energy dissipation cavity cut perpendicular to the cross section of the end surface of the piston is T-shaped or triangular rectangular, the width of the end surface of the first end surface of the weight in the radial direction close to the central axis of the piston is b1, the width of the end surface far from the central axis of the piston is b3, and the width between the end surface close to the central axis of the piston and the end surface far from the central axis of the piston is b3, and the following relationships are satisfied: b1+ b2+ b3 ═ b, b1 ═ b2 ═ b 3.

Further, when the kinetic energy dissipation cavity cut perpendicular to the section of the end face of the piston is T-shaped, the maximum depth of the kinetic energy dissipation cavity is H, the minimum depth of the kinetic energy dissipation cavity is H, the value of H is between 0.3mm and 0.8mm, and the value of H is 2 to 2.5 times of H.

Further, when the kinetic energy dissipation cavity cut perpendicular to the section of the end surface of the piston is triangular rectangular, the side length of the triangular section part of the kinetic energy dissipation cavity on the side close to the central axis of the piston is L1, the side length of the side far away from the central axis of the piston is L2, the included angle between L1 and L2 is D, and the value range of D is 20-47 °.

Furthermore, the maximum depth of the kinetic energy dissipation cavity is H, the minimum depth of the kinetic energy dissipation cavity is H1, wherein H and H1 satisfy that the value of H is between 0.3mm and 0.8mm, and the value of H is 2 to 3 times of H1.

Further, the kinetic energy dissipation cavity has a width B1 of an end surface close to the central axis of the piston and a width B2 of an end surface away from the central axis of the piston in a radial direction along the second end surface of the piston, and satisfies the following relationship: b1 ═ B2.

Further, the cylinder structure includes cylinder, upper flange and lower flange, and the first terminal surface of piston is adjacent and parallel arrangement with the terminal surface of upper flange, and the distance of the first terminal surface of piston and upper flange is, and the deepest degree of depth of kinetic energy dissipation cavity is H, and H/is between 1.5 ~ 2.25.

Furthermore, the mounting space is a mounting through hole penetrating through the first end surface of the piston and the second end surface of the piston; or the mounting space is a mounting groove provided at the first end of the piston.

Furthermore, when the installation space is the installation through hole, the second end surface of the balance block and the second end surface of the piston are located on the same plane.

Further, the installation through-hole is a plurality of, and a plurality of installation through-holes set up in order to form annular installation through-hole along the circumference looks interval of piston.

Further, the number of the mounting through holes of one annular mounting through hole is Z, wherein the value of Z is a positive integer between 18 and 36.

Further, the arc length of the mounting through hole corresponds to a circumferential angle d1, the distance between two adjacent mounting through holes on the same circumference has a circumferential angle d2, and d1 and d2 satisfy the following conditions: 3 < d2<5 DEG, and d1/d2 is between 3 and 5.

Further, the annular mounting through hole includes a plurality of, and a plurality of annular mounting through holes are arranged at intervals along the radial direction of the piston.

Further, the annular mounting through holes different in the radial direction are arranged in a staggered manner at a certain angle in the circumferential direction of the second end face of the piston.

Further, the annular mounting through holes on two adjacent circumferences are staggered by an angle d3, and d1/d3 is equal to 3.

Furthermore, the minimum distance of the adjacent annular mounting through holes along the radial direction of the piston is delta r, and the value range of delta r is between 0.4mm and 1.0 mm.

Further, the outer edge of the mounting through hole on the outermost circumference on the first end surface of the piston is a distance E1 from the outer edge of the first end surface of the piston, the inner edge of the mounting through hole on the innermost circumference on the first end surface of the piston is a distance E2 from the inner edge of the first end surface of the piston, and it is satisfied that E1 is E2 is E, and E/Δ r is between 2 and 3.

Further, 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.

Further, the number of the mounting through holes of each annular mounting through hole is the same, or the number of the mounting through holes included in each annular mounting through hole is different.

Further, the width of the mounting through hole in the radial direction along the second end surface of the piston is b, wherein the value range of b is between 0.9mm and 1.5 mm.

Further, the piston and the balance mass are both made of a ceramic material.

Further, the piston and the counterweight are of different materials.

According to the utility model discloses an on the other hand provides a rotor compressor, including the compressor main part with install the pump body subassembly in the compressor main part, pump body subassembly is foretell pump body subassembly.

According to another aspect of the present invention, there is provided an air conditioner, comprising a compressor, wherein the compressor is a rotor compressor as described above.

Use the technical scheme of the utility model, piston self is provided with installation space, and the balancing piece setting is in installation space. The center of mass of the pump body assembly can be positioned on the crankshaft by arranging the balance block, so that large deflection deformation of the crankshaft caused by eccentricity of the pump body assembly is greatly reduced. The technical scheme of the utility model the pump body subassembly among the prior art has been solved effectively because the eccentric settings of barycenter, the bent axle produces the problem that the amount of deflection warp easily.

Drawings

The accompanying drawings, which form a part of the present application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:

figure 1 shows a schematic cross-sectional view of an embodiment of a pump body assembly according to the present invention;

FIG. 2 shows an enlarged schematic view at E of the pump body assembly of FIG. 1;

FIG. 3 shows a schematic view of the compression process of the pump body assembly of FIG. 1;

FIG. 4 shows a schematic end view of a piston of the pump block assembly of FIG. 1;

FIG. 5 shows a schematic cross-sectional view at A-A of the piston of FIG. 4;

figure 6 shows a schematic view of the mating arrangement of the piston and counterweight of the pump block assembly of figure 1.

Wherein the figures include the following reference numerals:

10. a cylinder structure; 11. a cylinder; 12. an upper flange; 13. a lower flange; 20. a piston; 30. a counterbalance; 40. a crankshaft; 100. a kinetic energy dissipating cavity.

Detailed Description

It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.

As shown in fig. 1 to 6, the pump body assembly of the rotor compressor of the present embodiment includes: cylinder structure 10, piston 20, counterbalance 30, and crankshaft 40. The piston 20 is disposed in the cylinder structure 10, and the piston 20 is provided with an installation space, and a first end surface of the piston 20 has an opening of the installation space. The weight 30 is disposed in the installation space. A crankshaft 40 is connected to a first end surface of the piston 20.

As shown in fig. 2 and 6, in the solution of the present embodiment, the balance weight 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 balance weight 30 and the first end surface of the piston 20. The kinetic energy dissipation cavity 100 converts the kinetic energy of the gas in the pump body assembly into pressure energy, thereby greatly reducing the gas leakage of the compression cavity in the pump body assembly. When gas is sucked into a suction cavity in the pump body assembly, vortex is formed, and the kinetic energy dissipation cavity 100 can convert the kinetic energy of the gas vortex into pressure energy, so that the compression cavity and the exhaust cavity are better isolated.

Specifically, to better convert the kinetic energy of the gas into pressure energy, the first end surface of the counterweight 30 is non-planar. The non-plane can be a curved surface, a groove and the like. 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 of b0 ranges from 0.3mm to 0.5 mm. It should be noted that b0 is the width of the widest part of the groove, and when the value range of b0 is between 0.3mm and 0.5mm, the effect is better. The two side walls of the groove can be vertical surfaces or inclined surfaces.

As shown in fig. 2 and 6, in the present embodiment, the kinetic energy dissipation cavity 100 cut perpendicular to the cross section of the end surface of the piston 20 is T-shaped, triangular rectangular, or rectangular. Fig. 2 shows a T-shaped kinetic energy dissipation cavity 100, and fig. 6 shows a triangular rectangular kinetic energy dissipation cavity 100, where a triangular rectangle is interpreted as a combination of a triangle with a lower portion and an upper portion, and the sides of the upper portion are the sides of the lower portion. The experimental data of the gas leakage of the three kinetic energy dissipation cavities 100 are shown in the following table, and the sealing effect of the kinetic energy dissipation cavity 100 with the T-shaped section is best shown in the following table.

As shown in fig. 2, in the present embodiment, when the kinetic energy dissipation cavity 100 cut perpendicular to the cross section of the end surface of the piston 20 is T-shaped or triangular rectangular, the width of the end surface of the first end surface of the weight 30 close to the central axis of the piston 20 in the radial direction is b1, the width of the end surface far from the central axis of the piston 20 is b3, and the width between the end surface close to the central axis of the piston 20 and the end surface far from the central axis of the piston 20 is b3, and the following relationships are satisfied: b1+ b2+ b3 ═ b, b1 ═ b2 ═ b 3. The structure has low processing cost, and the balance weight 30 is firmer and has longer service cycle.

As shown in fig. 2, in the technical solution of this embodiment, when the kinetic energy dissipation cavity 100 cut perpendicular to the cross section of 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, where the value of H is between 0.3mm and 0.8mm, and the value of H is 2 to 2.5 times of H. The structure of the kinetic energy dissipation cavity 100 can also ensure the strength of the piston 20, and when the structural form of the kinetic energy dissipation cavity 100 of the present embodiment is T-shaped, the above-mentioned values of H and H have a good sealing effect.

As shown in fig. 6, as another structural form of the kinetic energy dissipation cavity 100 of the present embodiment, when the kinetic energy dissipation cavity 100 cut perpendicular to the cross section of the end surface of the piston 20 is a triangular rectangular shape, the side length of the triangular cross section of the kinetic energy dissipation cavity 100 on the side close to the central axis of the piston 20 is L1, the side length of the triangular cross section of the kinetic energy dissipation cavity 100 on the side away from the central axis of the piston 20 is L2, the included angle between L1 and L2 is D, and the value of D ranges from 20 ° to 47 °. The structure has lower processing cost and firmer structure of the balance weight 30.

Specifically, when the kinetic energy dissipation cavity 100 has a triangular rectangular cross section, the maximum depth of the kinetic energy dissipation cavity 100 is H, and the minimum depth thereof is H1, where H and H1 satisfy that the value of H is between 0.3mm and 0.8mm, and the value of H is 2 to 3 times of H1. The above values ensure the sealing effect and make the balance weight 30 stronger. The kinetic energy dissipation cavity 100 has a width B1 of an end surface close to the central axis of the piston 20 and a width B2 of an end surface far from the central axis of the piston 20 in a radial direction along the second end surface of the piston 20, and satisfies the following relationship: b1 ═ B2. The equal widths result in the same strength of the weight 30, which extends the life cycle of the weight 30.

As shown in fig. 2, in the technical solution of the present embodiment, the cylinder structure 10 includes a cylinder 11, an upper flange 12 and a lower flange 13, the first end surface of the piston 20 is adjacent to and parallel to the end surface of the upper flange 12, the distance between the first end surface of the piston 20 and the upper flange 12 is H, and the deepest depth of the kinetic energy dissipation cavity 100 is H, where H/is between 1.5 and 2.25. The kinetic energy dissipation cavity 100 described above has a good sealing effect.

As shown in fig. 1 to 6, in the solution of the present embodiment, the mounting space is a mounting through hole penetrating through the first end surface of the piston 20 and the second end surface of the piston 20; or the mounting space is a mounting groove provided at the first end of the piston 20. The structure enables the pump body assembly to be compact in structure, and a balancing block structure does not need to be additionally arranged on the pump body assembly.

As shown in fig. 1 to 6, in the present embodiment, when the installation space is an installation through hole, the second end surface of the balance weight 30 and the second end surface of the piston 20 are located on the same plane. According to the characteristics of the pump body assembly, the lower flange and the piston are sealed through an oil film, so that the second end surface of the balance weight 30 and the second end surface of the piston 20 are located on the same plane.

As shown in fig. 3, in the solution of the present embodiment, the number of the mounting through holes is plural, and the plural mounting through holes are provided at intervals along the circumferential direction of the piston 20 to form an annular mounting through hole. The installation through hole of above-mentioned structure is stronger in regularity, is convenient for set up balancing piece 30.

As shown in fig. 3, in the technical solution of this embodiment, the number of the mounting through holes of one annular mounting through hole is Z, where Z is a positive integer between 18 and 36. The installation through hole is easy to process, and the setting regularity is strong.

As shown in fig. 4, in the technical solution of the present embodiment, a circumferential angle corresponding to an arc length of the mounting through hole is d1, a circumferential angle of a distance between two adjacent mounting through holes on the same circumference is d2, and d1 and d2 satisfy: 3 < d2<5 DEG, and d1/d2 is between 3 and 5. The mounting holes ensure the strength of the piston 20 and cooperate well with the balance mass 30 to prevent gas leakage from the high pressure region to the low pressure region.

As shown in fig. 4, in the solution of the present 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 in the radial direction of the piston 20. The balance weight 30 and the mounting through hole are assembled together to form a kinetic energy dissipation cavity and a throttling gap which act together to seal air. The arrangement of the mounting through holes is designed for the final formed sealing structure (kinetic energy dissipation cavity + throttling gap). The kinetic energy dissipation cavities 100 with the structure are arranged at intervals, so that gas flowing through the leakage channel can dissipate kinetic energy in more kinetic energy dissipation cavities as far as possible, adjacent pressure difference is reduced as far as possible, the effect of minimum leakage amount is obtained, and the sealing effect is more remarkable as the rotating speed of the pump body is higher. The multi-group sealing structure (the kinetic energy dissipation cavity and the throttling gap) can be used for isolating gas leakage in a multi-layer mode, and gas sealing is facilitated.

As shown in fig. 4, in the solution of the present embodiment, the annular mounting through holes different in the radial direction are arranged at a certain angle offset in the circumferential direction of the second end face of the piston 20. The structure avoids the situation that the gaps between the installation through holes of different rings are opposite, and the strength of the structure is high when the gaps between the installation through holes of different rings are opposite.

As shown in fig. 4, in the solution of the present embodiment, the offset angle of the annular mounting through holes on two adjacent circumferences is d3, and d1/d3 is equal to 3. The overlapping amount between the installation through holes of different circular rings of the structure is large, and gas leakage is avoided.

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

As shown in fig. 6, in the present embodiment, the distance from the outer edge of the mounting through-hole on the outermost circumference on the first end surface of the piston 20 to the outer edge of the first end surface of the piston 20 is E1, the distance from the inner edge of the mounting through-hole on the innermost circumference on the first end surface of the piston 20 to the inner edge of the first end surface of the piston 20 is E2, and it is satisfied that E1 is E2 is E, and E/Δ r is between 2 and 3. The outermost and innermost portions of the piston 20 are subjected to a large force, and the above-described structure ensures that the piston 20 is relatively strong.

As shown in fig. 4 and 5, in the technical solution of the present embodiment, the number of the plurality of annular mounting through holes is Y, where the value of Y is a positive integer between 3 and 5. The structure ensures that the piston 20 is firmer on one hand and the sealing effect of the pump body assembly is better on the other hand.

As shown in fig. 4, in the solution of the present 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-holes can be arranged as desired.

As shown in fig. 2, in the solution of the present embodiment, the width of the mounting through hole in the radial direction of the second end surface of the piston 20 is b, wherein the value of b ranges from 0.9mm to 1.5 mm. The above structure ensures that the piston 20 is relatively strong and the weight 30 is easily engaged with the piston 20.

As shown in fig. 1 to 6, in the solution of the present embodiment, the piston 20 and the weight 30 are both made of a ceramic material. The above materials make the pump block assembly lighter in weight and reduce centrifugal force when the crankshaft 40 rotates at high speed. Specifically, the piston 20 and the balance weight 30 are both manufactured through processes such as high-temperature sintering and sand blasting, so that the piston 20 and the balance weight 30 are firmly fitted. Further specifically, the materials of the piston 20 and the weight 30 are different.

The pump body assembly of the application is provided with a plurality of annular kinetic energy dissipation cavities on the matched end face of the piston 20 and the upper flange 12, so that the sealing performance between the piston 20 and the upper flange 12 is greatly enhanced, and the problem of sealing of the part with the largest leakage rate of the pump body of the rolling rotor compressor is solved, thereby improving the sealing performance and the volume efficiency of the pump body of the rolling rotor compressor. The piston 20 and the upper flange 12 matched end face are provided with the annular kinetic energy dissipation cavities 100, so that the contact area between the end face of the piston 20 and the end face of the upper flange 12 is reduced, friction and abrasion of a friction pair are reduced, and the power consumption of the compressor is reduced. The utility model provides a plurality of kinetic energy dissipation cavities 100 of seting up on piston 20 and the last flange 12 complex terminal surface have increased the oil reserve of refrigeration oil in piston and last flange fit clearance, are favorable to the mating surface to form the oil film, have strengthened the lubrication between the mating surface, have reduced the friction consumption of compressor. The density of the piston material in this application is about half of the density of conventional piston material, and seted up a plurality of annular kinetic energy dissipation cavities 100 on the piston terminal surface for the quality of piston 20 has reduced 50% at least, so can reduce the eccentric produced centrifugal force when bent axle 40 hypervelocity is rotatory effectively, improve the vibration and the noise problem of compressor, reduced the quality of installing at rotor both ends balancing piece simultaneously, reduced the manufacturing cost of compressor. The piston material has the advantages of small surface friction coefficient and good surface smoothness, can effectively reduce the abrasion of a roller friction pair, and reduces the power consumption of the compressor. The piston material has high hardness and high wear resistance, and can raise the running reliability of the compressor in superhigh speed condition greatly.

As can be seen from the above: the development of traditional single cylinder rolling rotor formula compressor in the high-speed field mainly has two bottleneck problems, and a bent axle amount of deflection warp seriously: because the crankshaft is provided with the eccentric part, when the crankshaft rotates at a high rotating speed (the rotating speed is about 120 rps), the eccentric part and the rolling piston sleeved on the excircle of the eccentric part have larger centrifugal force, so that the eccentric part of the crankshaft and the cantilever end of the crankshaft (the part of the long shaft of the crankshaft extending out of the flange on the cylinder) generate larger deflection deformation, the friction power consumption of the compressor is increased, the air gap between the stator and the rotor of the motor is reduced, the vibration effect of the compressor is increased, and the power consumption of the compressor, the efficiency of the motor and the vibration and noise level of the compressor are increased. The second gas leakage amount is large: because a certain assembly gap exists in pump body parts of the rolling rotor type compressor, when a large pressure difference exists on two sides of the assembly gap, a large amount of gas refrigerant can be leaked from a high-pressure area to a low-pressure area through the pump body assembly gap, and the volumetric efficiency and the energy efficiency of the compressor are reduced. However, in order to realize the development of the miniaturization and high speed of the rotor compressor, that is, the rotating speed of the motor of the single-cylinder rolling rotor compressor is increased from 120rps to 200rps or even to 240rps, the above two problems are further aggravated and worsened, which causes the serious abrasion of the parts of the compressor pump body, the sharp increase of the leakage total amount of the gas working medium in unit time, the collision and sweeping of the motor rotor and the stator, and the exceeding of the vibration and noise level of the compressor, and in serious cases, the jamming and shutdown of the compressor pump body are caused. The technical scheme of the application effectively solves the two problems when the rotating speed of the motor is higher than 120 rps.

The application also provides a rotor compressor, including compressor body and the pump body subassembly of installing in compressor body. The pump body component is the pump body component.

The application also provides an air conditioner comprising a compressor. The compressor is the above-mentioned rotary compressor.

The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A pump body assembly of a rotary compressor, comprising:

a cylinder structure (10);

the piston (20) is arranged in the cylinder structure (10), an installation space is arranged on the piston (20), and the first end face of the piston (20) is provided with an opening of the installation space;

a weight (30), the weight (30) being disposed within the mounting space;

a crankshaft (40), the crankshaft (40) being connected to a first end surface of the piston (20).

2. Pump block assembly of a rotary compressor, according to claim 1, characterized in that said counterweight (30) is lower than said first end face of said piston (20), so that a kinetic energy dissipation cavity (100) is formed between said first end face of said counterweight (30) and said first end face of said piston (20).

3. Pump body assembly of a rotary compressor, according to claim 2, characterized in that the first end face of the counterweight (30) is non-planar.

4. Pump body assembly of a rotary compressor, according to claim 2, characterized in that the first end face of the counterweight (30) has a groove.

5. Pump block assembly of a rotary compressor, according to claim 4, characterized in that the groove of the counterweight (30) has a width b in the radial direction of the piston (20)₀Wherein, said b₀The value range of (A) is between 0.3mm and 0.5 mm.

6. Pump body assembly of a rotary compressor, according to claim 2, characterized in that the kinetic energy dissipation cavities (100) cut perpendicularly to the section of the end face of the piston (20) are T-shaped, triangular rectangular or rectangular.

7. The pump body assembly of a rotary compressor according to claim 6, wherein when the kinetic energy dissipation cavity (100) cut perpendicular to the section of the end surface of the piston (20) is T-shaped or triangular rectangular, the end surface of the first end surface of the weight (30) close to the central axis of the piston (20) has a width b1, the end surface away from the central axis of the piston (20) has a width b3, and the width between the end surface close to the central axis of the piston (20) and the end surface away from the central axis of the piston (20) is b3, and the following relationships are satisfied: b1+ b2+ b3 ═ b, b1 ═ b2 ═ b 3.

8. The pump body assembly of a rotary compressor, according to claim 2, characterized in that when the kinetic energy dissipation cavity (100) cut perpendicularly to the section of 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 0.3mm and 0.8mm and the value of H is 2 to 2.5 times H.

9. The pump body assembly of a rotary compressor according to claim 2, wherein when the kinetic energy dissipation cavity (100) cut perpendicular to the section of the end surface of the piston (20) is triangular rectangular, the side length of the triangular section portion of the kinetic energy dissipation cavity (100) on the side close to the central axis of the piston (20) is L1, the side length of the side far from the central axis of the piston (20) is L2, and the included angle between L1 and L2 is D, wherein D has a value ranging from 20 ° to 47 °.

10. Pump body assembly of a rotary compressor, according to claim 3, characterized in that the maximum depth of said kinetic energy dissipation cavity (100) is H, and the minimum depth thereof is H1, where H and H1 satisfy the condition that the value of H is between 0.3mm and 0.8mm, and the value of H is 2 to 3 times H1.

11. The pump block assembly of the rotary compressor according to claim 9, wherein the kinetic energy dissipation cavity (100) has a width B1 of an end face close to the central axis of the piston (20) and a width B2 of an end face away from the central axis of the piston (20) in a radial direction along the second end face of the piston (20), satisfying the following relationship: b1 ═ B2.

12. The pump body assembly of the rotor compressor, according to claim 2, is characterized in that the cylinder structure (10) comprises a cylinder (11), an upper flange (12) and a lower flange (13), the first end face of the piston (20) is arranged adjacent to and parallel to the end face of the upper flange (12), the first end face of the piston (20) is at a distance from the upper flange (12), and the deepest depth of the kinetic energy dissipation cavity (100) is H, H/is between 1.5 and 2.25.

13. The pump block assembly of the rotary compressor according to claim 2, wherein the mounting space is a mounting through hole penetrating a first end face of the piston (20) and a second end face of the piston (20); or the mounting space is a mounting groove provided at a first end of the piston (20).

14. The pump block assembly of a rotary compressor according to claim 13, wherein when the mounting space is a mounting through hole, the second end surface of the weight (30) and the second end surface of the piston (20) are located on the same plane.

15. The pump body assembly of a rotary compressor according to claim 14, wherein the mounting through-hole is plural, and the plural mounting through-holes are provided at intervals in a circumferential direction of the piston (20) to form an annular mounting through-hole.

16. The pump body assembly of the rotary compressor, according to claim 15, wherein the number of the mounting through holes of one annular mounting through hole is Z, wherein Z is a positive integer between 18 and 36.

17. The pump body assembly of the rotary compressor of claim 16, wherein the arc length of the mounting through hole corresponds to a circumferential angle d1, the circumferential angle of the distance between two adjacent mounting through holes on the same circumference is d2, and the d1 and the d2 satisfy the following conditions: 3 < d2<5 DEG, and d1/d2 is between 3 and 5.

18. The pump block assembly of the rotary compressor according to claim 17, wherein the annular mounting through hole comprises a plurality of annular mounting through holes arranged at intervals in a radial direction of the piston (20).

19. The pump block assembly of the rotary compressor according to claim 18, wherein the annular mounting through holes different in the radial direction are arranged offset at an angle in the circumferential direction along the second end face of the piston (20).

20. The pump body assembly of the rotary compressor of claim 18, wherein the annular mounting through holes on two adjacent circumferences are staggered by an angle d3, and the d1/d3 is equal to 3.

21. The pump body assembly of the rotary compressor, according to claim 18, characterized in that the minimum distance between adjacent annular mounting through holes along the radial direction of the piston (20) is Δ r, and the value of Δ r ranges from 0.4mm to 1.0 mm.

22. The pump block assembly of the rotary compressor according to claim 21, wherein the distance from the outer edge of the mounting through hole on the outermost circumference on the first end surface of the piston (20) to the outer edge of the first end surface of the piston (20) is E1, the distance from the inner edge of the mounting through hole on the innermost circumference on the first end surface of the piston (20) to the inner edge of the first end surface of the piston (20) is E2, and E1-E2-E and E/Δ r are between 2 and 3.

23. The pump body assembly of the rotary compressor, according to claim 18, wherein the number of the plurality of annular mounting through holes is Y, wherein Y is a positive integer between 3 and 5.

24. The pump body assembly of a rotary compressor of claim 15, wherein the number of the mounting through holes of each of the annular mounting through holes is the same or the number of the mounting through holes included in each of the annular mounting through holes is different.

25. The pump body assembly of the rotary compressor according to claim 14, wherein the mounting through hole has a width b in a radial direction along the second end face of the piston (20), wherein b ranges from 0.9mm to 1.5 mm.

26. Pump block of a rotary compressor, according to claim 1, characterized in that said piston (20) and said counterweight (30) are made of ceramic material.

27. Pump body assembly of a rotary compressor, according to claim 26, characterized in that said piston (20) and said counterweight (30) are of different material.

28. A rotary compressor comprising a compressor body and a pump body assembly mounted on the compressor body, wherein the pump body assembly is as claimed in any one of claims 1 to 27.

29. An air conditioner including a compressor, wherein the compressor is the rotary compressor of claim 28.