CN212296875U - Compression pump body assembly, compressor and air conditioner - Google Patents

Abstract

The utility model provides a compression pump body subassembly, compressor, air conditioner, wherein compression pump body subassembly, including the bent axle, along first muffler, first flange, first cylinder, second flange, first baffle, the apron of the axial of bent axle closed assembly in proper order, it holds the chamber to have the air current on the apron, still includes first pressure pulsation decay passageway, first pressure pulsation decay passageway link up first muffler inner chamber with the air current holds the chamber, the compressed air current that first cylinder formed can discharge the inner chamber of first muffler and warp discharge to the motor cavity of resorption that the compressor had behind the first pressure pulsation decay passageway. According to the utility model discloses a compression pump body subassembly, compressor, air conditioner discharges into the motor lower chamber after reducing the exhaust pressure pulsation in introducing the pressure pulsation decay passageway earlier with the working chamber exhaust, effectively reduces the aerodynamic noise in the compressor.

Description

Compression pump body assembly, compressor and air conditioner

Technical Field

The utility model belongs to the technical field of air conditioning, concretely relates to compression pump body subassembly, compressor, air conditioner.

Background

Noise of a household air conditioner is an important factor affecting the comfort index of residents, and noise generated by a compressor is a main source of noise in an air conditioning system. The noise component of the compressor is complex, mainly including aerodynamic noise, mechanical noise and electromagnetic noise. Since the exhaust pressure pulsation is generated due to the uneven exhaust flow rate, on the one hand, significant aerodynamic noise is generated, and on the other hand, the gas reacts on a mechanical structure to generate mechanical noise, and therefore, the reduction of the pressure pulsation is important for controlling the aerodynamic noise.

At present, for noise reduction of a compressor, a mode of arranging a silencing cavity (resonant cavity) on an exhaust flow path of the compressor is mostly adopted, but the silencing capability of the mode is limited.

SUMMERY OF THE UTILITY MODEL

Therefore, the to-be-solved technical problem of the utility model is to provide a compression pump body subassembly, compressor, air conditioner discharges into the motor lower chamber again after reducing the exhaust pressure pulsation in introducing the pressure pulsation decay passageway earlier, effectively reduces the aerodynamic noise in the compressor.

In order to solve the problem, the utility model provides a compression pump body subassembly, including the bent axle, along first muffler, first flange, first cylinder, second flange, first baffle, the apron of axial closed assembly in proper order of bent axle, it holds the chamber to have the air current on the apron, still includes first pressure pulsation decay passageway, first pressure pulsation decay passageway link up first muffler inner chamber with the chamber is held to the air current, the compressed air current that first cylinder formed can discharge the inner chamber of first muffler and warp discharge to the motor cavity of resorption that the compressor had behind the first pressure pulsation decay passageway.

Preferably, the compression pump body assembly further comprises a second pressure pulsation attenuation channel, and the air flow containing cavity is communicated with the lower motor cavity through the second pressure pulsation attenuation channel.

Preferably, the first pressure pulsation damping channel sequentially penetrates through an inner cavity of the first muffler, the first flange, the first cylinder, the second flange and the first partition plate; and/or the second pressure pulsation attenuation channel sequentially penetrates through the airflow containing cavity, the first partition plate, the second flange, the first cylinder, the first flange, the mounting skirt part of the first silencer and the lower cavity of the motor.

Preferably, the channel wall body of the first pressure pulsation damping channel is provided with a plurality of blind holes, and the perforation rate of the blind holes is 9% -11%; and/or the channel wall body of the second pressure pulsation damping channel is provided with a plurality of holes, and the perforation rate of the blind holes is 9-11%.

Preferably, the aperture of the blind hole is D, and D is more than or equal to 2mm and less than or equal to 10 mm; and/or the depth of the blind hole is h, wherein h is more than or equal to 2mm and less than or equal to 5 mm.

Preferably, the total flow rate of the first pressure pulsation damping channel and the second pressure pulsation damping channel is Vz, the working volume of the first cylinder is Vg, and Vz/Vg is more than or equal to 0.5 and less than or equal to 1.5.

Preferably, 0.6 ≦ Vz/Vg ≦ 0.9.

Preferably, the compression pump body assembly further comprises a second muffler, and the second pressure pulsation damping channel is communicated with the lower motor cavity through the second muffler.

Preferably, the first cylinder has a suction opening, and the first pressure pulsation damping channel and/or the second pressure pulsation damping channel is/are arranged adjacent to the suction opening.

Preferably, the compression pump body subassembly still includes second baffle, second cylinder, first muffler, first flange, first cylinder, second baffle, second cylinder, second flange, first baffle, apron along the axial of bent axle is closed assembly in proper order, first pressure pulsation decay passageway link up first muffler inner chamber with the air current holds the chamber, first cylinder reaches the compressed air flow that the second cylinder formed can be discharged the inner chamber of first muffler and warp first pressure pulsation decay passageway gets into the air current holds the chamber and warp second pressure pulsation decay passageway discharges to the motor cavity of having to the compressor.

Preferably, the first pressure pulsation damping channel sequentially penetrates through an inner cavity of the first muffler, the first flange, the first cylinder, the second partition plate, the second cylinder, the second flange, the first partition plate and the airflow accommodating cavity; and/or the second pressure pulsation attenuation channel sequentially penetrates through the airflow containing cavity, the first partition plate, the second flange, the second cylinder, the second partition plate, the first cylinder, the first flange, the mounting skirt part of the first silencer and the lower motor cavity.

The utility model also provides a compressor, including foretell compression pump body subassembly.

The utility model also provides an air conditioner, including foretell compressor.

The utility model provides a compression pump body component, a compressor and an air conditioner, after the high-pressure airflow discharged from a first cylinder enters a first silencer, the high-pressure airflow is not directly discharged into a lower cavity of a motor through an exhaust port formed on the first silencer after being silenced as in the prior art, but enters the first pressure pulsation attenuation channel, then enters the airflow containing cavity after pulsation attenuation and is finally discharged into the motor lower cavity, thereby realizing the pulsation attenuation of the high-pressure airflow discharged by the first cylinder, effectively reducing the pneumatic noise in the compressor, solving the problem that the noise of the compressor, particularly the variable frequency compressor, exceeds the standard under the high-frequency condition, the technical proposal effectively reduces the pressure pulsation of the high-pressure airflow by utilizing the on-way pressure loss of the first pressure pulsation attenuation channel, although the discharge pressure (pressure loss) of the compressor is reduced to some extent, the effect is more remarkable in terms of suppression of the discharge aerodynamic noise of the compressor.

Drawings

Fig. 1 is a schematic view of a disassembled structure of a compression pump body assembly according to an embodiment of the present invention;

FIG. 2 is a schematic view of the first muffler of FIG. 1;

FIG. 3 is a schematic structural view of the first separator of FIG. 1;

FIG. 4 is a schematic structural diagram of the cover plate in FIG. 1;

FIG. 5 is a schematic view of the flow path of the exhaust gas flow in the compression pump block assembly shown in FIG. 1 (the direction of the arrows in the figure show the direction of flow);

FIG. 6 is a schematic flow path of exhaust gas flow for a prior art compression pump block assembly (two-cylinder non-dual stage compression, with the flow direction indicated by the arrows);

fig. 7 is a diagram of the exhaust pressure pulsation frequency of the compression pump body assembly according to the present invention;

FIG. 8 is a graph of discharge pressure pulsation frequency using the compression pump block assembly of FIG. 6;

fig. 9 is a noise contrast diagram of the structure adopting the technical solution of the present invention and the prior art (fig. 6);

FIG. 10 is a schematic view of the exhaust gas flow path corresponding to FIG. 1 (the direction of the arrows in the figure show the direction of flow);

fig. 11 is a schematic view of the exhaust gas flow path corresponding to the compression pump body assembly according to another embodiment of the present invention (the direction of the arrow in the figure shows the flow direction of the gas flow);

fig. 12 is a schematic view of the exhaust gas flow path corresponding to a compression pump body assembly according to yet another embodiment of the present invention (the direction of the arrows in the figure shows the direction of the gas flow).

The reference numerals are represented as:

1. a crankshaft; 2. a first muffler; 21. a first through hole; 22. a second through hole; 31. a first flange; 311. a third through hole; 32. a first cylinder; 33. a second flange; 34. a first separator; 341. a fourth via hole; 342. a fifth through hole; 35. a cover plate; 351. an airflow accommodating chamber; 36. a second separator; 37. a second cylinder; 4. a second muffler; 100. a second roller; 101. a second slide sheet.

Detailed Description

With reference to fig. 1 to 12 in combination, according to an embodiment of the present invention, there is provided a compression pump body assembly, including a crankshaft 1, a first muffler 2, a first flange 31, a first cylinder 32, a second flange 33, a first partition 34, a cover plate 35 sequentially stacked along an axial direction of the crankshaft 1, wherein the first cylinder 32 is provided therein with a first roller (not shown) and a first sliding piece (not shown) matched therewith, when the crankshaft 1 is driven by a driving motor to rotate, the first roller, the first cylinder 32 and the first sliding piece form a first working chamber of the pump body assembly, the cover plate 35 is provided thereon with an air flow accommodating chamber 351, and the compression pump body assembly further includes a first pressure pulsation damping passage, the first pressure pulsation damping passage penetrates through an inner chamber of the first muffler 2 and the air flow accommodating chamber 351, and a compressed air flow formed by the first cylinder 32 can be discharged into the inner chamber of the first muffler 2 and enter the first pressure pulsation damping passage into the inner chamber of the first muffler 2 The airflow receiving chamber 351 is discharged to a lower motor chamber of the compressor through the second pressure pulsation damping passage. In the technical scheme, the high-pressure airflow discharged from the first cylinder 32 enters the first silencer 2, is not directly discharged into the lower cavity of the motor through the exhaust port formed on the first silencer after being silenced as in the prior art, but enters the first pressure pulsation damping channel, then enters the airflow accommodating cavity 351 after pulsation damping and finally is discharged into the motor lower cavity, thereby realizing the pulsation attenuation of the high-pressure airflow discharged by the first air cylinder 32, effectively reducing the pneumatic noise in the compressor, solving the problem that the noise of the compressor, particularly the frequency conversion compressor, exceeds the standard under the high-frequency condition, the technical proposal effectively reduces the pressure pulsation of the high-pressure airflow by utilizing the on-way pressure loss of the first pressure pulsation attenuation channel, although the discharge pressure (pressure loss) of the compressor is reduced to some extent, the effect is more remarkable in terms of suppression of the discharge aerodynamic noise of the compressor. Fig. 10 shows a schematic view of the airflow flow path of the foregoing solution.

Further, the compression pump body assembly further includes a second pressure pulsation damping passage, the air flow accommodating chamber 351 is communicated with the motor lower chamber through the second pressure pulsation damping passage, and the second pressure pulsation damping passage is provided to optimize an exhaust path in the pump body assembly and further damp pressure pulsation of exhaust together with the first pressure pulsation damping passage.

The first pressure pulsation damping channel and the second pressure pulsation damping channel may be implemented by using a pipeline independent of the physical structure of the pump body assembly (for example, the above-mentioned components such as the first flange 31, the first cylinder 32, and the second flange 33), for example, the utility model discloses a pipeline (copper pipe) with a length of approximately 10m is added on the exhaust path of the existing pump body assembly for experimental comparison, and it is found that the value of the airflow pressure pulsation is greatly reduced compared with the case of not adding a long pipe, which verifies that the technical idea of reducing the airflow pressure pulsation by using the attenuation of the flow path energy is feasible. As a more preferable technical solution, the first pressure pulsation damping path passes through an inner cavity of the first muffler 2, the first flange 31, the first cylinder 32, the second flange 33, and the first partition plate 34 in this order; and/or, the second pressure pulsation damping channel sequentially penetrates through the airflow accommodating cavity 351, the first partition plate 34, the second flange 33, the first cylinder 32, the first flange 31, the mounting skirt part of the first silencer 2 and the motor lower cavity, namely, the first pressure pulsation damping channel and the second pressure pulsation damping channel are jointly formed through-flow holes constructed on the stacked parts, so that the structure of the compression pump body assembly is more compact and reasonable. Specifically, for example, the following modifications are mainly made on the basis of the various components of the existing compression pump body assembly: the exhaust hole communicated with the lower cavity of the motor on the original first muffler 2 is eliminated, and the skirt part is provided with a first through hole 21, wherein the first through hole 21 is an orifice communicated with the lower cavity of the motor by the second pressure pulsation damping channel, and the inner cavity of the first muffler 2 enters the first pressure pulsation damping channel through a second through hole 22 arranged on the first flange 31, that is, compared with the first flange 31 in the prior art, the first flange 31 is additionally provided with a second through hole 22 adapted to the first pressure pulsation damping channel, and meanwhile, the first flange 31 is additionally provided with a third through hole 311 corresponding to the first through hole 21, and through holes are arranged on the first flange 31 corresponding to the second through hole 22 and the third through hole 311 in the axial direction of the crankshaft 1, so as to ensure that the first pressure pulsation damping channel and the second pressure pulsation damping channel can form two axial flow channels parallel to the axial direction of the crankshaft 1, the first pressure pulsation damping passage is communicated with the air flow accommodating chamber 351 through a fourth through hole 341 provided in the first partition plate 34, the second pressure pulsation damping passage is communicated with the airflow receiving chamber 351 through a fifth through hole 342 formed in the first partition plate 34, that is, the first partition plate 34 closes the airflow receiving chamber 351 of the cover plate 35, the airflow receiving chamber 351 forms a flow direction turning part of the exhaust airflow, which can increase pressure loss of fluid by turning the flow direction of the airflow, further, the flow lengths of the first pressure pulsation damping passage and the second pressure pulsation damping passage can be shortened, and the pressure pulsation damping effect can be achieved (that is, the same damping effect can be achieved without an excessively long damping passage). It should be understood that the original exhaust port on the first flange 31 and the suction port on the first cylinder 32 need not be modified or modified.

The first and second pressure pulsation damping passages may have various passage cross-sectional shapes, such as a circular shape, a square shape, and an arc-shaped waist hole shape as shown in fig. 1 of the present application, which is not particularly limited.

Furthermore, a channel wall body of the first pressure pulsation attenuation channel is provided with a plurality of blind holes, and the perforation rate of the blind holes is 9% -11%; and/or the channel wall body of the second pressure pulsation attenuation channel is provided with a plurality of holes, and the perforation rate of the blind holes is 9% -11%, so that the pressure loss is further ensured, and the performance of the compression pump body assembly is not influenced by too large pressure loss. Specifically, the aperture of the blind hole is D, and D is more than or equal to 2mm and less than or equal to 10 mm; and/or the depth of the blind hole is h, wherein h is more than or equal to 2mm and less than or equal to 5 mm. The aforementioned perforation rate refers to a ratio of a total surface area of the openings of all the blind holes formed in the channel wall of the first pressure pulsation damping channel to a total surface area of the channel wall of the first pressure pulsation damping channel, and of course, has the same meaning as the aforementioned perforation rate corresponding to the second pressure pulsation damping channel, and is not described herein again.

Preferably, the total flow rate of the first pressure pulsation damping channel and the second pressure pulsation damping channel is Vz, the working volume of the first cylinder 32 is Vg, Vz/Vg is more than or equal to 0.5 and less than or equal to 1.5, and most preferably, Vz/Vg is more than or equal to 0.6 and less than or equal to 0.9, so as to achieve better silencing effect.

Further, the compression pump body assembly further comprises a second muffler 4, and the second pressure pulsation damping channel is communicated with the lower cavity of the motor through the second muffler 4, that is, the inner cavity of the second muffler 4 is communicated with the second pressure pulsation damping channel, and a discharge hole communicated with the lower cavity of the motor is formed in the second pressure pulsation damping channel. As shown in fig. 11, the second muffler 4 is used to perform a secondary muffling process on the exhaust gas that has passed through the first pressure pulsation damping passage and the second pressure pulsation damping passage, thereby further reducing the noise level. Of course, the second muffler 4 may also be designed as shown in fig. 12, and in particular, the exhaust gas of the first muffler 2 enters the first pressure pulsation damping channel via the second muffler 4, which is suitable for use in a compression pump assembly having a two-stage muffler structure.

Preferably, the first pressure pulsation damping channel and/or the second pressure pulsation damping channel are/is arranged close to the air suction port, so that heat exchange between air flow in the first pressure pulsation damping channel and/or the second pressure pulsation damping channel and air flow in the air suction port is realized, the temperature of the air flow in the compression pump body assembly can be increased, and the liquid impact problem caused by liquid carrying in the air suction under the low-frequency condition of the compressor is further improved.

Further, the compression pump body assembly further comprises a second partition plate 36 and a second cylinder 37, the first muffler 2, the first flange 31, the first cylinder 32, the second partition plate 36, the second cylinder 37, the second flange 33, the first partition plate 34 and the cover plate 35 are sequentially stacked along the axial direction of the crankshaft 1, the second cylinder 37 is provided with a second roller 100 and a second slide 101 corresponding to the second roller, the second roller 100, the second cylinder 37 and the second slide 101 form a second working chamber of the pump-block assembly, the first pressure pulsation damping passage penetrates the inner chamber of the first muffler 2 and the gas flow accommodating chamber 351, the compressed air flow formed by the first cylinder 32 and the second cylinder 37 can be discharged into the inner chamber of the first muffler 2, and enters the air flow accommodating chamber 351 through the first pressure pulsation damping passage and is discharged to the lower motor chamber of the compressor through the second pressure pulsation damping passage. The first cylinder 32 and the second cylinder 37 at this time form a compression structure having two cylinders, and the first pressure pulsation damping channel penetrates through the inner cavity of the first muffler 2, the first flange 31, the first cylinder 32, the second partition plate 36, the second cylinder 37, the second flange 33, the first partition plate 34, and the airflow accommodating chamber 351 in this order, similarly to a single-cylinder compression structure (when only the first cylinder 32 is provided); and/or the second pressure pulsation damping channel sequentially penetrates through the airflow accommodating cavity 351, the first partition plate 34, the second flange 33, the second cylinder 37, the second partition plate 36, the first cylinder 32, the first flange 31, the mounting skirt part of the first silencer 2 and the lower motor cavity.

At this moment, the utility model discloses an air current route among the compression pump body subassembly roughly can be divided into three, see fig. 5, the high-pressure exhaust in first cylinder 32, the second cylinder 37 gathers in the inner chamber of first muffler 2 via route (r), then enters via second through-hole 22 on the first flange 31 first pressure pulsation damping passageway (ii), arrives and gets into the air current by fourth through-hole 341 behind the first baffle 34 and hold chamber 351 and get into by fifth through-hole 342 second pressure pulsation damping passageway (iii) arrives first muffler 2 and locates to arrange to the motor cavity of resorption via first through-hole 21. Compared with the prior art, the double-cylinder (non-double-stage) compression pump body assembly as shown in fig. 6 has the advantages that the exhaust of the first cylinder and the exhaust of the second cylinder directly enter the lower cavity of the motor through the corresponding exhaust passages, the shortest passage tube pass is often selected based on the requirement of improving the performance of the compressor, and the length of the first pressure pulsation attenuation passage and the length of the second pressure pulsation attenuation passage almost penetrate through the whole axial thickness of the compression pump body assembly so as to increase the pressure loss through increasing the passage tube pass and further effectively reduce the pneumatic noise.

In order to verify the technical effect of the technical scheme of the utility model, the utility model people made corresponding contrast test design to it is shown as figure 7 to figure 9 to obtain the result, wherein prior art's technical scheme adopts the compression pump body subassembly shown in figure 6.

Fig. 7 is the adoption the utility model discloses a compression pump body subassembly of technical scheme structure (only adopt first muffler 2 and be equipped with first pressure pulsation decay passageway and second pressure pulsation decay passageway simultaneously) exhaust pressure pulsation frequency chart (select four positions to exhaust gas flow and detect), fig. 8 is the exhaust pressure pulsation frequency chart (select four positions to exhaust gas flow and detect) of the compression pump body subassembly of adopting prior art's technical scheme structure (as shown in fig. 6), can know from the figure, the first order pressure pulsation value of four measurement stations on the compressor motor epicoele of conventional scheme is up to 2355Pa, the second order pressure pulsation value is up to 275Pa, and adopt the technical scheme of the utility model, first order pressure pulsation value falls to 284Pa, the second order pressure pulsation value falls to 115Pa, from this visible adoption the utility model discloses scheme pressure pulsation is showing and is reduced. Fig. 9 is a noise contrast diagram adopting two structures, and from the overall noise distribution, the noise value of the scheme of the utility model is obviously lower than that of the conventional scheme, and the noise is averagely reduced by about 3 dB. Therefore compare with conventional scheme, the utility model discloses the scheme has obviously reduced the noise value.

According to the utility model discloses an embodiment still provides a compressor, including foretell compression pump body subassembly.

According to the utility model discloses an embodiment still provides an air conditioner, including foretell compressor.

It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.

The above description is only exemplary of the present invention and should not be construed as limiting the present invention, and any modifications, equivalents and improvements made within the spirit and principles of the present invention are intended to be included within the scope of the present invention. The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, a plurality of modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (13)

1. The utility model provides a compression pump body subassembly, its characterized in that includes bent axle (1), along first muffler (2), first flange (31), first cylinder (32), second flange (33), first baffle (34), apron (35) of axial suit in proper order of bent axle (1), the apron (35) are gone up and are had the air current and hold chamber (351), still include first pressure pulsation decay passageway, first pressure pulsation decay passageway link up first muffler (2) inner chamber with chamber (351) is held to the air current, the compressed air current that first cylinder (32) formed can discharge into the inner chamber of first muffler (2) and through discharge to the motor cavity that the compressor had behind the first pressure pulsation decay passageway.

2. The compression pump body assembly of claim 1, further comprising a second pressure pulsation dampening channel through which the air flow receiving cavity (351) communicates with the under-motor cavity.

3. The compression pump body assembly according to claim 2, wherein the first pressure pulsation damping channel passes through the inner cavity of the first muffler (2), the first flange (31), the first cylinder (32), the second flange (33), the first partition plate (34) in this order; and/or the second pressure pulsation attenuation channel sequentially penetrates through the airflow containing cavity (351), the first partition plate (34), the second flange (33), the first cylinder (32), the first flange (31), the mounting skirt part of the first silencer (2) and the lower motor cavity.

4. The compression pump body assembly of claim 2, wherein the passage wall of the first pressure pulsation dampening passage has a plurality of blind holes therein, the plurality of blind holes having a perforation rate of between 9% and 11%; and/or the channel wall body of the second pressure pulsation damping channel is provided with a plurality of holes, and the perforation rate of the blind holes is 9-11%.

5. The compression pump body assembly of claim 4, wherein the blind bore has a bore diameter D, 2mm ≦ D ≦ 10 mm; and/or the depth of the blind hole is h, wherein h is more than or equal to 2mm and less than or equal to 5 mm.

6. The compression pump block assembly of claim 2, wherein the first and second pressure pulsation damping passages have a total flow rate of Vz, and the first cylinder (32) has a swept volume of Vg, Vz/Vg being 0.5 ≦ 1.5.

7. The compression pump block assembly of claim 6, wherein Vz/Vg is 0.6 ≦ 0.9.

8. The compression pump body assembly according to claim 2, further comprising a second muffler (4), the second pressure pulsation damping channel communicating with the lower motor chamber through the second muffler (4).

9. The compression pump block assembly of claim 2, wherein the first cylinder (32) has an intake port, and the first and/or second pressure pulsation dampening channels are disposed adjacent the intake port.

10. The compression pump body assembly according to any one of claims 2 to 9, further comprising a second diaphragm (36), a second cylinder (37), the first silencer (2), the first flange (31), the first cylinder (32), the second partition plate (36), the second cylinder (37), the second flange (33), the first partition plate (34) and the cover plate (35) are sequentially stacked along the axial direction of the crankshaft (1), the first pressure pulsation damping passage penetrates an inner cavity of the first muffler (2) and the gas flow accommodating chamber (351), the compressed air flow formed by the first cylinder (32) and the second cylinder (37) can be discharged into the inner cavity of the first silencer (2) and enters the air flow accommodating cavity (351) through the first pressure pulsation damping channel and is discharged to the lower motor cavity of the compressor through the second pressure pulsation damping channel.

11. The compression pump block assembly according to claim 10, wherein the first pressure pulsation damping channel passes through an inner cavity of the first muffler (2), a first flange (31), a first cylinder (32), a second partition plate (36), a second cylinder (37), a second flange (33), a first partition plate (34), a gas flow accommodating chamber (351) in this order; and/or the second pressure pulsation attenuation channel sequentially penetrates through the airflow containing cavity (351), the first partition plate (34), the second flange (33), the second cylinder (37), the second partition plate (36), the first cylinder (32), the first flange (31), the mounting skirt part of the first silencer (2) and the lower motor cavity.

12. A compressor comprising a compression pump body assembly, characterized in that it is a compression pump body assembly according to any one of claims 1 to 11.

13. An air conditioner comprising a compressor, wherein said compressor is the compressor of claim 12.

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