CN106438374B

CN106438374B - Compressor and air conditioner with same

Info

Publication number: CN106438374B
Application number: CN201610974711.8A
Authority: CN
Inventors: 陈瑞祥; 杨欧翔
Original assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Current assignee: Gree Green Refrigeration Technology Center Co Ltd of Zhuhai
Priority date: 2016-11-04
Filing date: 2016-11-04
Publication date: 2020-08-11
Anticipated expiration: 2036-11-04
Also published as: CN106438374A

Abstract

The invention provides a compressor and an air conditioner with the same, wherein the compressor comprises: the shell is provided with an air supplementing port; the air cylinder comprises a first air cylinder body, a first air suction port and a first air exhaust port, wherein the first air cylinder body is arranged on the first air cylinder body; the second exhaust port is communicated with the first air suction port through the mixing cavity; and the first end of the air supplementing channel is communicated with the air supplementing port, and the second end of the air supplementing channel is communicated with the mixing cavity, wherein at least part of the air supplementing channel is formed in the first cylinder body so that the fluid in the air supplementing channel exchanges heat with the fluid in the working cavity of the first cylinder. The technical scheme of the invention solves the problems that the dryness of the refrigerant in the mixing cavity of the compressor in the prior art is low and the liquid impact phenomenon is easily caused to the high-pressure cylinder.

Description

Compressor and air conditioner with same

Technical Field

The invention relates to the technical field of refrigeration equipment, in particular to a compressor and an air conditioner with the same.

Background

In the air conditioner refrigeration compressor in the prior art, when the air conditioner is in a low-temperature heating operation condition, the heating quantity is often greatly attenuated and the heating effect is not good due to the increase of the high-low pressure ratio. In order to improve the heating capacity of the compressor operating under low temperature conditions, a refrigerant of medium pressure in the system is usually added to a proper position of a medium pressure cavity of the compression mechanism part to form a two-stage compression refrigeration cycle, so as to improve the heating effect under the low temperature heating conditions. The prior art compressor has the following problems:

when the intermediate pressure is higher, the liquid carrying capacity of the medium-pressure refrigerant in the system is larger, the dryness of the refrigerant in the intermediate cavity is reduced after mixing, liquid impact is easily caused to the high-pressure cylinder, and the service life of the compressor is reduced.

Disclosure of Invention

The invention mainly aims to provide a compressor and an air conditioner with the same, and aims to solve the problems that in the prior art, the dryness of a refrigerant in a mixing cavity of the compressor is low, and a liquid impact phenomenon is easily caused on a high-pressure cylinder.

In order to achieve the above object, according to one aspect of the present invention, there is provided a compressor including: the shell is provided with an air supplementing port; the air cylinder comprises a first air cylinder body, a first air suction port and a first air exhaust port, wherein the first air cylinder body is arranged on the first air cylinder body; the second exhaust port is communicated with the first air suction port through the mixing cavity; and the first end of the air supplementing channel is communicated with the air supplementing port, and the second end of the air supplementing channel is communicated with the mixing cavity, wherein at least part of the air supplementing channel is formed in the first cylinder body so that the fluid in the air supplementing channel exchanges heat with the fluid in the working cavity of the first cylinder.

Further, be provided with first hole section and the second hole section of intercommunication each other on the first cylinder body, first hole section extends to the surface of the lateral wall of first cylinder body and communicates with the tonifying qi mouth, and the second hole section extends to the terminal surface of first cylinder body and communicates with the hybrid chamber, and first hole section and second hole section form the tonifying qi passageway.

Further, first cylinder still includes the slide groove of setting on first cylinder body, and first hole section and second hole section setting deviate from the one side in slide groove at first exhaust port.

Further, the first bore section extends in a radial direction of the first cylinder block, and an angle formed by a center line of the first bore section and the first exhaust port in a circumferential direction of the first cylinder is in a range of 20 to 50 degrees.

Further, the centerline of the second bore section is parallel to the centerline of the first cylinder.

Further, the distance from the center line of the second bore section to the inner side wall of the first cylinder is in the range of 3 to 5 mm.

Further, the second hole section penetrates through two opposite end faces of the first cylinder body.

Further, be provided with first flange on the terminal surface that first cylinder body deviates from the second cylinder, first flange supports and seals the one end that the second hole section deviates from the second cylinder with first cylinder body.

Further, the compressor further includes: the partition plate is arranged on the end face, facing the second cylinder body, of the first cylinder body, and is provided with a first overflowing hole corresponding to the second hole section and a second overflowing hole corresponding to the first air suction port; a second flange arranged on the end surface of the second cylinder body facing the first cylinder body, a first accommodating groove arranged on the second flange and communicated with the second exhaust port,

wherein, baffle and second flange butt setting, baffle and first holding tank enclose into partial mixing chamber.

Further, a check valve is arranged at the first flow passage hole, and the check valve enables the first flow passage hole to flow in a single direction from the second hole section to the mixing cavity.

Further, the check valve includes: the valve plate is covered at the first overflow hole; the baffle is covered on the valve plate; and the valve plate and the baffle are fixed on the partition plate by the fixing columns.

Further, the compressor further includes: the second flange sets up on the terminal surface that deviates from first cylinder body of second cylinder body, is provided with the second holding tank on the second flange, and second holding tank and second gas vent intercommunication, apron, lid are established on the second flange, and wherein, the space that apron and second holding tank enclose communicates and forms the hybrid chamber jointly with the space that baffle and first holding tank enclose.

Further, the first overflowing hole is provided with a reducing section, and the overflowing area of the reducing section is gradually reduced in the direction from the second hole section to the mixing cavity.

Further, the first cylinder is a high-pressure cylinder, the second cylinder is a low-pressure cylinder, and the first cylinder is arranged above the second cylinder.

According to another aspect of the present invention, there is provided an air conditioner including a compressor, the compressor being the above-mentioned compressor.

By applying the technical scheme of the invention, when the refrigerant flows into the air supplementing channel, the temperature in the first air cylinder is transferred to the refrigerant in the air supplementing channel through the first cylinder body. The structure realizes the heating effect of the medium-pressure refrigerant, improves the dryness of the medium-pressure refrigerant, reduces the liquid carrying capacity and prevents the first cylinder from being subjected to liquid impact. Therefore, the technical scheme of the invention solves the problems that the dryness of the refrigerant in the mixing cavity of the compressor in the prior art is low and the liquid impact phenomenon is easily caused to the high-pressure cylinder.

Drawings

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

fig. 1 shows a schematic cross-sectional view of a first embodiment of a compressor according to the present invention;

FIG. 2 is an enlarged view of a portion of the first and second cylinders of the compressor of FIG. 1;

FIG. 3 shows a schematic top view of a first cylinder of the compressor of FIG. 1;

FIG. 4 is an enlarged view of a portion of the compressor of FIG. 1 at the charge air passage;

FIG. 5 shows a schematic view of the check valve of FIG. 4;

FIG. 6 is a schematic view illustrating an assembly of a check valve and a diaphragm of the compressor of FIG. 1;

FIG. 7 is an enlarged view of a portion of the gas supply passage of the second embodiment of the compressor according to the present invention; and

fig. 8 shows a schematic view of the check valve of fig. 7.

Wherein the figures include the following reference numerals:

10. a housing; 11. an air supplement port; 20. a first cylinder; 21. a first air intake port; 22. a first exhaust port; 23. a first cylinder; 231. a first bore section; 232. a second bore section; 24. a slide groove; 25. a first flange; 26. a partition plate; 261. a first overflow aperture; 2611. a diameter-changing section; 262. a second overflowing hole; 30. a second cylinder; 31. a second air suction port; 32. a second cylinder; 33. a second flange; 331. a first accommodating groove; 34. a second flange; 341. a second accommodating groove; 35. a cover plate; 40. a mixing chamber; 50. a gas supply channel; 60. a check valve; 61. a valve plate; 62. a baffle plate; 63. and (5) fixing the column.

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 embodiments with reference to the attached drawings.

When the existing air conditioner refrigeration compressor is in a low-temperature heating operation condition, the high-low pressure ratio is increased, so that the heating quantity is attenuated greatly and the heating effect is poor; in order to improve the heating capacity of the compressor operating under low temperature conditions, a refrigerant of medium pressure in the system is usually added to a proper position of a medium pressure cavity of the compression mechanism part to form a two-stage compression refrigeration cycle, so as to improve the heating effect under the low temperature heating conditions.

Generally, a medium-pressure air supplement pipe is arranged in the system, the medium-pressure air supplement pipe is connected to an air supplement channel arranged in the compressor, and the air supplement channel is connected to a medium-pressure cavity of the compressor. When the compressor is in operation, refrigerant from the medium pressure of the system enters the medium pressure cavity through the medium pressure air supplementing pipe; when the medium pressure of the system is higher than a certain critical value, the refrigerant from the medium pressure of the system flows into a medium pressure cavity of the compressor under the action of the pressure, so that a double-stage compression refrigeration cycle is formed, and the capacity and the efficiency of the system are improved. However, when the medium pressure in the system is lower than the critical value, the refrigerant in the medium-pressure air supplement pipe flows back, i.e. the refrigerant flows from the medium-pressure cavity to the medium pressure in the system, so that the capacity and the efficiency of the system are greatly reduced. In addition, when the intermediate pressure is higher, the liquid carrying capacity of the medium-pressure refrigerant in the system is larger, the dryness of the refrigerant in the intermediate cavity is reduced after mixing, liquid impact is easily caused to the high-pressure cylinder, and the service life of the compressor is reduced. In order to solve the above problem, the present application provides a compressor, which has the following specific structure:

the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the application, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.

The relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present application unless specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.

In the description of the present application, it is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are used for convenience of description and simplicity of description only, and in the case of not making a reverse description, these directional terms do not indicate and imply that the device or element being referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore, should not be considered as limiting the scope of the present application; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

It should be noted that the terms "first", "second", and the like are used to define the components, and are only used for convenience of distinguishing the corresponding components, and the terms have no special meanings unless otherwise stated, and therefore, the scope of protection of the present application is not to be construed as being limited.

As shown in fig. 1 and 2, the compressor of the present embodiment includes a housing 10, a first cylinder 20 and a second cylinder 30 disposed opposite to each other, a mixing chamber 40, and a gas supplementing passage 50. The casing 10 is provided with an air supply port 11, and the first cylinder 20 includes a first cylinder 23, and a first intake port 21 and a first exhaust port 22 provided in the first cylinder 23. The second cylinder 30 includes a second cylinder 32, and a second intake port 31 and a second exhaust port provided in the second cylinder 32. The second exhaust port communicates with the first intake port 21 through the mixing chamber 40. The first end of the air supply passage 50 is communicated with the air supply port 11, and the second end of the air supply passage 50 is communicated with the mixing chamber 40. At least a portion of the charge air passage 50 is formed in the first cylinder block 23 to exchange heat between the fluid in the charge air passage 50 and the fluid in the working chamber of the first cylinder block 20.

With the technical solution of the present embodiment, when the refrigerant flows into the gas make-up passage 50, the temperature in the first cylinder 20 is transferred to the refrigerant in the gas make-up passage 50 through the first cylinder 23. That is, the above structure realizes the heating effect of the medium-pressure refrigerant, improves the dryness of the medium-pressure refrigerant, reduces the liquid carrying amount, and prevents the first cylinder 20 from being hit by liquid. Therefore, the technical scheme of the embodiment solves the problems that the dryness of the refrigerant in the mixing cavity of the compressor in the prior art is low and the liquid impact phenomenon is easily caused to the high-pressure cylinder.

As shown in fig. 2, in the present embodiment, the refrigerant flows in the compression mechanism section in the following manner: the low-temperature and low-pressure refrigerant from the system evaporator enters the second suction port 31 through the liquid separator, and the sucked air is compressed by the second cylinder 30 to form low-pressure stage exhaust gas and is discharged into the mixing chamber 40. Air supplement from the medium pressure of the system enters the mixing cavity 40 through the air supplement channel 50, the medium pressure air supplement is mixed with the exhaust gas of the second air cylinder 30, the well first air suction port 21 enters the first air cylinder 20, and the first air cylinder 20 compresses the refrigerant to form high-pressure stage exhaust gas and discharges the high-pressure stage exhaust gas out of the compressor.

As shown in fig. 2, in the solution of the present embodiment, the first cylinder 23 is provided with a first hole section 231 and a second hole section 232 which are communicated with each other. The first hole section 231 extends to the surface of the outer side wall of the first cylinder 23 and communicates with the air supplement port 11, and the second hole section 232 extends to the end surface of the first cylinder 23 and communicates with the mixing chamber 40. The first hole section 231 and the second hole section 232 form the gas replenishing passage 50. Specifically, the system medium pressure air supplement enters into the first cylinder 23 through the outer side wall of the first cylinder 23, and the mixing chamber 40 is arranged at the end face of the first cylinder 23. The first and

second orifice segments

231, 232 may be in a smooth or right angle transition, and the first and

second orifice segments

231, 232 deflect the flow path of the system medium pressure make-up air and cause the system medium pressure make-up air to flow from the side wall of the first cylinder 23 to the end wall of the first cylinder 23.

As shown in fig. 3, in the solution of the present embodiment, the first cylinder 20 further includes a slide groove 24 disposed on the first cylinder block 23, and the first hole section 231 and the second hole section 232 are disposed on a side of the first exhaust port 22 facing away from the slide groove 24. In the technical solution of this embodiment, in order to improve the heat exchange efficiency between the first cylinder 23 and the medium-pressure refrigerant, a certain size requirement is required to be satisfied between the first hole section 231 and the second hole section 232 and between the first exhaust port 22 and the first cylinder 23, which is specifically as follows:

specifically, the first exhaust port 22 of the first cylinder 23 is at an angle a to the first bore section 231 and the second bore section 232. This angle determines the position at which the air supplement passage 50 is placed in the circumferential direction of the first cylinder 23. When the air supply channel 50 is placed close to the side of the suction compression cavity, because the first cylinder 20 does not start to compress, the temperature of the air supply channel is close to that of the low-pressure stage exhaust, the temperature difference with the medium-pressure air supply is small, the heat exchange quantity is small, and the influence on the dryness of the high-pressure stage suction air is small. When the amount of the air supply belt is large, the valve plate is easy to be impacted, the service life of the valve plate is shortened, and the first cylinder 20 is impacted by liquid impact, so that the performance of the whole machine is influenced. When the air supply channel 50 is arranged at the side close to the exhaust compression cavity, the heat exchange amount is large because the temperature inside the exhaust compression cavity is high and the temperature difference with the medium-pressure air supply is large. The high-temperature heating medium-pressure refrigerant passing through the compression cavity of the first cylinder 20 improves the dryness of the refrigerant, reduces the liquid carrying amount, prevents the air supply check device from causing liquid impact, and simultaneously can improve the dryness of high-pressure suction to prevent the first cylinder 20 from causing liquid impact. Therefore, the charge air passage 50 should be placed close to the discharge compression chamber in the following specific positional relationship.

Preferably, the first bore section 231 extends in a radial direction of the first cylinder block 23, and an angle formed by a center line of the first bore section 231 and the first exhaust port 22 in a circumferential direction of the first cylinder 20 is in a range of 20 to 50 degrees. The above-described configuration of the first bore section 231 facilitates machining on the one hand and calculation and determination of the angle a on the other hand.

In addition, in order to ensure that the heat exchange amount between the first cylinder 20 and the air supply passage 50 is large enough, the distance dimension B between the air supply passage 50 and the inner circle of the first cylinder 23 should be within a reasonable range. The larger the dimension B, the smaller the heat exchange amount, and too small results in deterioration of the roundness of the inner circle of the first cylinder 23 and stress, which affects reliability.

Therefore, it is preferable that the center line of the second bore section 232 is parallel to the center line of the first cylinder 23. The distance from the center line of the second orifice section 232 to the inner side wall of the first cylinder 23 is in the range of 3 to 5 mm. The above-described structure facilitates, on the one hand, the machining of the second bore section 232 and, on the other hand, the calculation and determination of the dimension B.

As shown in fig. 2, in the solution of the present embodiment, the second hole section 232 penetrates through two opposite end surfaces of the first cylinder block 23. Specifically, the above-described structure facilitates the machining of the second bore section 232. In the actual process, the second hole section 232 penetrates through two opposite end faces of the first cylinder 23, and then the first hole section 231 is drilled, so that the air supplement channel 50 can be processed as long as the first hole section 231 is communicated with the second hole section 232.

Preferably, a first flange 25 is arranged on an end surface of the first cylinder block 23 facing away from the second cylinder 30, and the first flange 25 abuts against the first cylinder block 23 and seals an end of the second hole section 232 facing away from the second cylinder 30. The first flange 25 closes the upper end of the second bore section 232 and allows the pressurized system air to flow only down the second bore section 232.

As shown in fig. 2, in the solution of the present embodiment, the compressor further comprises a partition 26 and a second flange 33. Specifically, the partition plate 26 is provided on an end surface of the first cylinder 23 facing the second cylinder 32, and the partition plate 26 is provided with a first overflowing hole 261 corresponding to the second hole section 232 and a second overflowing hole 262 corresponding to the first suction port 21. The second flange 33 is provided on an end surface of the second cylinder 32 facing the first cylinder 23, the second flange 33 is provided with a first receiving groove 331, and the first receiving groove 331 communicates with the second exhaust port. The partition 26 is disposed in abutment with the second flange 33, and the partition 26 and the first receiving groove 331 define a portion of the mixing chamber 40. The partition 26 abuts against the lower end face of the first cylinder 23, and the first overflowing hole 261 is aligned with the second hole section 232. The second flange 33 abuts against the partition 26, and a first receiving chamber is enclosed between the second flange 33 and the partition 26, said receiving chamber forming part of the mixing chamber 40. Specifically, after the second cylinder 30 exhausts, the compressed refrigerant is exhausted into the first accommodating cavity through the second exhaust port. The system medium-pressure supplement gas enters the first accommodating cavity through the supplement gas channel 50 and the first overflowing hole 261, and the compressed refrigerant and the system medium-pressure exhaust gas are mixed in the first accommodating cavity, enter the first air inlet 21 from the second overflowing hole 262 and are further compressed.

As shown in fig. 4 and 5, in the solution of the present embodiment, a check valve 60 is disposed at the first overflowing hole 261, and the check valve 60 makes the first overflowing hole 261 flow in one direction in a direction from the second hole section 232 to the mixing chamber 40. The check valve 60 allows the medium-pressure refrigerant in the system to flow only from the charge air passage 50 to the mixing chamber 40, and prevents the medium-pressure refrigerant in the system from flowing backward, thereby preventing the compression efficiency of the compressor from being lowered.

As shown in fig. 6, the check valve 60 includes a valve sheet 61, a flapper 62, and a fixing post 63. The valve sheet 61 is covered at the first overflowing hole 261. The baffle plate 62 covers the valve sheet 61. The fixing posts 63 fix the valve sheet 61 and the baffle 62 to the partition 26. Specifically, the fixing posts 63 nail the valve sheet 61 and the baffle plate 62 to the partition plate 26. The fixing posts 63 may be rivets or screws.

As shown in fig. 2, in the solution of the present embodiment, the compressor further includes a second flange 34 and a cover plate 35. The second flange 34 is disposed on an end surface of the second cylinder 32 facing away from the first cylinder 23, the second flange 34 is provided with a second receiving groove 341, and the second receiving groove 341 is communicated with the second exhaust port. The cover plate 35 is covered on the second flange 34, and the space enclosed by the cover plate 35 and the second receiving groove 341 and the space enclosed by the partition plate 26 and the first receiving groove 331 are communicated to form the mixing chamber 40. Specifically, the second flange 34 abuts against a lower end surface of the second cylinder 32, and when the cover plate 35 is covered on the second flange 34, a second accommodating chamber is defined between the second flange 34 and the cover plate 35. As can be seen from fig. 2, the first receiving chamber and the second receiving chamber are respectively located on both sides of the second cylinder 32, and are communicated through a passage (not shown) provided in the second cylinder 32, and the first receiving chamber and the second receiving chamber together form the above-mentioned mixing chamber 40.

In the technical solution of the present embodiment, the first cylinder 20 is a high pressure cylinder, the second cylinder 30 is a low pressure cylinder, and the first cylinder 20 is disposed above the second cylinder 30. The two-stage compressor of the present embodiment. Of course, the high-pressure cylinder and the low-pressure cylinder may be plural.

As shown in fig. 7 and 8, the second embodiment of the compressor according to the present application is different from the first embodiment in that the first overflowing hole 261 has a diameter-varying section 2611, and an overflowing area of the diameter-varying section 2611 is gradually reduced in a direction from the second hole section 232 to the mixing chamber 40. As shown in fig. 7 and 8, the difference between the second embodiment and the first embodiment is that the first overflowing hole 261 is provided with a variable cross-section flow port, so that the dynamic pressure of the make-up gas refrigerant gas can be increased by the variable cross-section effect, the pressure difference between the two sides required by the valve plate 61 to open is reduced, and the flow resistance of the check valve 60 is reduced. Meanwhile, the valve plate 61 and the baffle plate 62 of the check valve 60 can also be smaller, which is beneficial to the miniaturization of the compressor.

The application also provides an air conditioner, wherein the air conditioner comprises a compressor, and the compressor is the compressor.

The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by 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 compressor, comprising:

the air supply device comprises a shell (10), wherein an air supply port (11) is formed in the shell (10);

the air cylinder comprises a first air cylinder (20) and a second air cylinder (30) which are oppositely arranged, wherein the first air cylinder (20) comprises a first cylinder body (23), a first air suction port (21) and a first air exhaust port (22) which are arranged on the first cylinder body (23), and the second air cylinder (30) comprises a second cylinder body (32), a second air suction port (31) and a second air exhaust port which are arranged on the second cylinder body (32);

a mixing chamber (40), the second exhaust port communicating with the first intake port (21) through the mixing chamber (40);

an air supplement channel (50), a first end of the air supplement channel (50) is communicated with the air supplement port (11), a second end of the air supplement channel (50) is communicated with the mixing cavity (40), wherein at least part of the air supplement channel (50) is formed in the first cylinder body (23) so that fluid in the air supplement channel (50) exchanges heat with fluid in a working cavity of the first cylinder (20);

a first hole section (231) and a second hole section (232) which are communicated with each other are arranged on the first cylinder body (23), the first hole section (231) extends to the surface of the outer side wall of the first cylinder body (23) and is communicated with the air replenishing port (11), the second hole section (232) extends to the end face of the first cylinder body (23) and is communicated with the mixing cavity (40), and the first hole section (231) and the second hole section (232) form the air replenishing channel (50);

the first bore section (231) extends in a radial direction of the first cylinder block (23), and an angle formed by a center line of the first bore section (231) and the first exhaust port (22) in a circumferential direction of the first cylinder (20) is in a range of 20 to 50 degrees.

2. Compressor according to claim 1, characterized in that the first cylinder (20) further comprises a slide groove (24) provided on the first cylinder block (23), the first bore section (231) and the second bore section (232) being provided on a side of the first exhaust port (22) facing away from the slide groove (24).

3. The compressor of any one of claims 1 to 2, wherein a centerline of the second bore section (232) is parallel to a centerline of the first cylinder block (23).

4. The compressor of claim 3, wherein a distance from a centerline of the second bore section (232) to an inner side wall of the first cylinder block (23) is in a range of 3 to 5 millimeters.

5. A compressor according to claim 3, wherein the second bore section (232) passes through opposite end faces of the first cylinder block (23).

6. Compressor according to claim 5, characterized in that a first flange (25) is arranged on the end surface of the first cylinder block (23) facing away from the second cylinder (30), the first flange (25) abutting against the first cylinder block (23) and closing the end of the second bore section (232) facing away from the second cylinder (30).

7. The compressor of claim 1, further comprising:

a partition plate (26) which is provided on an end surface of the first cylinder (23) facing the second cylinder (32), the partition plate (26) being provided with a first overflowing hole (261) corresponding to the second hole section (232) and a second overflowing hole (262) corresponding to the first intake port (21);

a second flange (33) provided on an end surface of the second cylinder (32) facing the first cylinder (23), the second flange (33) being provided with a first accommodation groove (331), the first accommodation groove (331) being communicated with the second exhaust port,

wherein the partition (26) and the second flange (33) are arranged in an abutting manner, and the partition (26) and the first accommodating groove (331) enclose a part of the mixing cavity (40).

8. Compressor according to claim 7, characterized in that a check valve (60) is arranged at the first flow-through hole (261), the check valve (60) providing a one-way flow through the first flow-through hole (261) in the direction from the second hole section (232) to the mixing chamber (40).

9. The compressor of claim 8, wherein the check valve (60) comprises:

the valve plate (61) is covered at the first overflowing hole (261);

the baffle (62) is covered on the valve plate (61);

the fixing columns (63) fix the valve plate (61) and the baffle (62) on the partition plate (26) through the fixing columns (63).

10. The compressor of claim 7, further comprising:

a second flange (34) disposed on an end surface of the second cylinder (32) facing away from the first cylinder (23), the second flange (34) having a second receiving groove (341) disposed thereon, the second receiving groove (341) communicating with the second exhaust port,

a cover plate (35) covering the second flange (34),

wherein, the space enclosed by the cover plate (35) and the second receiving groove (341) and the space enclosed by the clapboard (26) and the first receiving groove (331) are communicated and jointly form the mixing cavity (40).

11. The compressor as claimed in claim 7, wherein the first overflowing hole (261) has a reducing section (2611), and an overflowing area of the reducing section (2611) is gradually reduced in a direction from the second hole section (232) to the mixing chamber (40).

12. Compressor according to claim 1, characterized in that said first cylinder (20) is a high-pressure cylinder and said second cylinder (30) is a low-pressure cylinder, said first cylinder (20) being arranged above said second cylinder (30).

13. An air conditioner comprising a compressor, wherein the compressor is as claimed in any one of claims 1 to 12.