CN106765749A

CN106765749A - Air conditioner

Info

Publication number: CN106765749A
Application number: CN201611078879.7A
Authority: CN
Inventors: 梁祥飞; 郑波; 黄柏良; 潘俊; 庄嵘
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2016-11-29
Filing date: 2016-11-29
Publication date: 2017-05-31

Abstract

The invention provides an air conditioner, which comprises a compressor, a first heat exchanger, an air supply supercooling device, a second heat exchanger and a gas-liquid separator which are communicated. Wherein, the compressor includes pump body structure, and pump body structure includes a plurality of cylinders, and at least one in a plurality of cylinders includes main working chamber, and is a plurality of at least one in the cylinder includes supplementary working chamber, and main working chamber and supplementary working chamber all have induction port and gas vent. The air suction port of the auxiliary working cavity is selectively communicated with the gas-liquid separator or the air supply supercooling device, and the air exhaust port of the auxiliary working cavity is selectively communicated with the first heat exchanger or the air supply supercooling device. The arrangement enables the exhaust port of the auxiliary working cavity to be selectively communicated with the air suction port or the exhaust port of one of the air cylinders according to the specific operation working condition of the air conditioner, so that the seasonal performance coefficient of the air conditioner during operation is effectively improved, and the heating capacity of the air conditioner is improved.

Description

Air conditioner

Technical Field

The invention relates to the technical field of air conditioner equipment, in particular to an air conditioner.

Background

In the prior art, the heating capacity of an air source heat pump is rapidly attenuated along with the reduction of the outdoor environment temperature, so that the heating coefficient of performance (COP) of the air source heat pump is correspondingly attenuated, the heating comfort and the operation economy of a heat pump type air conditioner are reduced along with the reduction of the environment temperature, even the situation that the heating comfort cannot meet the requirement of a user and auxiliary electric heating needs to be started can occur, the COP of the air source heat pump at the moment is greatly reduced, namely the problem that the air conditioner in the prior art has poor heating capacity. The existing low-temperature air source heat pump product adopts a quasi-second-stage or double-stage compression air-supply enthalpy-increasing technology to improve the heating capacity, and although COP is improved to a certain extent, the position of a quasi-second-stage air-supply opening or the volume ratio of a double-stage compression high-low pressure stage is fixed during design. Therefore, the existing air-supply enthalpy-increasing technology only obtains better COP under the design working condition, and the low-temperature air source heat pump has a wider operating temperature range, so that the COP of the air source heat pump can not achieve the best effect when the air source heat pump operates under the full working condition.

In the prior art, because the volume ratio of the second cylinder to the first cylinder is a fixed value, the problem that the optimal effect of the heating COP is difficult to achieve when the heating COP deviates from the design working condition also exists. And there is still a sliding friction loss between the rollers and the upper and lower flanges and cylinder walls when the second cylinder is in the non-compression mode, resulting in a reduction in compressor efficiency compared to a single stage compressor. In addition, the variable capacitance control structure in the prior art is complex, and the stability and reliability of the air conditioner system are reduced. The compressor in the prior art also has the problems that the air conditioner is easy to generate reliability due to uneven distribution of lubricating oil, and has the defects of high manufacturing cost, large occupied space and the like.

Disclosure of Invention

The invention mainly aims to provide an air conditioner, which comprises a compressor, a first heat exchanger, an air supplementing and supercooling device, a second heat exchanger and a gas-liquid separator, wherein the compressor, the first heat exchanger, the air supplementing and supercooling device, the second heat exchanger and the gas-liquid separator are communicated; the compressor comprises a pump body structure, the pump body structure comprises a plurality of cylinders, at least one of the cylinders comprises a main working cavity, at least one of the cylinders comprises an auxiliary working cavity, and the main working cavity and the auxiliary working cavity are both provided with an air suction port and an air exhaust port; the air suction port of the auxiliary working cavity is selectively communicated with the gas-liquid separator or the air supply supercooling device, and the air exhaust port of the auxiliary working cavity is selectively communicated with the first heat exchanger or the air supply supercooling device.

Furthermore, a first valve is arranged on a pipeline for communicating the exhaust port of the auxiliary working cavity with the air supply supercooling device.

Furthermore, a second valve is arranged on a pipeline for communicating the air suction port of the auxiliary working cavity with the air supply supercooling device.

Furthermore, a third valve is arranged on a pipeline for communicating the exhaust port of the auxiliary working cavity with the first heat exchanger.

Furthermore, a fourth valve is arranged on a pipeline for communicating an air suction port of the auxiliary working cavity with the gas-liquid separator.

Further, the plurality of cylinders includes: the first cylinder comprises a first sliding sheet and a second sliding sheet, the first sliding sheet and the second sliding sheet divide an inner cavity of the first cylinder into a first working cavity and a second working cavity, and the second working cavity forms an auxiliary working cavity.

Furthermore, the first working chamber is provided with a first air suction port and a first air exhaust port, the first air suction port is communicated with the air supply supercooling device, the first air exhaust port is communicated with the first heat exchanger, the second working chamber is provided with a second air suction port and a second air exhaust port, the second air exhaust port is communicated with the first heat exchanger or the first air suction port, and the second air suction port is selectively communicated with the air supply supercooling device or the gas-liquid separator.

Further, the plurality of cylinders further includes: and the second cylinder is positioned below the first cylinder and is provided with a third working cavity, the third working cavity is provided with a third air suction port and a third air exhaust port, the third air suction port is communicated with the gas-liquid separator, the third air exhaust port is communicated with the first air suction port, and the third working cavity is a main working cavity.

Further, a plurality of cylinders set up along vertical direction, and each cylinder all has a working chamber, and the working chamber is main working chamber or for supplementary working chamber.

Furthermore, the multiple cylinders comprise a third cylinder and a fourth cylinder, the third cylinder is provided with a fourth working cavity, the fourth working cavity is provided with a fourth air suction port and a fourth air exhaust port, the fourth cylinder is provided with a fifth working cavity, the fifth working cavity is provided with a fifth air suction port and a fifth air exhaust port, the fourth air suction port is communicated with the second heat exchanger, the fourth air exhaust port is communicated with the fifth air suction port, the fifth air exhaust port is communicated with the first heat exchanger, and the fourth working cavity is a main working cavity.

Furthermore, the multiple cylinders further comprise a fifth cylinder, the fifth cylinder is provided with a sixth working cavity, the sixth working cavity is provided with a sixth air suction port and a sixth air exhaust port, the sixth air suction port is selectively communicated with the second heat exchanger or the air supply supercooling device, the sixth air exhaust port is selectively communicated with the fifth air suction port or the first heat exchanger, and the sixth working cavity is an auxiliary working cavity.

Further, the air make-up subcooling device comprises: and a liquid inlet pipeline of the flash tank is communicated with the outlet end of the first heat exchanger, a liquid outlet pipeline of the flash tank is communicated with the inlet end of the second heat exchanger, and an air outlet of the flash tank is communicated with an air suction port of the auxiliary working cavity.

Furthermore, a sixth valve is arranged on a pipeline for communicating the air outlet of the flash tank with the air suction port of the auxiliary working cavity.

Furthermore, the inlet end of the air supply supercooling device is communicated with the outlet end of the first heat exchanger, the outlet end of the air supply supercooling device is communicated with the inlet end of the second heat exchanger, the air supply supercooling device further comprises an auxiliary path, one end of the auxiliary path is communicated with the outlet end of the first heat exchanger, the other end of the auxiliary path is communicated with an air suction port of the auxiliary working cavity, and a throttling device is arranged on the auxiliary path.

Furthermore, the volume ratio of the second working chamber to the third working chamber is Q1, wherein Q1 is more than or equal to 0.1 and less than or equal to 0.4.

Furthermore, the volume ratio of the first working chamber to the third working chamber is Q2, wherein Q2 is more than or equal to 0.6 and less than or equal to 0.75.

Furthermore, the volume ratio of the sixth working chamber to the fourth working chamber is Q3, wherein Q3 is more than or equal to 0.1 and less than or equal to 0.4.

Furthermore, the volume ratio of the fifth working chamber to the fourth working chamber is Q4, wherein Q4 is more than or equal to 0.6 and less than or equal to 0.75.

Further, the exhaust port of the auxiliary working chamber is selectively communicated with the first heat exchanger or the air supply supercooling device outside the shell of the compressor.

By applying the technical scheme of the invention, the air conditioner comprises a compressor, a first heat exchanger, an air supply supercooling device, a second heat exchanger and a gas-liquid separator which are communicated. The compressor comprises a pump body structure, the pump body structure comprises a plurality of cylinders, at least one of the cylinders comprises a main working cavity, at least one of the cylinders comprises an auxiliary working cavity, and the main working cavity and the auxiliary working cavity are provided with an air suction port and an air exhaust port. The air suction port of the auxiliary working cavity is selectively communicated with the gas-liquid separator or the air supply supercooling device, and the air exhaust port of the auxiliary working cavity is selectively communicated with the first heat exchanger or the air supply supercooling device. The arrangement enables the air suction port of the auxiliary working cavity to be selectively communicated with the gas-liquid separator or the air supply supercooling device according to the specific operation working condition of the air conditioner, and the air exhaust port of the auxiliary working cavity to be selectively communicated with the first heat exchanger or the air supply supercooling device, so that the seasonal performance coefficient of the air conditioner during operation is effectively improved, and the heating capacity of the air conditioner is improved.

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 is a schematic view illustrating a first type of compressor cylinder of an air conditioner according to the present invention;

fig. 2 is a schematic view illustrating a second type of compressor cylinder of an air conditioner according to the present invention;

fig. 3 is a schematic view illustrating a structure of a third compressor cylinder of an air conditioner according to the present invention;

fig. 4 is a schematic configuration diagram illustrating a first control system of an air conditioner according to the present invention;

fig. 5 is a schematic structural view illustrating a second control system of an air conditioner according to the present invention;

fig. 6 is a schematic view illustrating a first compressor cylinder connection structure of an air conditioner according to the present invention;

fig. 7 is a schematic view illustrating a second compressor cylinder connection structure of an air conditioner according to the present invention;

fig. 8 is a schematic view illustrating a third compressor cylinder connection structure of an air conditioner according to the present invention;

fig. 9 is a schematic view illustrating a fourth compressor cylinder connection structure of an air conditioner according to the present invention; and

fig. 10 is a schematic view illustrating a fifth compressor cylinder connection structure of an air conditioner according to the present invention.

Wherein the figures include the following reference numerals:

10. a compressor; 11. a first cylinder; 12. a first slip sheet; 13. a second slip sheet; 14. a second cylinder; 15. a third cylinder; 16. a fourth cylinder; 17. a fifth cylinder; 20. a first heat exchanger; 30. a gas supplementing and supercooling device; 31. a road is assisted; 32. a flash tank; 40. a second heat exchanger; 50. a pipeline; 51. a main road; 52. a branch circuit; 53. a branch circuit; 531. a branch circuit; 532. a branch circuit; 54. a branch circuit; 55. a branch circuit; 60. a gas-liquid separator; 71. a first valve; 72. a second valve; 73. a third valve; 74. a fourth valve; 75. a throttling device; 76. a sixth valve; 77. a throttling device; 78. a throttling device.

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.

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.

It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the terms so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.

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.

Exemplary embodiments according to the present application will now be described in more detail with reference to the accompanying drawings. These exemplary embodiments may, however, be embodied in many different forms and should not be construed as limited to only the embodiments set forth herein. It is to be understood that these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art, in the drawings, it is possible to enlarge the thicknesses of layers and regions for clarity, and the same devices are denoted by the same reference numerals, and thus the description thereof will be omitted.

Referring to fig. 1 to 10, according to an embodiment of the present invention, an air conditioner is provided.

Specifically, the air conditioner comprises a compressor 10, a first heat exchanger 20, an air supply supercooling device 30, a second heat exchanger 40 and a gas-liquid separator 60 which are communicated with each other. The compressor 10 includes a pump structure, the pump structure includes a plurality of cylinders, at least one of the cylinders includes a main working chamber, at least one of the cylinders includes an auxiliary working chamber, and the main working chamber and the auxiliary working chamber both have an air suction port and an air discharge port. The air inlet of the auxiliary working cavity is selectively communicated with the gas-liquid separator 60 or the air supply supercooling device 30, and the air outlet of the auxiliary working cavity is selectively communicated with the first heat exchanger 20 or the air supply supercooling device 30.

In the embodiment, the arrangement enables the air suction port of the auxiliary working cavity to be selectively communicated with the gas-liquid separator or the air supply supercooling device according to the specific operation condition of the air conditioner, and the air exhaust port of the auxiliary working cavity to be selectively communicated with the first heat exchanger or the air supply supercooling device, so that the seasonal performance coefficient of the air conditioner during operation is effectively improved, and the heating capacity of the air conditioner is improved.

In order to further realize that the air outlet and the air inlet of the auxiliary working chamber can be switched or selected, a first valve 71 is respectively arranged on a pipeline for communicating the air outlet of the auxiliary working chamber and the air supply supercooling device 30. A second valve 72 is provided in a line connecting the suction port of the auxiliary working chamber and the subcooling device 30. A third valve 73 is provided in a line connecting the exhaust port of the auxiliary working chamber and the first heat exchanger 20. A fourth valve 74 is provided in a conduit connecting the suction port of the auxiliary working chamber and the gas-liquid separator 60. The setting makes can be according to the specific operating condition control valve on the corresponding pipeline of compressor in order to change the intercommunication mode of the induction port and the gas vent of compressor, has improved the compression performance of compressor effectively. Preferably, the discharge port of the auxiliary working chamber is selectively communicated with the first heat exchanger 20 or the supplementary air supercooling means 30 outside the shell of the compressor 10.

The plurality of cylinders includes a first cylinder 11. A plurality of working chambers (shown as a and B in fig. 1) are formed in the first cylinder 11, and each working chamber has an intake port (shown as an intake port 121 and an intake port 131 in fig. 1, and a roller 132 is provided in the cylinder) and an exhaust port (not shown). The structure of the air cylinder can be effectively simplified and the reliability of the operation of the compressor is improved.

Wherein, the pump body structure of the compressor includes a first cylinder 11. The first cylinder 11 comprises a first sliding piece 12 and a second sliding piece 13, the first sliding piece 12 and the second sliding piece 13 divide an inner cavity of the first cylinder 11 into a first working cavity and a second working cavity, and the second working cavity forms an auxiliary working cavity. The first working chamber is provided with a first air suction port and a first air exhaust port, the first air suction port is communicated with the air supply supercooling device 30, the first air exhaust port is communicated with the first heat exchanger 20, the second working chamber is provided with a second air suction port and a second air exhaust port, the second air exhaust port is selectively communicated with the first heat exchanger 20 or the first air suction port, and the second air suction port is selectively communicated with the air supply supercooling device 30 or the gas-liquid separator 60. The arrangement enables the air suction port of the auxiliary working cavity to be selectively communicated with the gas-liquid separator or the air supply supercooling device according to the specific operation working condition of the air conditioner, and the air exhaust port of the auxiliary working cavity to be selectively communicated with the first heat exchanger or the air supply supercooling device, so that the seasonal performance coefficient of the air conditioner during operation is effectively improved, and the heating capacity of the air conditioner is improved.

The plurality of cylinders also includes a second cylinder 14. The second cylinder 14 is located below the first cylinder 11, the second cylinder 14 has a third working chamber, the third working chamber has a third air suction port and a third air discharge port, the third air suction port is communicated with the gas-liquid separator 60, the third air discharge port is communicated with the first air suction port, and the third working chamber is a main working chamber. The arrangement enables the second cylinder 14 to be in a normal compression state when the first cylinder 11 is in the normal compression state, and effectively solves the problems that in the prior art, when one of the cylinders is overlapped by a plurality of cylinders and compressed normally, other cylinders cannot realize the normal compression mode, so that the compression friction loss is caused, and the heating capacity of the compressor and the air conditioner is reduced.

As shown in fig. 3, the pump body structure in this embodiment may also be configured to: a plurality of cylinders set up along vertical direction, and each cylinder all has a working chamber, and the working chamber is main working chamber or is supplementary working chamber. The arrangement can also play a role in improving the heating capacity of the compressor, and the practicability and the reliability of the compressor are improved.

The plurality of cylinders includes a third cylinder, a fourth cylinder, and a fifth cylinder. The third cylinder has a fourth working chamber having a fourth suction port and a fourth exhaust port, the fourth cylinder has a fifth working chamber having a fifth suction port and a fifth exhaust port, the fourth suction port is communicated with the second heat exchanger 40, the fourth exhaust port is communicated with the fifth suction port, and the fifth exhaust port is communicated with the first heat exchanger 20. The fifth cylinder is provided with a sixth working cavity, the sixth working cavity is provided with a sixth air suction port and a sixth air exhaust port, the sixth air suction port is selectively communicated with the second heat exchanger 40 or the air supply supercooling device 30, the sixth air exhaust port is selectively communicated with the fifth air suction port or the first heat exchanger 20, the fourth working cavity is a main working cavity, and the sixth working cavity is an auxiliary working cavity.

The subcooling device 30 includes a flash tank 32. The liquid inlet pipeline of the flash evaporator 32 is communicated with the outlet end of the first heat exchanger 20, the liquid outlet pipeline of the flash evaporator 32 is communicated with the inlet end of the second heat exchanger 40, and the air outlet of the flash evaporator 32 is communicated with the air suction port of the auxiliary working cavity. The arrangement can also increase the compression performance of the compressor and improve the working efficiency of the air conditioner.

Furthermore, in order to further control the refrigerant flow rate in the branch of the pipeline 50, a sixth valve 76 is provided in a pipeline connecting the outlet of the flash tank 32 and the suction port of the auxiliary working chamber.

The inlet end of the air supply supercooling device 30 is communicated with the outlet end of the first heat exchanger 20, the outlet end of the air supply supercooling device 30 is communicated with the inlet end of the second heat exchanger 40, the air supply supercooling device 30 further comprises an auxiliary path 31, one end of the auxiliary path 31 is communicated with the outlet end of the first heat exchanger 20, the other end of the auxiliary path 31 is communicated with an air suction port of the auxiliary working cavity, and a throttling device 75 is arranged on the auxiliary path 31. In order to improve the air supply effect of the compressor, the auxiliary path 31 is provided with a throttling device 75, so that the flow of the refrigerant in the pipeline 50 can be effectively controlled, and the heating efficiency of the compressor is improved.

The pump body structure comprises a silencing cavity. The second exhaust port is communicated with the first exhaust port and the inlet of the muffling chamber, and the outlet of the muffling chamber is communicated with the first heat exchanger 20. The refrigerant discharged from the second exhaust port and the first exhaust port is converged at the inlet of the silencing cavity and is discharged into the first heat exchanger 20 through the outlet of the silencing cavity, so that the exhaust noise of the compressor can be effectively reduced, the noise pollution during the operation of the compressor is increased, and the comfort of the air conditioner is effectively improved.

Wherein the pipeline 50 comprises a main path 51 and a branch path 52. A first end of the main path 51 is communicated with the air outlet of the air make-up subcooling device 30. One end of the branch passage 52 communicates with the second end of the main passage 51, and the second end of the branch passage 52 communicates with the second suction port. The air supply can be carried out through the second air suction port by the aid of the pump body structure due to the arrangement, the exhaust temperature of the compressor is effectively reduced, and the heating capacity and COP of the air conditioner in the whole operation working condition are increased.

The conduit 50 also includes a branch 53. One end of the branch 53 communicates with the second end of the main path 51, and the second end of the branch 53 communicates with the second exhaust port. The trend of refrigerant in the control line 50 can be effectively controlled in setting like this, has realized that the air conditioner can carry out tonifying qi or tonifying qi adjustment according to the operating condition of difference, has avoided the compressor in the air conditioner to have tonifying qi mixing loss and return loss scheduling problem effectively, has increased the practicality of this air conditioner.

As shown in fig. 4, branch 53 includes branch 531 and branch 532. A first end of branch 531 communicates with branch 53 and a second end of branch 531 communicates with the second exhaust port. A first end of branch 532 is in communication with the main path of branch 53 and a second end of branch 532 is in communication with the first suction port. Further, in order to control the direction of the refrigerant in the pipe 50 well, the first valve 71 is provided in the branch 531, and the second valve 72 is provided in the branch 52. Wherein the second discharge port communicates with the first discharge port outside the shell of compressor 10 via branch 54. This arrangement can effectively increase the heating capacity of the compressor, wherein the letter C and the letter D in the drawing indicate the outdoor unit and the indoor unit areas, respectively.

To further increase the heating capacity of the compressor, the air conditioner also includes a bypass 54. One end of the branch 54 communicates with the first branch 531 and between the first valve 71 and the second exhaust port, and the other end of the branch 54 communicates with the first heat exchanger 20. In order to control the flow rate of the refrigerant in the branch 54, a third valve 73 is provided in the branch 54.

The conduit 50 also includes a branch 55. One end of the branch 55 communicates with the branch 52 and is located between the second valve 72 and the second suction port, and the other end of the branch 55 communicates with the outlet end of the gas-liquid separator 60. This arrangement also enables the heating capacity of the compressor to be further increased, and further, the fourth valve 74 is provided in the first branch passage 55 so as to control the flow rate of the refrigerant in the branch passage 55.

Specifically, the inlet end of the air supply supercooling device 30 is communicated with the outlet end of the first heat exchanger 20, the outlet end of the air supply supercooling device 30 is communicated with the inlet end of the second heat exchanger 40, and the air supply supercooling device 30 further comprises a bypass 31. One end of the auxiliary path 31 communicates with the outlet end of the first heat exchanger 20, and the other end of the auxiliary path 31 communicates with the air supplement path 50. The arrangement is such that the refrigerant discharged from the outlet end of the first heat exchanger 20, i.e., the refrigerant, can enter the gas supplementing supercooling device 30 through the auxiliary passage 31 for heat exchange and then enter the pump body structure through the pipeline 50 for gas supplementing.

In order to enhance the air supply effect of the air supply line 50, the bypass 31 is provided with a second throttling device 75, so that the flow rate of the refrigerant in the air supply line 50 can be effectively controlled.

To further optimize the compressor performance, the heating capacity of the air conditioner is increased. The volume ratio of the second working chamber to the third working chamber is set to Q1, wherein Q1 is more than or equal to 0.1 and less than or equal to 0.4, and further Q1 is more than or equal to 0.15 and less than or equal to 0.25. The volume ratio of the first working chamber to the third working chamber is set to Q2, wherein Q2 is more than or equal to 0.6 and less than or equal to 0.75. The volume ratio of the sixth working chamber to the fourth working chamber is Q3, wherein Q3 is more than or equal to 0.1 and less than or equal to 0.4, and further Q3 is more than or equal to 0.15 and less than or equal to 0.25. And the volume ratio of the fifth working chamber to the fourth working chamber is Q4, wherein Q4 is more than or equal to 0.6 and less than or equal to 0.75.

Specifically, as shown in fig. 4, the refrigerant flow path of the two-stage compression heat pump cycle includes a compressor 10, a second heat exchanger 40 as an outdoor heat exchanger, a first heat exchanger 20 as an indoor heat exchanger, a gas supplementing subcooling device 30 as a subcooling device, a second throttling device 75 as an auxiliary throttling device, a main throttling device 78 as a main throttling device, a gas-liquid separator 60, a fourth valve 74 as an electromagnetic two-way valve, a second valve 72, a third valve 73, and a first valve 71. As shown in fig. 2 and 3, the compressor has first, second and third compression chambers, the first compression chamber, i.e., the third cylinder 15 in fig. 3, having a first suction port and a first discharge port, the second compression chamber, i.e., the fourth cylinder 16 in fig. 3, having a second suction port and a second discharge port, and the third compression chamber, i.e., the fifth cylinder 17 in fig. 3, having a third suction port and a third discharge port. A first air suction port of the compressor is communicated with an outlet of the gas-liquid separator, a second air suction port is communicated with a first exhaust port, the second exhaust port is sequentially communicated with an indoor heat exchanger, a main path channel of the supercooling device, the main throttling device, the outdoor heat exchanger and inlets of the gas-liquid separator, a third air suction port is sequentially communicated with an auxiliary path of the supercooling device, the auxiliary path throttling device and the indoor heat exchanger through a second valve 72, and a third exhaust port is communicated with the indoor heat exchanger through a third valve 73. The compressor is also provided with an air supplementing port, and the second air suction port is also communicated with the auxiliary path of the supercooling device through the air supplementing port. The third suction port of the compressor is also communicated with the outlet of the gas-liquid separator through a fourth valve 74, and the third exhaust port is also communicated with the air supplement port through a first valve 71.

As shown in fig. 6 to 10, when the gas is needed to supplement in the middle of the two-stage compression formed by the first and second compression chambers connected in series, the auxiliary path throttling device is opened, when the fourth valve 74 and the first valve 71 of the electromagnetic two-way valve are closed, and the second valve 72 and the third valve 73 are opened, the main path recooling cycle is realized, and the operating mode of the compressor is as shown in fig. 6. The heat pump device cycle is specifically as follows: the refrigerant enters a gas-liquid separator for gas-liquid separation after being subjected to heat absorption, evaporation and gasification in the outdoor heat exchanger, low-pressure refrigerant gas enters a first compression cavity through a first air suction port and is compressed into medium-pressure superheated gas which is discharged from a first exhaust port into an intermediate cavity (with the functions of noise elimination and air supply), most of the gas enters a second compression cavity through a second air suction port and is compressed into high-pressure superheated gas which is discharged from a second exhaust port into a noise elimination cavity, then the high-pressure superheated gas flows through a motor winding and is cooled and then is discharged from an exhaust port of a compressor into an indoor heat exchanger, the high-pressure superheated gas is condensed and releases heat in the indoor heat exchanger and is divided into a main path and an auxiliary path after being supercooled, the main path refrigerant enters a main path channel of a supercooling device and is throttled by a main throttling device and is decompressed into two-phase refrigerant, and then enters an outdoor heat exchanger, the auxiliary path refrigerant is throttled by an auxiliary throttling device and is reduced to the, and the mixed gas and part of the medium-pressure superheated gas from the first exhaust port enter a third compression cavity through a third air suction port of the compressor and are compressed to high-pressure superheated gas, and the high-pressure superheated gas is exhausted to the indoor heat exchanger from the third exhaust port. At the moment, the supercooling device has a re-supercooling effect on the main path refrigerant, the specific enthalpy of the refrigerant entering the outdoor heat exchanger is reduced, so that the specific enthalpy difference of an inlet and an outlet is increased, the power consumption of the unit heating capacity of the first compression cavity and the second compression cavity is reduced, the power consumption of the unit heating capacity of the third compression cavity is lower, and the volume heating capacity is higher, so that the heating performance coefficient and the heating capacity of the heat pump device are improved on the whole compared with those of the conventional single-stage compression heat pump device. As shown in fig. 6, the compressor has a large volume ratio between high and low pressure stages when operating in the two-stage compression air-make-up operation mode, and is suitable for the operation condition of the heat pump with low heat load and low condensation temperature.

When the heat load is large and the condensing temperature is high, as shown in fig. 7, the compressor is operated in the dual-stage compression operation mode, in which the second valve 72 and the first valve 71 are closed, the fourth valve 74 and the third valve 73 and the auxiliary throttling device are opened, and the supercooling device has a re-supercooling effect so that the heating coefficient and the heating amount can be increased.

When the heat load is large and the evaporation temperature is low, the compressor operates in the two-stage compression air-make operation mode as shown in fig. 7 and has a small volume ratio of high-pressure stage to low-pressure stage, at this time, the second valve 72 and the third valve 73 are closed, the fourth valve 74, the first valve 71 and the auxiliary throttling device are opened, and the supercooling device has a re-supercooling effect, so that the heating coefficient and the heating capacity can be improved.

When the heat load is low, the compressor is operated in the parallel compression operation mode as shown in fig. 10, in which the fourth valve 74 and the third valve 73 are opened, the second valve 72, the first valve 71 and the auxiliary throttling device are closed, and the supercooling means has no supercooling effect.

The heat pump device in this embodiment, that is, the air conditioner, operates in the recooling mode under most of the operating conditions, and operates in the non-recooling mode under only a few operating conditions, such as the initial start-up, low load and low pressure ratio, and mild operating conditions of the heat pump device. Therefore, compared with a single-stage compression heat pump device, the seasonal heating performance coefficient is improved, and the heating quantity under the working conditions of low temperature and ultralow temperature is improved. The volume ratio of the high-pressure stage and the low-pressure stage of the compressor of the pump device is variable, and three options are available, so that the seasonal heating performance coefficient is effectively improved compared with that of a conventional two-stage compression air-supply enthalpy-increasing heat pump device.

The effective internal volume ratio of a third compression cavity, namely a second working cavity, to a first compression cavity, namely a third working cavity, of the compressor is 0.1-0.4, and the further optimized internal volume ratio is 0.15-0.25. The effective internal volume ratio of a second compression cavity, namely a first working cavity, and a first compression cavity, namely a third working cavity, of the compressor is 0.6-0.75.

The auxiliary throttle device is an electronic expansion valve with a valve closing function, and the main throttle device is an electronic expansion valve, a capillary tube or a throttle component of the electronic expansion valve connected with the capillary tube in series.

The subcooling device is an intermediate heat exchanger having two-sided refrigerant channels. The double-sided refrigerant of the subcooling device as in fig. 4 is in a counterflow arrangement, but alternatively a parallel flow arrangement may be used.

The electromagnetic two-way valve may be replaced by an electromagnetic three-way valve having the same function.

As shown in fig. 5, which is a system diagram of an alternative embodiment of the heat pump device, unlike the preferred embodiment, the form of the subcooling device in fig. 5 is replaced by a flash evaporator form by an intermediate heat exchanger, the corresponding auxiliary throttling device is replaced by a throttling device 77, the main throttling device is changed into a throttling device 78, and an electromagnetic two-way valve, i.e., a sixth valve 76, is added to the air supply branch and is respectively connected with the second valve 72 and the first valve 71.

In this alternative embodiment, the subcooled refrigerant from the indoor heat exchanger is throttled by the throttling device to be reduced to a medium-pressure two-phase state, the gas and the liquid are separated in the subcooling device, the separated gas enters the third compression cavity or the second compression cavity of the compressor through the second valve 72 or the sixth valve 76, or the separated liquid enters the first compression cavity or the third compression cavity of the compressor through the second throttling device, the outdoor heat exchanger and the gas-liquid separator.

In an alternative embodiment, the compressor of the heat pump apparatus has an operation mode as shown in fig. 6 to 10. The fourth valve 74 and the first valve 71 are closed, and the second valve 72, the third valve 73 and the sixth valve 76 are opened, so that the high-pressure stage volume and the low-pressure stage volume are relatively large in the double-stage compression air-replenishing working mode shown in fig. 6. The second valve 72, the first valve 71 are closed, and the fourth valve 74, the third valve 73, and the sixth valve 76 are open, as shown in the dual stage compression and charge mode of operation of fig. 7. The fourth valve 74, the first valve 71, and the sixth valve 76 are closed, and the third valve 73 is opened, as shown in the parallel compression mode of fig. 8. The second valve 72 and the third valve 73 are closed, and the fourth valve 74, the second valve 72 and the sixth valve 76 are opened, so that the volumes of the high pressure stage and the low pressure stage are relatively small in the double-stage compression air compensation working mode shown in fig. 9. The second valve 72, the first valve 71 and the sixth valve 76 are closed, and the fourth valve 74 and the third valve 73 are opened, as shown in the parallel compression mode of fig. 10. The supercooling device has a re-supercooling effect in the working modes of the first four compressors, so that the heating coefficient and the heating quantity are improved.

The supercooling device of the embodiment has no heat exchange temperature difference, so that the supercooling device has high supercooling effect when operated in the re-supercooling mode. The first and second throttling devices in this alternative embodiment may be electronic expansion valves, capillary tubes, etc., and the valves in this embodiment may also be replaced by electromagnetic three-way valves having the same function. The supercooling device in this embodiment can be a bidirectional flash evaporator, and a necessary four-way reversing valve is added to realize a refrigerating function.

The compressor in the embodiment adopts multiple compression cavities to form multiple better working modes through the switching of the external valve. The compressor is provided with a first compression cavity and a second compression cavity which are mutually connected in series and a third compression cavity which can be compressed in parallel with two or one of the compression cavities connected in series, the first compression cavity and the second compression cavity are respectively a low-pressure stage and a high-pressure stage in a double-stage, an air suction port of the third compression cavity can be selectively connected with an air suction port of the first compression cavity or an air supplement port of the double-stage compression or an air supplement branch of the double-stage compression through the switching of an external valve of the compressor, and the air supplement branch of the double-stage compression can be selectively supplemented with air or not supplemented with air through the opening or.

The exhaust port of the third compression cavity can be selectively connected with the exhaust port of the second compression cavity through the switching of an external valve, or connected with the air supplement port of the double-stage compression and the air suction port of the third compression cavity is connected with the air suction port of the first compression cavity. The air supply branch is connected with a gas outlet of a supercooling device, and the supercooling device can be a flash evaporator or an intermediate heat exchanger. Herein, the parallel compression means that at least two compression chambers respectively compress at least two different fluids at the same time.

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. An air conditioner is characterized by comprising a compressor (10), a first heat exchanger (20), an air supply supercooling device (30), a second heat exchanger (40) and a gas-liquid separator (60), which are communicated with each other; wherein,

the compressor (10) comprises a pump body structure, the pump body structure comprises a plurality of cylinders, at least one of the cylinders comprises a main working cavity, at least one of the cylinders comprises an auxiliary working cavity, and the main working cavity and the auxiliary working cavity are provided with a suction port and an exhaust port respectively;

the air suction port of the auxiliary working cavity is selectively communicated with the gas-liquid separator (60) or the air supply supercooling device (30), and the air exhaust port of the auxiliary working cavity is selectively communicated with the first heat exchanger (20) or the air supply supercooling device (30).

2. The air conditioner according to claim 1, wherein a first valve (71) is provided on a pipeline connecting the exhaust port of the auxiliary working chamber and the air make-up subcooling device (30).

3. The air conditioner according to claim 1, wherein a second valve (72) is provided on a line connecting the suction port of the auxiliary working chamber and the supplementary air supercooling means (30).

4. The air conditioner according to claim 1, wherein a third valve (73) is provided on a pipe communicating the exhaust port of the auxiliary working chamber and the first heat exchanger (20).

5. The air conditioner according to claim 1, wherein a fourth valve (74) is provided on a pipe communicating the suction port of the auxiliary working chamber and the gas-liquid separator (60).

6. The air conditioner according to claim 1, wherein the plurality of cylinders comprise:

first cylinder (11), first cylinder (11) include first gleitbretter (12) and second gleitbretter (13), first gleitbretter (12) with second gleitbretter (13) will first working chamber and second working chamber are separated into to the inner chamber of first cylinder (11), the second working chamber forms supplementary working chamber.

7. The air conditioner according to claim 6, wherein the first working chamber has a first air intake communicated with the air make-up subcooling device (30) and a first air exhaust communicated with the first heat exchanger (20), and the second working chamber has a second air intake communicated with the first heat exchanger (20) or the first air intake and a second air exhaust, the second air intake being selectively communicated with the air make-up subcooling device (30) or the gas-liquid separator (60).

8. The air conditioner of claim 7, wherein the plurality of cylinders further comprises:

the second air cylinder (14) is located below the first air cylinder (11), the second air cylinder (14) is provided with a third working cavity, the third working cavity is provided with a third air suction port and a third air exhaust port, the third air suction port is communicated with the air-liquid separator (60), the third air exhaust port is communicated with the first air suction port, and the third working cavity is the main working cavity.

9. The air conditioner according to claim 1, wherein a plurality of said cylinders are arranged in a vertical direction, each of said cylinders having a working chamber, said working chamber being said main working chamber or said auxiliary working chamber.

10. The air conditioner according to claim 9, wherein the plurality of cylinders includes a third cylinder having a fourth working chamber having a fourth suction port and a fourth exhaust port, and a fifth working chamber having a fifth suction port and a fifth exhaust port, the fourth suction port being in communication with the second heat exchanger (40), the fourth exhaust port being in communication with the fifth suction port, the fifth exhaust port being in communication with the first heat exchanger (20), wherein the fourth working chamber is the main working chamber.

11. The air conditioner according to claim 10, wherein the plurality of cylinders further includes a fifth cylinder having a sixth working chamber having a sixth suction port in selective communication with the second heat exchanger (40) or the supplemental subcooling device (30) and a sixth discharge port in selective communication with the fifth suction port or the first heat exchanger (20), wherein the sixth working chamber is the auxiliary working chamber.

12. The air conditioner according to claim 1, wherein the air make-up subcooling device (30) comprises:

and a liquid inlet pipeline of the flash evaporator (32) is communicated with the outlet end of the first heat exchanger (20), a liquid outlet pipeline of the flash evaporator (32) is communicated with the inlet end of the second heat exchanger (40), and a gas outlet of the flash evaporator (32) is communicated with a gas suction port of the auxiliary working cavity.

13. Air conditioner according to claim 12, characterized in that a sixth valve (76) is provided in the line connecting the outlet of the flash tank (32) with the suction inlet of the auxiliary working chamber.

14. The air conditioner according to claim 1, wherein the inlet end of the air supply supercooling device (30) is communicated with the outlet end of the first heat exchanger (20), the outlet end of the air supply supercooling device (30) is communicated with the inlet end of the second heat exchanger (40), the air supply supercooling device (30) further comprises an auxiliary path (31), one end of the auxiliary path (31) is communicated with the outlet end of the first heat exchanger (20), the other end of the auxiliary path (31) is communicated with the air suction port of the auxiliary working chamber, and a throttling device (75) is arranged on the auxiliary path (31).

15. The air conditioner as claimed in claim 8, wherein a volume ratio of the second working chamber to the third working chamber is Q1, wherein 0.1 ≦ Q1 ≦ 0.4.

16. The air conditioner as claimed in claim 8, wherein a volume ratio of the first working chamber to the third working chamber is Q2, wherein 0.6 ≦ Q2 ≦ 0.75.

17. The air conditioner as claimed in claim 11, wherein a volume ratio of the sixth working chamber to the fourth working chamber is Q3, wherein 0.1 ≦ Q3 ≦ 0.4.

18. The air conditioner as claimed in claim 11, wherein a volume ratio of the fifth working chamber to the fourth working chamber is Q4, wherein 0.6 ≦ Q4 ≦ 0.75.

19. The air conditioner according to claim 1, wherein the discharge port of the auxiliary working chamber is in communication with the first heat exchanger (20) or the supplementary subcooling device (30) selectively outside the shell of the compressor (10).