CN108931021B - Heat pump system and air conditioner with same - Google Patents
Heat pump system and air conditioner with same Download PDFInfo
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- CN108931021B CN108931021B CN201811093618.1A CN201811093618A CN108931021B CN 108931021 B CN108931021 B CN 108931021B CN 201811093618 A CN201811093618 A CN 201811093618A CN 108931021 B CN108931021 B CN 108931021B
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- 239000007788 liquid Substances 0.000 claims abstract description 68
- 239000003507 refrigerant Substances 0.000 claims abstract description 18
- 238000004891 communication Methods 0.000 claims description 14
- 238000009833 condensation Methods 0.000 description 10
- 230000005494 condensation Effects 0.000 description 10
- 239000013526 supercooled liquid Substances 0.000 description 10
- 238000001704 evaporation Methods 0.000 description 8
- 230000008020 evaporation Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 230000001965 increasing effect Effects 0.000 description 6
- 229920006395 saturated elastomer Polymers 0.000 description 6
- 230000001502 supplementing effect Effects 0.000 description 6
- 230000008569 process Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000002427 irreversible effect Effects 0.000 description 3
- 239000011555 saturated liquid Substances 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
Abstract
The application provides a heat pump system and an air conditioner with the same. The heat pump system comprises a compressor, wherein the compressor is provided with a plurality of air cylinders, and each air cylinder is provided with an independent air suction port; the plurality of cylinders at least comprise one variable volume cylinder, the variable volume cylinder has a working state when the refrigerant is compressed, and the variable volume cylinder has an idle state when the refrigerant is not compressed; the plurality of cylinders comprise at least one parallel cylinder, and an air suction port of the parallel cylinder is selectively communicated with an outlet end of the medium-pressure gas pipeline or the gas-liquid separator. By changing the connection mode of the air suction ports of the parallel air cylinders and the working state of the variable capacity air cylinders, the compressor can keep stable running frequency under high load, noise is reduced, reliability is improved, stable running frequency under low load is also kept, the efficiency of the compressor and the performance coefficient of the heat pump device are improved, and the energy efficiency of the heat pump device is improved.
Description
Technical Field
The application relates to the technical field of air conditioning equipment, in particular to a heat pump system and an air conditioner with the heat pump system.
Background
In the prior art, the heating capacity of the air source heat pump is rapidly reduced along with the reduction of the outdoor environment temperature, so that the heating capacity of the air source heat pump cannot meet the demands of users. In the prior art, a two-stage or quasi-two-stage compression middle air supplementing enthalpy increasing technology is generally adopted, but air supplementing mixing loss and reflux loss exist, and the two-stage air supplementing has the problems of flow resistance loss and the like, so that the air supplementing enthalpy increasing effect is affected to a certain extent. The existing two-stage compressor has the disadvantages of fixed high-low pressure displacement ratio, poor adaptability when working conditions change, poor energy efficiency, high frequency of operation of the compressor when the load is overlarge, increased noise of the compressor, poor reliability, low frequency of operation of the compressor when the load is overlarge, reduced efficiency of the compressor, reduced performance coefficient and even possible shutdown in some cases.
Disclosure of Invention
The application mainly aims to provide a heat pump system and an air conditioner with the same, so as to solve the problem of low energy efficiency of a heat pump device in the prior art.
In order to achieve the above object, according to one aspect of the present application, there is provided a heat pump system comprising: the compressor is provided with a plurality of cylinders, and each cylinder is provided with an independent air suction port; the plurality of cylinders at least comprise one variable volume cylinder, the variable volume cylinder has a working state when the refrigerant is compressed, and the variable volume cylinder has an idle state when the refrigerant is not compressed; the plurality of cylinders comprise at least one parallel cylinder, and an air suction port of the parallel cylinder is selectively communicated with an outlet end of the medium-pressure gas pipeline or the gas-liquid separator.
Further, the plurality of cylinders includes: the first air cylinder is arranged in the compressor shell and is provided with a first air suction port which is communicated with the outlet end of the gas-liquid separator; the second air cylinder is arranged in the compressor shell and is provided with a second air suction port, the second air suction port is communicated with the outlet end of the gas-liquid separator, and the second air cylinder is a variable-volume air cylinder; the third air cylinder is arranged in the compressor shell and is provided with a third air suction port, the third air suction port is selectively communicated with an outlet end of the medium-pressure gas pipeline or the gas-liquid separator, and the third air cylinder is a parallel air cylinder.
Further, the heat pump system further includes: the first end of the air suction main path is communicated with the outlet end of the gas-liquid separator; the first end of the first air suction branch is communicated with the second end of the air suction main path, and the second end of the first air suction branch is communicated with the first air suction port; the first end of the second air suction branch is communicated with the second end of the air suction main path, and the second end of the second air suction branch is communicated with the second air suction port; and the first end of the third air suction branch is selectively communicated with the second end of the air suction main path or the medium-pressure air pipeline, and the second end of the third air suction branch is communicated with the third air suction port.
Further, the heat pump system further includes: the first valve body is positioned between the second end of the air suction main path and the connecting part of the first end of the third air suction branch path and the medium-pressure gas pipeline.
Further, the heat pump system further includes: the second valve body is arranged on the medium-pressure gas pipeline.
Further, the heat pump system further includes: the inlet end of the condenser is communicated with the exhaust port of the compressor; the outlet end of the evaporator is communicated with the inlet end of the gas-liquid separator; the first outlet end of the flash evaporator is communicated with the medium-pressure gas pipeline, the second outlet end of the flash evaporator is communicated with the inlet end of the evaporator, and the inlet end of the flash evaporator is communicated with the outlet end of the condenser.
Further, the heat pump system further includes: the inlet end of the condenser is communicated with the exhaust port of the compressor; the outlet end of the evaporator is communicated with the inlet end of the gas-liquid separator; and the first outlet end of the economizer is communicated with the medium-pressure gas pipeline, the second outlet end of the economizer is communicated with the inlet end of the evaporator, the first inlet end of the economizer is communicated with the outlet end of the condenser, and the second inlet end of the economizer is communicated with the outlet end of the condenser.
Further, the heat pump system further includes: a first throttling device is positioned on a pipeline which is communicated between the condenser and the first inlet end of the economizer.
Further, the heat pump system further includes: and the first throttling device is positioned on a pipeline communicated between the condenser and the flash evaporator.
Further, the plurality of condensers are arranged in parallel, the plurality of first throttling devices are arranged in a one-to-one correspondence with the plurality of condensers.
Further, the heat pump system further includes: and the second throttling device is arranged on a pipeline between the evaporator and the flash evaporator.
Further, the heat pump system further includes: and the second throttling device is arranged on a pipeline between the evaporator and the economizer.
Further, the first cylinder has a volume V P1 The volume of the second cylinder is V P2 The volume of the third cylinder is V P3 Wherein V is 0.05.ltoreq.V P3 /(V P1 +V P2 ) Not more than 0.25, and V not less than 0.5 P1 /V P2 ≤1。
According to another aspect of the present application, there is provided an air conditioner including a heat pump system, the heat pump system being the heat pump system described above.
By adopting the technical scheme of the application, one of the cylinders in the compressor is set as the variable capacity cylinder, the variable capacity cylinder has the working state and the idle state, one of the cylinders is set as the parallel cylinder, the air suction port of the parallel cylinder is selectively communicated with the middle pressure gas pipeline or the outlet end of the gas-liquid separator, and the stable operating frequency of the compressor can be maintained under high load, the noise is reduced, the reliability is improved, the stable operating frequency can be maintained under low load, the efficiency of the compressor and the performance coefficient of the heat pump device are improved, and the energy efficiency of the heat pump device is improved.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
fig. 1 shows a schematic structural view of an embodiment one of a heat pump system according to the present application;
fig. 2 shows a schematic structural diagram of a second embodiment of a heat pump system according to the application;
fig. 3 shows a schematic view of an operation mode of an embodiment one of a compressor of the heat pump system according to the present application;
fig. 4 shows a schematic view of an operation mode of a second embodiment of a compressor of the heat pump system according to the application;
fig. 5 shows a schematic view of an operation mode of a third embodiment of a compressor of the heat pump system according to the present application;
fig. 6 shows a schematic view of an operation mode of a fourth embodiment of a compressor of the heat pump system according to the present application;
fig. 7 shows a schematic structural diagram of a third embodiment of a heat pump system according to the application.
Wherein the above figures include the following reference numerals:
1. a compressor; 2. a condenser; 3. an evaporator; 4. a gas-liquid separator; 5. a first throttle device; 6. a second throttle device; 101. an air suction main path; 1011. a first suction branch; 1012. a second suction branch; 1013. a third suction branch; 102. a medium pressure gas line; 20. a first air suction port; 30. a second air suction port; 40. a third air suction port; 50. a first cylinder; 60. a second cylinder; 70. a third cylinder; 7. a second valve body; 8. a first valve body; 9. a flash; 10. an economizer; 80. and an exhaust port.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
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 exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims and drawings of the present application are used for distinguishing between similar objects 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 … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative 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 in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (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 the embodiments set forth herein. It should be understood that these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of these exemplary embodiments to those skilled in the art, that in the drawings, it is possible to enlarge the thicknesses of layers and regions for clarity, and that identical reference numerals are used to designate identical devices, and thus descriptions thereof will be omitted.
As shown in connection with fig. 1 to 7, a heat pump system is provided according to an embodiment of the present application.
Specifically, as shown in fig. 1, the heat pump system includes a compressor 1, the compressor 1 having a plurality of cylinders each having an independent suction port; the plurality of cylinders at least comprise one variable volume cylinder, the variable volume cylinder has a working state when the refrigerant is compressed, and the variable volume cylinder has an idle state when the refrigerant is not compressed; the plurality of cylinders comprises at least one parallel cylinder, and the air suction port of the parallel cylinder is selectively communicated with the medium pressure gas pipeline 102 or the outlet end of the gas-liquid separator 4.
In this embodiment, one of the plurality of cylinders in the compressor is set as a variable capacity cylinder, the variable capacity cylinder has an operating state and an idle state, one of the plurality of cylinders is set as a parallel cylinder, an air suction port of the parallel cylinder is selectively communicated with an outlet end of a medium-pressure gas pipeline or a gas-liquid separator, and by changing a connection mode of the air suction port of the parallel cylinder and changing the operating state of the variable capacity cylinder, the compressor can maintain stable operating frequency under high load, noise is reduced, reliability is improved, stable operating frequency under low load is maintained, and efficiency of the compressor and performance coefficient of the heat pump device are improved, thereby improving energy efficiency of the heat pump device.
As shown in fig. 3 to 6, the plurality of cylinders includes a first cylinder 50, the first cylinder 50 being disposed in the compressor housing, the first cylinder 50 having a first suction port 20, the first suction port 20 being in communication with an outlet end of the gas-liquid separator 4; the second cylinder 60, the second cylinder 60 is set up in compressor housing, the second cylinder 60 has the second air suction port 30, the second air suction port 30 is communicated with outlet end of the gas-liquid separator 4, the second cylinder 60 is the variable volume cylinder; the third cylinder 70, the third cylinder 70 is set in the compressor housing, the third cylinder 70 has the third air suction port 40, the third air suction port 40 is selectively connected with the medium pressure gas pipeline 102 or the outlet end of the gas-liquid separator 4, the third cylinder 70 is a parallel cylinder. By changing the working state of the variable-capacity cylinder, namely the second cylinder 60, the compressor can keep stable operating frequency under high load, noise is reduced, reliability is improved, stable operating frequency under low load is also kept, the efficiency of the compressor and the coefficient of performance of the heat pump device are improved, and the energy efficiency of the heat pump device is improved. By changing the connection mode of the third air suction port, the air supplementing or normal air suction operation can be performed on the compressor.
As shown in fig. 1, 2 and 7, the heat pump system further includes an air suction main circuit 101, a first air suction branch 1011, a second air suction branch 1012 and a third air suction branch 1013, wherein a first end of the air suction main circuit 101 is communicated with an outlet end of the gas-liquid separator 4; a first suction branch 1011, a first end of the first suction branch 1011 is communicated with a second end of the suction main path 101, a second end of the first suction branch 1011 is communicated with the first suction port 20, a second suction branch 1012, a first end of the second suction branch 1012 is communicated with a second end of the suction main path 101, a second end of the second suction branch 1012 is communicated with the second suction port 30, a third suction branch 1013, a first end of the third suction branch 1013 is selectively communicated with the second end of the suction main path 101 or the medium pressure gas line 102, and a second end of the third suction branch 1013 is communicated with the third suction port 40. By changing the connection mode of the third suction branch 1013, the compressor can keep stable operation frequency under high load, noise is reduced, reliability is improved, stable operation frequency under low load is also kept, efficiency of the compressor and performance coefficient of the heat pump device are improved, and energy efficiency of the heat pump device is improved.
The heat pump system further comprises a first valve body 8 and a second valve body 7, wherein the first valve body 8 is positioned between the second end of the air suction main path 101 and the connection part of the first end of the third air suction branch path 1013 and the medium pressure gas pipeline 102, and the second valve body 7 is arranged on the medium pressure gas pipeline 102. The connection mode of the third suction branch 1013 can be changed by adjusting the first valve body 8 and the second valve body 7, so that the compressor can keep stable operation frequency under high load, noise is reduced, reliability is improved, stable operation frequency under low load is also kept, the efficiency of the compressor and the performance coefficient of the heat pump device are improved, and the energy efficiency of the heat pump device is improved.
As shown in fig. 1, the heat pump system further comprises a condenser 2, an evaporator 3 and a flash evaporator 9, wherein the inlet end of the condenser 2 is communicated with the exhaust port of the compressor, the outlet end of the evaporator 3 is communicated with the inlet end of the gas-liquid separator 4, the first outlet end of the flash evaporator 9 is communicated with the medium-pressure gas pipeline 102, the second outlet end of the flash evaporator 9 is communicated with the inlet end of the evaporator 3, and the inlet end of the flash evaporator 9 is communicated with the outlet end of the condenser 2.
As shown in fig. 7, the heat pump system further includes a condenser 2, an evaporator 3, and an economizer 10, an inlet end of the condenser 2 being in communication with a discharge port of the compressor; the outlet end of the evaporator 3 is communicated with the inlet end of the gas-liquid separator 4, the first outlet end of the economizer 10 is communicated with the medium-pressure gas pipeline 102, the second outlet end of the economizer 10 is communicated with the inlet end of the evaporator 3, the first inlet end of the economizer 10 is communicated with the outlet end of the condenser 2, and the second inlet end of the economizer 10 is communicated with the outlet end of the condenser 2.
As shown in fig. 7, the heat pump system further includes a first throttling device 5, and the first throttling device 5 is located on a line communicating between the condenser 2 and the first inlet end of the economizer 10. When the high-temperature and high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, the refrigerant becomes a medium-temperature and medium-pressure gas-liquid two-phase after entering the first throttling device 5.
As shown in fig. 1, the heat pump system further comprises a first throttling device 5, and the first throttling device 5 is positioned on a pipeline communicating between the condenser 2 and the flash vessel 9. When the high-temperature and high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, the refrigerant becomes a medium-temperature and medium-pressure gas-liquid two-phase after entering the first throttling device 5.
As shown in fig. 2, the plurality of condensers 2 is provided with the first throttle device 5 in parallel, and the plurality of throttle devices are provided in one-to-one correspondence with the plurality of condensers 2. The condenser 2 may be a plurality of condensers, and a first throttling device 5 is added to the branch of each condenser group, and the system diagram of this embodiment is shown in fig. 2, so that the actual load requirements of the respective condensers can be met by adjusting the throttling device.
In this embodiment, the heat pump system further comprises a second throttling means 6, the second throttling means 6 being arranged on the line between the evaporator 3 and the flash vessel 9. The saturated steam which does not generate heat exchange under the intermediate pressure is separated by adopting the secondary throttling, and is independently compressed by utilizing one cylinder, so that the expansion work in the irreversible throttling process is recovered, the specific enthalpy of the refrigerant at the inlet of the evaporator is reduced, the power consumption of the compressor with unit refrigerating capacity is reduced, the energy efficiency of the heat pump device is improved, the exhaust temperature of some compressors can be reduced by increasing the enthalpy, and the reliability of the compressors under some extreme working conditions is improved.
In this embodiment, the heat pump system further comprises a second throttling device 6, the second throttling device 6 being arranged on the line between the evaporator 3 and the economizer 10. The saturated steam which does not generate heat exchange under the intermediate pressure is separated by adopting the secondary throttling, and is independently compressed by utilizing one cylinder, so that the expansion work in the irreversible throttling process is recovered, the specific enthalpy of the refrigerant at the inlet of the evaporator is reduced, the power consumption of the compressor with unit refrigerating capacity is reduced, the energy efficiency of the heat pump device is improved, the exhaust temperature of some compressors can be reduced by increasing the enthalpy, and the reliability of the compressors under some extreme working conditions is improved.
In the present embodiment, the first cylinder 50 has a volume V P1 The volume of the second cylinder 60 is V P2 The volume of the third cylinder 70 is V P3 Wherein V is 0.05.ltoreq.V P3 /(V P1 +V P2 ) Less than or equal to 0.25, and/or, 0.5 less than or equal to V P1 /V P2 And is less than or equal to 1. The arrangement can not only enable the compressor to keep stable running frequency under high load, reduce noise and improve reliability, but also keep stable running frequency under low load, improve the efficiency of the compressor and the performance coefficient of the heat pump device, and improve the energy efficiency of the heat pump device.
The heat pump system of the above embodiment may also be used in the technical field of air conditioner apparatuses, that is, according to another aspect of the present application, there is provided an air conditioner including the heat pump system of the above embodiment.
A heat pump device comprises a compressor 1, a condenser 2, a flash evaporator 9, an evaporator 3 and a gas-liquid separator 4 which are communicated. The compressor 1 has three cylinders, including a main cylinder, i.e. a first cylinder 50, an unloading cylinder, i.e. a second cylinder 60 and a third cylinder 70, and three suction openings, i.e. a main cylinder first suction opening 20, an unloading cylinder second suction opening 30 and a third cylinder third suction opening 40, respectively, and a common discharge opening 80. The third cylinder third suction port 40 is selectively communicated with the flash evaporator 9 or the gas-liquid separator 4. The main cylinder first air suction port 20 and the unloading cylinder second air suction port 30 of the compressor 1 are communicated in parallel and are communicated with the outlet end of the evaporator 3, the gas-liquid separator 4 is arranged in the middle, the first valve body 8 is arranged on an air suction pipeline of the third cylinder third air suction port 40 communicated with the gas-liquid separator 4, the second valve body 7 is arranged on a medium-pressure gas pipeline 102 communicated with the flash evaporator 9, and the exhaust port 80 of the compressor is communicated with the inlet end of the condenser 2. The liquid inlet pipeline of the flash evaporator 9 is communicated with the outlet end of the condenser 2, a first throttling device 5 is arranged in the middle of the pipeline, the liquid outlet pipeline of the flash evaporator 9 is communicated with the inlet end of the evaporator 3, a second throttling device 6 is arranged in the middle of the pipeline, and the gas outlet of the flash evaporator 9 is communicated with a medium-pressure gas pipeline 102. The flash vessel 9 may be replaced by an economizer 10, where the main inlet of the economizer 10 is connected to the outlet of the condenser 2, the main outlet is connected to the inlet of the evaporator 3, a second throttling device 6 is arranged in the middle of the pipeline, the auxiliary inlet of the economizer 10 is connected to the outlet of the condenser 2, a first throttling device 5 is arranged in the middle of the pipeline, and the auxiliary outlet is connected to the medium pressure gas pipeline 102.
In the present embodiment, the first suction port 20 is in communication with the suction line, there are four operation modes in which when the second cylinder 60 is not unloaded, three cylinders are operated simultaneously, the operation mode in which the third suction port 40 is in communication with the medium pressure gas line 102 is as shown in fig. 3, the operation mode in which the third suction port 40 is also in communication with the suction line is as shown in fig. 5, the operation modes in which the first cylinder 50 and the third cylinder 70 are operated when the second cylinder 60 is unloaded, the operation mode in which the third suction port 40 is also in communication with the suction line is as shown in fig. 5, and the operation mode in which the third suction port 40 is in communication with the medium pressure gas line 102 is as shown in fig. 6.
The heat pump system is in normal operation: when the load is large, the first valve body 8 is closed, the second valve body 7 is opened, and the operation mode is as shown in fig. 3, and at this time, the second cylinder 60 of the compressor is not unloaded, so that the frequency of the compressor is not particularly high, thereby reducing noise and improving reliability. The high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to emit heat for condensation, then enters the first throttling device 5, the refrigerant is changed into gas-liquid two phases with medium temperature and medium pressure, then enters the flash evaporator 9 to realize gas-liquid separation, wherein the medium-pressure saturated gas passes through the second valve body 7 and then enters the suction pipeline of the third cylinder 70 of the compressor, the high-temperature high-pressure gas is compressed in the third cylinder 70 and discharged, the medium-pressure saturated liquid is throttled again by the second throttling device 6 and becomes gas-liquid two phases with low temperature and low pressure, then enters the evaporator 3 to absorb heat for evaporation and then becomes low-pressure gas, then enters the gas-liquid separator 4, the gas discharged from the gas-liquid separator simultaneously enters the first cylinder 50 and the second cylinder 60 which are main cylinders of the compressor, the high-temperature high-pressure gas is compressed in the first cylinder 50 and the second cylinder 60, and the gas discharged from the three cylinders are mixed and then discharged from the exhaust port 80 of the compressor. In addition, when the load is small, the first valve body 8 is opened, the second valve body 7 is closed, and the operation mode is as shown in fig. 4, and the second cylinder 60 of the compressor is unloaded at the moment, so that the frequency of the compressor is not particularly low, the efficiency of the compressor is improved, and the energy efficiency of the heat pump system is improved. The high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to emit heat for condensation, then enters the first throttling device 5, the refrigerant is changed into gas-liquid two phases with medium temperature and medium pressure, then enters the flash evaporator 9, at the moment, the flash evaporator 9 plays a role of a liquid storage device in the system, the refrigerant enters the second throttling device 6 after exiting from the flash evaporator 9 and is throttled again to be changed into gas-liquid two phases with low temperature and low pressure, then enters the evaporator 3 to absorb heat for evaporation and then is changed into low-pressure gas, then enters the gas-liquid separator 4, the gas exiting from the gas-liquid separator simultaneously enters the first cylinder 50 and the third cylinder 70 of the compressor, and the gas exiting from the two cylinders is mixed and then is discharged from the exhaust port 80 of the compressor. When the air conditioning system works normally (the running mode is shown in fig. 3 and fig. 4), the stable running frequency can be kept under high load, the noise is reduced, the reliability is improved, the stable running frequency can be kept under low load, the efficiency of the compressor and the energy efficiency of the heat pump system are improved, and the shutdown phenomenon is avoided. In addition, in the operation mode, as shown in fig. 3, secondary throttling is adopted, saturated steam which does not generate heat exchange under the middle pressure is separated, and the single cylinder is utilized for compression, so that the expansion work in the irreversible throttling process is recovered, the dryness of the inlet of the evaporator is reduced, the heat exchange efficiency of the evaporator is improved, the energy efficiency of a heat pump system is improved, the air supplementing enthalpy increasing capacity can reduce the exhaust temperature of some compressors, and the reliability of the compressors under extreme working conditions is improved.
Other modes of operation of the heat pump system: in the operating mode, as shown in fig. 5, the first valve body 8 is open, the second valve body 7 is closed, and the second cylinder 60 of the compressor is not unloaded. At this time, the high-temperature and high-pressure exhaust gas of the compressor 1 enters the condenser 2 to emit heat for condensation, then enters the first throttling device 5, the refrigerant turns into gas-liquid two phases with medium temperature and medium pressure, then enters the flash evaporator 9, at this time, the flash evaporator 9 plays a role of a liquid storage device in the system, the refrigerant enters the second throttling device 6 after exiting from the flash evaporator 9 and then turns into gas-liquid two phases with low temperature and low pressure after throttling again, then enters the evaporator 3 to absorb heat for evaporation, turns into low-pressure gas, then enters the gas-liquid separator 4, the gas exiting from the gas-liquid separator simultaneously enters the first cylinder 50, the second cylinder 60 and the third cylinder 70 of the compressor, and the gas exiting from the three cylinders is discharged from the exhaust port 80 of the compressor after being mixed. In the operating mode, as shown in fig. 6, the first valve body 8 is closed, the second valve body 7 is opened, and the second cylinder 60 of the compressor is unloaded. At this time, the high-temperature and high-pressure exhaust gas of the compressor 1 enters the condenser 2 to emit heat for condensation, then enters the first throttling device 5, the refrigerant is changed into medium-temperature and medium-pressure gas-liquid two phases, then enters the flash evaporator 9 to realize gas-liquid separation, wherein the medium-pressure saturated gas passes through the second valve body 7 and then enters the suction pipeline of the third cylinder 70 of the compressor, the high-temperature and high-pressure gas is compressed in the third cylinder 70 to be discharged, the medium-pressure saturated liquid is throttled again by the second throttling device 6 to be changed into low-temperature and low-pressure gas-liquid two phases, then enters the evaporator 3 to absorb heat for evaporation and then become low-pressure gas, then enters the gas-liquid separator 4, the gas discharged from the gas-liquid separator enters the first cylinder 50 of the compressor to be compressed into high-temperature and high-pressure gas in the first cylinder 50, and the gas discharged from the two cylinders are mixed and then discharged from the exhaust port 80 of the compressor.
The flash vessel 9 in fig. 1 can be replaced with an economizer 10, and the replaced heat pump system is shown in fig. 7. The refrigerant circulation mode and operation mode in the whole heat pump system are basically the same as those of the heat pump system in fig. 1 described above, except that the functions of saturated gas and saturated liquid generated by the flash tank 9 are realized by the economizer 10. Part of the high-pressure supercooled liquid from the condenser is changed into medium-temperature medium-pressure gas-liquid two-phase after passing through the first throttling device 5, exchanges heat with the other part of the high-pressure supercooled liquid, absorbs heat, enters the medium-pressure gas pipeline 102, releases heat, is further supercooled, and then enters the second throttling device 6. The mode of operation after replacement is as follows:
the heat pump system is in normal operation: when the load is large, the first valve body 8 is closed, the second valve body 7 is opened, and the operation mode is as shown in fig. 3, and at this time, the second cylinder 60 of the compressor is not unloaded, so that the frequency of the compressor is not particularly high, thereby reducing noise and improving reliability. After the high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, part of the discharged high-pressure supercooled liquid is changed into medium-temperature medium-pressure gas-liquid two phases after passing through the first throttling device 5, exchanges heat with the other part of the high-pressure supercooled liquid, enters the medium-pressure gas pipeline 102 through the second valve body 7 after absorbing heat, then enters the air suction pipeline of the third cylinder 70 of the compressor, is compressed into high-temperature high-pressure gas in the third cylinder 70 for discharge, the other part of the high-pressure supercooled liquid is further supercooled after releasing heat, then enters the second throttling device 6 for throttling again into low-temperature low-pressure gas-liquid two phases, then enters the evaporator 3 for absorbing heat for evaporation, then becomes low-pressure gas, then enters the gas-liquid separator 4, and the gas discharged from the gas-liquid separator simultaneously enters the first cylinder 50 and the second cylinder 60 of the compressor, is compressed into high-temperature high-pressure gas in the first cylinder 50 and the second cylinder 60 for discharge, and the gas discharged from the exhaust port of the compressor after mixing. In addition, when the load is small, the first valve body 8 is opened, the second valve body 7 is closed, and the operation mode is as shown in fig. 4, and the second cylinder 60 of the compressor is unloaded at the moment, so that the frequency of the compressor is not particularly low, the efficiency of the compressor is improved, and the energy efficiency of the heat pump system is improved. After the high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, the second valve body 7 is in a closed state, the first throttling device 5 and the economizer 10 are not in action, so that high-pressure supercooled liquid directly passes through the economizer 10, then passes through the second throttling device 6 and throttles to become low-temperature low-pressure gas-liquid two phases, then enters the evaporator 3 to absorb heat for evaporation and then becomes low-pressure gas, then enters the gas-liquid separator 4, the gas discharged from the gas-liquid separator simultaneously enters the first cylinder 50 and the third cylinder 70 of the compressor, and the gas discharged from the two cylinders is mixed and then discharged from the exhaust port 80 of the compressor.
Other modes of operation of the heat pump system: in the operating mode, as shown in fig. 5, the first valve body 8 is open, the second valve body 7 is closed, and the second cylinder 60 of the compressor is not unloaded. After the high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, the second valve body 7 is in a closed state, the first throttling device 5 and the economizer 10 are not in action, so that the high-pressure supercooled liquid directly passes through the economizer 10, then passes through the second throttling device 6 and is throttled to become low-temperature low-pressure gas-liquid two phases, then enters the evaporator 3 to absorb heat for evaporation and then becomes low-pressure gas, then enters the gas-liquid separator 4, the gas discharged from the gas-liquid separator simultaneously enters the first cylinder 50, the second cylinder 60 and the third cylinder 70 of the compressor, and the gas discharged from the three cylinders is mixed and then discharged from the exhaust port 80 of the compressor. In the operating mode, as shown in fig. 6, the first valve body 8 is closed, the second valve body 7 is opened, and the second cylinder 60 of the compressor is unloaded. After the high-temperature high-pressure exhaust gas of the compressor 1 enters the condenser 2 to release heat for condensation, part of the discharged high-pressure supercooled liquid is changed into medium-temperature medium-pressure gas-liquid two phases after passing through the first throttling device 5, exchanges heat with the other part of the high-pressure supercooled liquid, enters the medium-pressure gas pipeline 102 through the second valve body 7 after absorbing heat, then enters the air suction pipeline of the third cylinder 70 of the compressor, is compressed into high-temperature high-pressure gas in the third cylinder 70 for discharge, the other part of the high-pressure supercooled liquid is further supercooled after releasing heat, then enters the second throttling device 6 for throttling again into low-temperature low-pressure gas-liquid two phases, then enters the evaporator 3 for absorbing heat for evaporation, then becomes low-pressure gas, then enters the gas-liquid separator 4, and the gas discharged from the gas-liquid separator simultaneously enters the first cylinder 50 and the second cylinder 60 of the compressor, is compressed into high-temperature high-pressure gas in the first cylinder 50 and the second cylinder 60 for discharge, and the gas discharged from the exhaust port of the compressor after mixing.
In addition to the foregoing, references in the specification to "one embodiment," "another embodiment," "an embodiment," etc., indicate that the particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the application, as generally described. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment. Further, when a particular feature, structure, or characteristic is described in connection with any embodiment, it is intended that such feature, structure, or characteristic be implemented within the scope of the application.
In the foregoing embodiments, the descriptions of the embodiments are emphasized, and for parts of one embodiment that are not described in detail, reference may be made to related descriptions of other embodiments.
The above is only a preferred embodiment of the present application, and is not intended to limit the present application, but various modifications and variations can be made to the present application by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application should be included in the protection scope of the present application.
Claims (12)
1. A heat pump system, comprising:
a compressor (1), the compressor (1) having a plurality of cylinders, each of the plurality of cylinders having an independent suction port;
the plurality of cylinders at least comprise one variable volume cylinder, wherein the variable volume cylinder has an operating state when the refrigerant is compressed, and an idle state when the variable volume cylinder is not compressed;
at least one parallel cylinder is included in the plurality of cylinders, and an air suction port of the parallel cylinder is selectively communicated with an outlet end of the medium-pressure gas pipeline (102) or the gas-liquid separator (4);
the plurality of cylinders includes:
a first cylinder (50), wherein the first cylinder (50) is arranged in the compressor shell, the first cylinder (50) is provided with a first air suction port (20), and the first air suction port (20) is communicated with the outlet end of the gas-liquid separator (4);
a second cylinder (60), wherein the second cylinder (60) is arranged in the compressor housing, the second cylinder (60) is provided with a second air suction port (30), the second air suction port (30) is communicated with the outlet end of the gas-liquid separator (4), and the second cylinder (60) is a variable volume cylinder;
a third cylinder (70), the third cylinder (70) being disposed in the compressor housing, the third cylinder (70) having a third suction port (40), the third suction port (40) being selectively in communication with a medium pressure gas line (102) or an outlet end of a gas-liquid separator (4), the third cylinder (70) being a parallel cylinder;
the first cylinder (50) has a volume V P1 The volume of the second cylinder (60) is V P2 The volume of the third cylinder (70) is V P3 Wherein V is 0.05.ltoreq.V P3 /(V P1 +V P2 ) Not more than 0.25, and V not less than 0.5 P1 /V P2 ≤1。
2. The heat pump system of claim 1, further comprising:
a main air suction path (101), wherein a first end of the main air suction path (101) is communicated with an outlet end of the gas-liquid separator (4);
a first suction branch (1011), a first end of the first suction branch (1011) being in communication with a second end of the suction main path (101), a second end of the first suction branch (1011) being in communication with the first suction port (20);
-a second suction branch (1012), the first end of the second suction branch (1012) being in communication with the second end of the suction main circuit (101), the second end of the second suction branch (1012) being in communication with the second suction port (30);
-a third suction branch (1013), a first end of the third suction branch (1013) being in communication with a second end of the suction main (101) or the medium pressure gas line (102), the second end of the third suction branch (1013) being in communication with a third suction port (40).
3. The heat pump system of claim 2, further comprising:
-a first valve body (8), said first valve body (8) being located between the second end of the main suction line (101) and the junction of the first end of the third suction branch (1013) and the medium pressure gas line (102).
4. A heat pump system according to claim 3, further comprising:
and the second valve body (7) is arranged on the medium-pressure gas pipeline (102).
5. The heat pump system of claim 1, further comprising:
the inlet end of the condenser (2) is communicated with the exhaust port (80) of the compressor (1);
the outlet end of the evaporator (3) is communicated with the inlet end of the gas-liquid separator (4);
the first outlet end of the flash evaporator (9) is communicated with the medium-pressure gas pipeline (102), the second outlet end of the flash evaporator (9) is communicated with the inlet end of the evaporator (3), and the inlet end of the flash evaporator (9) is communicated with the outlet end of the condenser (2).
6. The heat pump system of claim 1, wherein the heat pump system further comprises:
the inlet end of the condenser (2) is communicated with the exhaust port (80) of the compressor (1);
the outlet end of the evaporator (3) is communicated with the inlet end of the gas-liquid separator (4);
the economizer (10), the first exit end of economizer (10) with middling pressure gas pipeline (102) are linked together, the second exit end of economizer (10) with the entrance point of evaporimeter (3), the first entrance point of economizer (10) with the exit end of condenser (2) is linked together, the second entrance point of economizer (10) with the exit end of condenser (2) is linked together.
7. The heat pump system of claim 6, further comprising:
-a first throttling device (5), said first throttling device (5) being located on a line communicating between said condenser (2) and a first inlet end of said economizer (10).
8. The heat pump system of claim 5, further comprising:
-a first throttling device (5), said first throttling device (5) being located on a line communicating between said condenser (2) and said flash vessel (9).
9. The heat pump system according to claim 8, wherein the plurality of condensers (2) are provided in parallel, the plurality of first throttle devices (5) are provided in plurality, and the plurality of first throttle devices (5) are provided in one-to-one correspondence with the plurality of condensers (2).
10. The heat pump system of claim 5, further comprising:
and the second throttling device (6) is arranged on a pipeline between the evaporator (3) and the flash evaporator (9).
11. The heat pump system of claim 6, further comprising:
-a second throttling device (6), said second throttling device (6) being arranged on a line between said evaporator (3) and said economizer (10).
12. An air conditioner comprising a heat pump system, characterized in that the heat pump system is the heat pump system according to any one of claims 1 to 11.
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| CN201811093618.1A CN108931021B (en) | 2018-09-19 | 2018-09-19 | Heat pump system and air conditioner with same |
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| CN201811093618.1A CN108931021B (en) | 2018-09-19 | 2018-09-19 | Heat pump system and air conditioner with same |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109708197B (en) * | 2018-12-27 | 2020-03-06 | 珠海格力电器股份有限公司 | Air conditioner system, air conditioner and method for controlling air conditioner |
| CN110608544A (en) * | 2019-09-19 | 2019-12-24 | 珠海格力电器股份有限公司 | Multi-cylinder multi-stage switching compressor double-source heat pump system, operation method thereof and air conditioner |
| CN111336703B (en) * | 2020-02-28 | 2022-08-02 | 广东美芝制冷设备有限公司 | Control device, refrigerant circulation system, and electric appliance |
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