CN206514563U - Air conditioning system unit and air conditioning system - Google Patents
Air conditioning system unit and air conditioning system Download PDFInfo
- Publication number
- CN206514563U CN206514563U CN201621404316.8U CN201621404316U CN206514563U CN 206514563 U CN206514563 U CN 206514563U CN 201621404316 U CN201621404316 U CN 201621404316U CN 206514563 U CN206514563 U CN 206514563U
- Authority
- CN
- China
- Prior art keywords
- subsystem
- inlet
- outlet
- economizer
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 56
- 239000003507 refrigerant Substances 0.000 claims abstract description 191
- 238000010438 heat treatment Methods 0.000 claims abstract description 79
- 238000010257 thawing Methods 0.000 claims abstract description 77
- 230000006835 compression Effects 0.000 claims abstract description 62
- 238000007906 compression Methods 0.000 claims abstract description 62
- 238000005057 refrigeration Methods 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 11
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 239000007788 liquid Substances 0.000 description 102
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 56
- 238000000034 method Methods 0.000 description 19
- 230000008569 process Effects 0.000 description 17
- 230000009467 reduction Effects 0.000 description 14
- 238000000926 separation method Methods 0.000 description 14
- 238000001704 evaporation Methods 0.000 description 11
- 239000013589 supplement Substances 0.000 description 11
- 238000002347 injection Methods 0.000 description 9
- 239000007924 injection Substances 0.000 description 9
- 230000001502 supplementing effect Effects 0.000 description 8
- 238000010521 absorption reaction Methods 0.000 description 6
- 230000008020 evaporation Effects 0.000 description 5
- 238000004781 supercooling Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 239000007921 spray Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The utility model provides an air conditioning system unit and air conditioning system. According to the utility model discloses an air conditioning system unit, including first subsystem and second subsystem; the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer, wherein the first compressor, the first outdoor heat exchanger, the first indoor heat exchanger and the first economizer are connected with one another to form a first compression cycle; the second subsystem comprises a second compressor, a second outdoor heat exchanger, a second indoor heat exchanger and a second economizer, wherein the second compressor, the second outdoor heat exchanger, the second indoor heat exchanger and the second economizer are connected with each other to form a second compression cycle; the air conditioning system unit further includes: selectively connecting the auxiliary circuit of the second economizer into the first compression cycle so that the refrigerant of the first compression cycle does not pass through the first defrosting pipeline of the first indoor heat exchanger any more; and selectively enabling the auxiliary path of the first economizer to be connected into the second compression cycle so that the refrigerant of the second compression cycle does not pass through the second defrosting pipeline of the second indoor heat exchanger any more, and realizing continuous heating.
Description
Technical Field
The utility model relates to an air conditioning field particularly, relates to an air conditioning system unit and air conditioning system.
Background
The air-cooled heat pump cold and hot water unit is used as a cold and hot source of a central air-conditioning system, and has the characteristics of convenience in installation, simplicity in operation, energy conservation, easiness in modularized integration and the like, so that the air-cooled heat pump cold and hot water unit is greatly developed in recent years, and the application range of the air-cooled heat pump cold and hot water unit is continuously widened. Most of the common air-cooled heat pump water chiller-heater units currently operate at the lowest ambient temperature of-15 ℃, and in order to widen the operation range of air-cooled air source heat pumps for heating, an enhanced vapor injection technology is mostly adopted. The lowest heating operation range of the air-cooled heat pump water chiller-heater unit adopting enhanced vapor injection can reach-25 ℃ to-30 ℃.
When the air-jet enthalpy-increasing air-cooled heat pump water chiller-heater unit heats in winter, the evaporation side fin heat exchanger and air exchange heat easily frosts on the surface of fins, and the fin heat exchange efficiency is influenced, so that the unit capacity and the reliability operation are influenced. At present, reverse circulation defrosting by reversing through a four-way valve is generally utilized, but the defrosting process needs to absorb heat from a water side, heating is stopped during defrosting, continuous heating cannot be realized, water temperature fluctuation is large, and the use comfort of a user is seriously influenced. The problem of continuous heating during defrosting is still not solved to the air injection enthalpy-increasing air-cooled heat pump water chiller-heater unit.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a can be at air conditioning system unit and air conditioning system who changes white in-process continuous heating.
The utility model provides an air conditioning system unit, which comprises a first subsystem and a second subsystem; the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer, wherein the first compressor, the first outdoor heat exchanger, the first indoor heat exchanger and the first economizer are connected with one another to form a first compression cycle; the second subsystem comprises a second compressor, a second outdoor heat exchanger, a second indoor heat exchanger and a second economizer, wherein the second compressor, the second outdoor heat exchanger, the second indoor heat exchanger and the second economizer are connected with each other to form a second compression cycle; the air conditioning system unit further includes: selectively connecting the auxiliary circuit of the second economizer into the first compression cycle so that the refrigerant of the first compression cycle does not pass through the first defrosting pipeline of the first indoor heat exchanger any more; and selectively enabling the auxiliary circuit of the first economizer to be connected into the second compression cycle so that the refrigerant of the second compression cycle does not pass through the second defrosting pipeline of the second indoor heat exchanger any more.
Further, the first compression cycle has a first junction and a second junction between the first outdoor heat exchanger and the first indoor heat exchanger; the second compression cycle has a third junction and a fourth junction between the second outdoor heat exchanger and the second indoor heat exchanger; the inlet pipe of the first economizer comprises an inlet joint, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint; the inlet end of the heating inlet branch pipe is connected with the first connection point, the inlet end of the refrigerating inlet branch pipe is connected with the second connection point, the outlet end of the main road inlet pipe is connected with the inlet end of the main road of the first economizer, the outlet end of the auxiliary road inlet pipe is connected with the auxiliary road inlet of the first economizer, and the auxiliary road inlet pipe is provided with an auxiliary road throttling device in series; the outlet pipe of the main path of the first economizer comprises an outlet main pipe, a heating outlet branch pipe and a refrigerating outlet branch pipe, wherein the heating outlet branch pipe and the refrigerating outlet branch pipe are connected with the outlet main pipe; the inlet pipe of the second economizer comprises an inlet joint, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint; the inlet end of the heating inlet branch pipe is connected with the third connecting point, the inlet end of the refrigerating inlet branch pipe is connected with the fourth connecting point, the outlet end of the main path inlet pipe is connected with the inlet end of the main path of the second economizer, the outlet end of the auxiliary path inlet pipe is connected with the auxiliary path inlet of the second economizer, and an auxiliary path throttling device is arranged on the auxiliary path inlet pipe in series; the exit tube of the main path of the second economizer comprises an outlet main tube, a heating outlet branch tube and a cooling outlet branch tube, wherein the heating outlet branch tube and the cooling outlet branch tube are connected with the outlet main tube, the outlet end of the heating outlet branch tube is connected with a fourth contact, the outlet end of the cooling outlet branch tube is connected with a third contact, the outlet main tube is provided with a main path throttling device in series, and the heating outlet branch tube and the cooling outlet branch tube are respectively provided with a one-way valve in series.
Further, the first defrosting pipeline comprises a first inlet pipe and a first outlet pipe, wherein the inlet end of the first inlet pipe is connected with the outlet end of the main path throttling device of the first economizer through a control valve, and the outlet end of the first inlet pipe is connected with the inlet end of the auxiliary path of the second economizer; the inlet end of the first outlet pipe is connected with the outlet end of the auxiliary path of the second economizer through a control valve, and the outlet end of the first outlet pipe is connected between the first indoor heat exchanger and the first compressor through the control valve; the second defrosting pipeline comprises a second inlet pipe and a second outlet pipe, wherein the inlet end of the second inlet pipe is connected with the outlet end of the main path throttling device of the second economizer through a control valve, and the outlet end of the second inlet pipe is connected with the inlet end of the auxiliary path of the first economizer; the inlet end of the second outlet pipe is connected with the outlet end of the auxiliary path of the first economizer through a control valve, and the outlet end of the second outlet pipe is connected between the second indoor heat exchanger and the second compressor through the control valve.
Furthermore, a control valve positioned at the upstream of the auxiliary way throttling device is also arranged on an auxiliary way inlet pipe of the first economizer in series; a control valve positioned at the upstream of the auxiliary way throttling device is also arranged on the auxiliary way inlet pipe of the second economizer in series; the first defrosting pipeline comprises a first inlet pipe and a first outlet pipe, wherein the inlet end of the first inlet pipe is connected with a refrigeration inlet branch pipe of the first economizer through a control valve, the outlet end of the first inlet pipe is connected between an auxiliary path throttling device of an auxiliary path inlet pipe of the second economizer and the control valve, the inlet end of the first outlet pipe is connected with the outlet end of an auxiliary path of the second economizer through the control valve, and the outlet end of the first outlet pipe is connected between the first indoor heat exchanger and the first compressor through the control valve; the second defrosting pipeline comprises a second inlet pipe and a second outlet pipe, wherein the inlet end of the second inlet pipe is connected with a refrigeration inlet branch pipe of a second economizer through a control valve, and the outlet end of the first inlet pipe is connected between an auxiliary path throttling device of an auxiliary path inlet pipe of the first economizer and the control valve; the inlet end of the second outlet pipe is connected with the outlet end of the auxiliary path of the first economizer through a control valve, and the outlet end of the second outlet pipe is connected between the second indoor heat exchanger and the second compressor through the control valve.
Further, the control valve is a three-way control valve or a two-way control valve.
Furthermore, the first indoor heat exchanger and the second indoor heat exchanger are integrated into an integrated heat exchanger, and the integrated heat exchanger is provided with a first refrigerant inlet and a first refrigerant outlet which are connected into the first compression cycle, and a second refrigerant inlet and a second refrigerant outlet which are connected into the second compression cycle.
The utility model also provides an air conditioning system, including at least one aforementioned air conditioning system unit.
Further, the indoor heat exchangers of all the air conditioning system units are integrated into one total heat exchanger.
According to the air conditioning system unit and the air conditioning system of the utility model, the first subsystem and the second subsystem respectively defrost, in the defrosting process of the first subsystem, the auxiliary path of the second economizer is connected into the first compression cycle through the first defrosting pipeline so that the refrigerant of the first compression cycle does not pass through the first indoor heat exchanger any more, and the second subsystem heats normally; the defrosting process of the second subsystem is reversed; therefore, the whole air conditioning system unit is ensured to continuously heat, the water temperature fluctuation is reduced, and the use comfort of a user is improved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification. In the drawings:
fig. 1 is a schematic view of a first embodiment of an air conditioning system unit according to the present invention;
fig. 2 is a schematic view of a second embodiment of an air conditioning system unit according to the invention;
fig. 3 is a schematic view of a third embodiment of an air conditioning system unit according to the invention;
fig. 4 is a schematic view of a fourth embodiment of an air conditioning system unit according to the invention;
fig. 5 is a schematic view of a fifth embodiment of an air conditioning system unit according to the invention.
Detailed Description
The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
As shown in fig. 1 to 5, an air conditioning system unit according to the present invention includes a first subsystem and a second subsystem; the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer, wherein the first compressor, the first outdoor heat exchanger, the first indoor heat exchanger and the first economizer are connected with one another to form a first compression cycle; the second subsystem comprises a second compressor, a second outdoor heat exchanger, a second indoor heat exchanger and a second economizer, wherein the second compressor, the second outdoor heat exchanger, the second indoor heat exchanger and the second economizer are connected with each other to form a second compression cycle; the air conditioning system unit further includes: selectively connecting the auxiliary circuit of the second economizer into the first compression cycle so that the refrigerant of the first compression cycle does not pass through the first defrosting pipeline of the first indoor heat exchanger any more; and selectively enabling the auxiliary circuit of the first economizer to be connected into the second compression cycle so that the refrigerant of the second compression cycle does not pass through the second defrosting pipeline of the second indoor heat exchanger any more. According to the air conditioning system unit and the air conditioning system of the utility model, the first subsystem and the second subsystem respectively defrost, in the defrosting process of the first subsystem, the auxiliary path of the second economizer is connected into the first compression cycle through the first defrosting pipeline so that the refrigerant of the first compression cycle does not pass through the first indoor heat exchanger any more, and the second subsystem heats normally; the defrosting process of the second subsystem is reversed; that is, when one subsystem is defrosted, the other subsystem is heated. The heating subsystem economizer is used as an evaporator of the defrosting subsystem, defrosting heat of the defrosting subsystem is derived from heat released by a compressor of the defrosting subsystem to do work and high-temperature liquid refrigerant of the other heating subsystem to be supercooled, and the heating subsystem and the defrosting subsystem realize energy complementation so as to reasonably utilize system energy. When the system is defrosted, heat is not absorbed from the indoor heat exchanger, so that the whole air conditioning system unit is ensured to continuously heat, the fluctuation of water temperature is reduced, and the use comfort of a user is improved.
It should be noted that, in the present invention, the outdoor heat exchanger and the indoor heat exchanger are only functionally expressed, the indoor heat exchanger should be understood as a heat exchanger acting indoors (cooling or heating), and the outdoor heat exchanger should also be understood as a heat exchanger absorbing or dissipating heat outdoors, and does not refer to a specific installation position being indoors or outdoors. In a small household air-cooled heat pump chiller-heater unit or air conditioner, an indoor heat exchanger is arranged indoors, and an outdoor heat exchanger is arranged outdoors. However, because the large commercial air-cooled heat pump water chiller-heater unit is generally an integral machine, and is integrally installed outdoors, the air-cooled heat pump water chiller-heater unit is not divided into an indoor space and an outdoor space from the installation position, in the large commercial air-cooled heat pump water chiller-heater unit, the air-side heat exchanger corresponds to the outdoor heat exchanger, the water-side heat exchanger corresponds to the indoor heat exchanger, and the water-side heat exchanger exchanges heat with the indoor space through a cold and hot water pipeline, so that the indoor.
Specifically, as shown in conjunction with fig. 4 and 5, the first compression cycle has a first junction a and a second junction b between the first outdoor heat exchanger and the first indoor heat exchanger; the second compression cycle has a third junction d and a fourth junction e between the second outdoor heat exchanger and the second indoor heat exchanger; the inlet pipe of the first economizer comprises an inlet joint c, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint c, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint c; the inlet end of the heating inlet branch pipe is connected with the first contact a, the inlet end of the refrigerating inlet branch pipe is connected with the second contact b, the outlet end of the main road inlet pipe is connected with the inlet end of the main road of the first economizer, the outlet end of the auxiliary road inlet pipe is connected with the auxiliary road inlet of the first economizer, and an auxiliary road throttling device is arranged on the auxiliary road inlet pipe in series; the outlet pipe of the main path of the first economizer comprises an outlet main pipe, a heating outlet branch pipe and a refrigerating outlet branch pipe, wherein the heating outlet branch pipe and the refrigerating outlet branch pipe are connected with the outlet main pipe; the inlet pipe of the second economizer comprises an inlet joint f, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint f, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint f; the inlet end of the heating inlet branch pipe is connected with the third contact d, the inlet end of the refrigerating inlet branch pipe is connected with the fourth contact e, the outlet end of the main path inlet pipe is connected with the inlet end of the main path of the second economizer, the outlet end of the auxiliary path inlet pipe is connected with the auxiliary path inlet of the second economizer, and an auxiliary path throttling device is arranged on the auxiliary path inlet pipe in series; the exit tube of the main path of the second economizer comprises an outlet main tube, a heating outlet branch tube and a cooling outlet branch tube, wherein the heating outlet branch tube and the cooling outlet branch tube are connected with the outlet main tube, the outlet end of the heating outlet branch tube is connected with a fourth contact e, the outlet end of the cooling outlet branch tube is connected with a third contact d, the outlet main tube is provided with a main path throttling device in series, and the heating outlet branch tube and the cooling outlet branch tube are respectively provided with a one-way valve in series.
It should be noted that, as shown in fig. 1 and fig. 2, in the present invention, the first indoor heat exchanger and the second indoor heat exchanger can be integrated into an integrated heat exchanger, and the integrated heat exchanger has a first refrigerant inlet and a first refrigerant outlet connected to the first compression cycle and a second refrigerant inlet and a second refrigerant outlet connected to the second compression cycle. Make an indoor heat exchanger of two subsystems sharing, compare in figure 4 and figure 5 with the mode that two subsystems adopted indoor heat exchanger respectively, can solve the indoor heat exchanger that the subsystem of defrosting corresponds and do not have the problem of heat input, also change the frost in-process promptly, the heating subsystem supplies heat to the indoor heat exchanger of two subsystems sharing to can reduce the temperature fluctuation of the indoor side of whole air conditioning system unit more effectively, guarantee continuous heating, improve the travelling comfort.
The specific working principle of the embodiments of the present invention will be specifically described by taking a large commercial air-cooled heat pump water chiller-heater unit as an example with reference to fig. 1 to 5.
A first embodiment system schematic is shown in fig. 1. In fig. 1, 11 is a compressor of the first subsystem, 1101 is a compressor suction port of the first subsystem, 1102 is a compressor discharge port of the first subsystem, and 1103 is a compressor supplement port of the first subsystem; 12 is a four-way valve of the first subsystem; 13 is a first three-way valve of the first subsystem; 04 is a system water side heat exchanger (an indoor side heat exchanger, which is shared by two subsystems), 0401 is a connecting water side heat exchanger air pipe port of the first subsystem, 0402 is a connecting water side heat exchanger liquid pipe port of the first subsystem; 15 is a first one-way valve of the first subsystem; 16 is an economizer of the first subsystem, 1601 is an economizer main path inlet of the first subsystem, 1602 is an economizer main path outlet of the first subsystem, 1603 is an economizer auxiliary path inlet of the first subsystem, 1604 is an economizer auxiliary path outlet of the first subsystem; 17 is a main path throttle valve of the first subsystem; 18 is a bypass throttle valve of the first subsystem; 19 is a second three-way valve of the first subsystem; 110 is a third three-way valve of the first subsystem; 111 is a second one-way valve of the first subsystem; 112 is a third one-way valve of the first subsystem; 113 is a fourth one-way valve of the first subsystem; 114 is a wind side fin heat exchanger (outdoor heat exchanger) of the first subsystem, 11401 is a wind side fin heat exchanger air pipe orifice of the first subsystem, and 11402 is a wind side fin heat exchanger liquid pipe orifice of the first subsystem; 115 is the gas-liquid separator of the first subsystem, 11501 is the gas-liquid separator inlet of the first subsystem, and 11502 is the gas-liquid separator outlet of the first subsystem. 116 is a fifth one-way valve of the first subsystem.
Similarly, in fig. 1, 21 is the compressor of the second subsystem, 2101 is the compressor suction of the second subsystem, 2102 is the compressor discharge of the second subsystem, 2103 is the compressor supply of the second subsystem; 22 is a four-way valve of the second subsystem; 23 is a first three-way valve of the second subsystem; 04 is a system water side heat exchanger (an indoor side heat exchanger, which is shared by two subsystems), 0403 is a connecting water side heat exchanger air pipe port of the second subsystem, 0404 is a connecting water side heat exchanger liquid pipe port of the second subsystem; 25 is a first one-way valve of the second subsystem; 26 is an economizer of the second subsystem, 2601 is an economizer main path inlet of the second subsystem, 2602 is an economizer main path outlet of the second subsystem, 2603 is an economizer auxiliary path inlet of the second subsystem, and 2604 is an economizer auxiliary path outlet of the second subsystem; 27 is a main path throttle valve of the second subsystem; 28 is a bypass throttle valve of the second subsystem; 29 is a second three-way valve of the second subsystem; 210 is a third three-way valve of the second subsystem; 211 is a second one-way valve of the second subsystem; 212 is a third one-way valve of the second subsystem; 213 is a fourth check valve of the second subsystem; 214 is a wind side fin heat exchanger of the second subsystem, 21401 is a wind side fin heat exchanger air pipe orifice of the second subsystem, and 21402 is a wind side fin heat exchanger liquid pipe orifice of the second subsystem; 215 is the gas liquid separator of the second subsystem, 21501 is the gas liquid separator inlet of the second subsystem, 21502 is the gas liquid separator outlet of the second subsystem. 216 is a fifth one-way valve of the second subsystem.
The three-way valve is used for communicating two ends of the three-way valve and disconnecting the third end. Taking the first three-way valve 13 of the first subsystem as an example, the following is described: when the ends 1301 and 1302 are communicated, the end 1303 is disconnected; when the ends 1301 and 1303 are communicated, the end 1302 is disconnected; when the 1302 and 1303 ends are connected, the 1301 end is disconnected. The rest is analogized in the same way.
The system has three basic modes of refrigeration, heating and defrosting, and the refrigerant circulation flow of each mode is described as follows:
1. a refrigeration mode:
the D end and the E end of the four-way valve 12 of the first subsystem are communicated, the S end and the C end are communicated, the 11001 end and the 11003 end of the third three-way valve 110 of the first subsystem are communicated, the 1902 end and the 1903 end of the second three-way valve 19 of the first subsystem are communicated, the 1303 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the E end and the S end and the C end of the four-way valve 22 of the second subsystem are communicated, the 21001 end and the 21003 end of the third three-way valve 210 of the second subsystem are communicated, the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem are communicated, and the 2301 end and the 2302 end of the first three-way valve 23 of the second. When in refrigeration, the two subsystems refrigerate independently.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the end D and the end E of the four-way valve 12 of the first subsystem, enters the wind side fin heat exchanger 114 of the first subsystem from the end 11401, releases heat to air, is condensed into a high-temperature liquid refrigerant, flows out from the end 11402, passes through the second one-way valve 111 of the first subsystem, and is then divided into two paths of refrigerant, namely a main path and an auxiliary path. The main path high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through 1601 end to release heat and cool into super-cooled refrigerant. The subcooled refrigerant from the 1602 end passes through the main path throttle valve 17 of the first subsystem for throttling and pressure reduction, passes through the 11001 end and the 11003 end of the third three-way valve of the first subsystem, passes through the third one-way valve 112 of the first subsystem, enters the water side heat exchanger 04 from the 0402 end for evaporation, heat absorption and refrigeration, the low-temperature low-pressure refrigerant from the 0401 end passes through the 1303 end and the 1301 end of the first three-way valve 13 of the first subsystem, passes through the C end and the S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 115 of the first subsystem from the 11501 end for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant from the 11502 end enters the compressor 11 of the first subsystem through the air suction port 1101 of the compressor 11 of the first subsystem for compression, thereby completing the main path. The high-temperature liquid refrigerant of the auxiliary circuit is throttled and decompressed into a gas-liquid two-phase refrigerant through the auxiliary circuit throttle valve 18 of the first subsystem, and enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate into a gaseous refrigerant. The gaseous refrigerant from the 1604 passes through 1902 end and 1903 end of the second three-way valve 19 of the first sub-system, and then passes through the fifth one-way valve 116 of the first sub-system to enter the compressor 11 of the first sub-system through the gas supplementing port 1103 of the compressor 11 of the first sub-system for compression, thereby completing the auxiliary gas supplementing circulation. The above process constitutes a refrigeration cycle of the first subsystem.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the end D and the end E of the four-way valve 22 of the second subsystem, enters the wind side fin heat exchanger 214 of the second subsystem from the end 21401, releases heat to air, is condensed into a high-temperature liquid refrigerant, flows out of the end 21402, passes through the second one-way valve 211 of the second subsystem, and is then divided into two paths of refrigerant, namely a main path and a secondary path. The main path high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to release heat and be cooled into a supercooled refrigerant. The subcooled refrigerant from the 2602 end passes through the main path throttle valve 27 of the second subsystem for throttling and pressure reduction, passes through the 21001 end and 21003 end of the third three-way valve of the second subsystem, passes through the third one-way valve 212 of the second subsystem, enters the water side heat exchanger 04 from the 0404 end for evaporation and heat absorption and refrigeration, the low-temperature low-pressure refrigerant from the 0403 end passes through the 2301 end and 2302 end of the first three-way valve 23 of the second subsystem, passes through the C end and S end of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 215 of the second subsystem by 21501 for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant from the 21502 end enters the compressor 21 of the second subsystem through the air suction port 2101 of the compressor 21 of the second subsystem for compression, thereby completing the main path refrigeration cycle. The high-temperature liquid refrigerant of the auxiliary circuit is throttled and decompressed into a gas-liquid two-phase refrigerant through an auxiliary circuit throttle valve 28 of the second subsystem, and enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate into a gaseous refrigerant. The gaseous refrigerant from the end 2604 passes through the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem, and then passes through the fifth one-way valve 216 of the second subsystem and enters the compressor 21 of the second subsystem through the air supplement port 2103 of the compressor 21 of the second subsystem for compression, thereby completing the auxiliary air supplement circulation. The above process constitutes the refrigeration cycle of the second subsystem.
2. Heating circulation:
the D end and the C end of the four-way valve 12 of the first subsystem are communicated, the S end and the E end are communicated, the 11001 end and the 11003 end of the third three-way valve 110 of the first subsystem are communicated, the 1902 end and the 1903 end of the second three-way valve 19 of the first subsystem are communicated, the 1303 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the C end and the S end and the E end of the four-way valve 22 of the second subsystem are communicated, the 21001 end and the 21003 end of the third three-way valve 210 of the second subsystem are communicated, the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem are communicated, and the 2301 end and the 2302 end of the first three-way valve 23 of the second. When heating, the two subsystems heat independently.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the end D and the end C of the four-way valve 12 of the first subsystem, passes through the end 1301 and the end 1303 of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the end 0401, is discharged to water and condensed into high-temperature liquid refrigerant, passes through the first one-way valve 15 of the first subsystem after exiting from the end 0402, and is divided into two paths of refrigerant, namely a main path and an auxiliary path. The main path high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through 1601 end to release heat and cool into super-cooled refrigerant. The subcooled refrigerant coming out of the 1602 end passes through the main path throttle valve 17 of the first subsystem for throttling and pressure reduction, passes through the 11001 end and the 11003 end of the third three-way valve of the first subsystem, passes through the fourth one-way valve 113 of the first subsystem, enters the wind side fin heat exchanger 114 of the first subsystem from the 11402 end for absorbing heat from air and evaporating into a low-temperature low-pressure refrigerant, comes out of the 11401 end and then passes through the E end and the S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 115 of the first subsystem from the 11501 end for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant comes out of the 11502 end and enters the compressor 1101 of the first subsystem through the air suction port of the compressor 11 of the first subsystem for compression, so as to finish. The high-temperature liquid refrigerant of the auxiliary circuit is throttled and decompressed into a gas-liquid two-phase refrigerant through the auxiliary circuit throttle valve 18 of the first subsystem, and enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate into a gaseous refrigerant. The gaseous refrigerant from the 1604 passes through 1902 end and 1903 end of the second three-way valve 19 of the first sub-system, and then passes through the fifth one-way valve 116 of the first sub-system to enter the compressor 11 of the first sub-system through the gas supplementing port 1103 of the compressor 11 of the first sub-system for compression, thereby completing the auxiliary gas supplementing circulation. The above process constitutes a heating cycle of the first subsystem.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the end D and the end C of the four-way valve 22 of the second subsystem, passes through the end 2302 and the end 2301 of the first three-way valve 23 of the second subsystem, enters the water side heat exchanger 04 from the end 0403, is discharged to water and condensed into high-temperature liquid refrigerant, passes through the first one-way valve 25 of the second subsystem after exiting from the end 0404, and is then divided into two paths of refrigerant of a main path and a secondary path. The main path high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to release heat and be cooled into a supercooled refrigerant. The subcooled refrigerant from the 2602 end passes through the main path throttle valve 27 of the second subsystem for throttling and pressure reduction, passes through the 21001 end and the 21003 end of the third three-way valve of the second subsystem, passes through the fourth one-way valve 213 of the second subsystem, enters the wind side fin heat exchanger 214 of the second subsystem from the 21402 end for absorbing heat from air and evaporating into a low-temperature low-pressure refrigerant, exits from the 21401 end and passes through the E end and the S end of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 215 of the second subsystem for gas-liquid separation from 21501, and the low-temperature low-pressure gaseous refrigerant exits from the 21502 end and enters the compressor 21 of the second subsystem through the air inlet 2101 of the compressor 21 of the second subsystem for compression, thereby completing the main path heating cycle. The high-temperature liquid refrigerant of the auxiliary circuit is throttled and decompressed into a gas-liquid two-phase refrigerant through the auxiliary circuit throttle valve 28 of the second subsystem, and enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate into a gaseous refrigerant. The gaseous refrigerant from the end 2604 passes through the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem, and then passes through the fifth one-way valve 216 of the second subsystem and enters the compressor 21 of the second subsystem through the air supplement port 2103 of the compressor 21 of the second subsystem for compression, thereby completing the auxiliary air supplement circulation. The above process constitutes a heating cycle of the second subsystem.
3. Defrosting circulation:
3.1, defrosting of the first subsystem and heating of the second subsystem (without enthalpy injection)
The D end and the E end of the four-way valve 12 of the first subsystem are communicated, the S end and the C end are communicated, the 11001 end and the 11002 end of the third three-way valve 110 of the first subsystem are communicated, the 1302 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the auxiliary path throttle valve 18 of the first subsystem is closed and is not communicated, the D end and the C end and the S end and the E end of the four-way valve 22 of the second subsystem are communicated, the 21001 end and the 21003 end of the third three-way valve 210 of the second subsystem are communicated, the 2902 end and the 2901 end of the second three-way valve 29 of the second subsystem are communicated, the 2302 end and the 2301 end of the first three-way valve 23 of the second subsystem are communicated, and the auxiliary path throttle valve 28 of the second. When the first subsystem defrosts, the second subsystem heats (does not inject enthalpy).
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the D end and the E end of the four-way valve 12 of the first subsystem, enters the wind side fin heat exchanger 114 of the first subsystem from the 11401 end to release heat and defrost, is condensed into a high-temperature liquid refrigerant, exits from the 11402 end to pass through the second one-way valve 111 of the first subsystem, and then enters the economizer 16 of the first subsystem through the 1601 end to release heat and cool into a supercooled refrigerant. The subcooled refrigerant from the 1602 end passes through the throttle valve 17 of the main path of the first subsystem for throttling and pressure reduction, passes through the 11001 end and the 11002 end of the third three-way valve of the first subsystem, enters the economizer 26 of the second subsystem from the 2603 end for absorbing heat and evaporating into a low-temperature low-pressure refrigerant, passes through the 2902 end and the 2901 end of the second three-way valve 29 of the second subsystem after passing out from the 2604 end, passes through the 1302 end and the 1301 end of the first three-way valve 13 of the first subsystem, passes through the C end and the S end of the four-way valve 12 of the first subsystem after passing out from the 1301 end, enters the gas-liquid separator 115 of the first subsystem from the 11501 end for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant enters the compressor 11 of the first subsystem through the air suction port 1101 of the compressor 11 of the first subsystem for compression, thereby completing the defrosting cycle of.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the D end and the C end of the four-way valve 22 of the second subsystem, passes through the 2302 end and the 2301 end of the first three-way valve 23 of the second subsystem, enters the water side heat exchanger 04 from the 0403 end, is radiated and condensed to water to form high-temperature liquid refrigerant, is discharged from the 0404 end and passes through the first one-way valve 25 of the second subsystem, and the high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be radiated and cooled to form supercooled refrigerant. The subcooled refrigerant from the 2602 end passes through the main throttle valve 27 of the second subsystem for throttling and pressure reduction, passes through the 21001 end and the 21003 end of the third three-way valve of the second subsystem, passes through the fourth one-way valve 213 of the second subsystem, enters the wind side fin heat exchanger 214 of the second subsystem from the 21402 end for absorbing heat from air and evaporating into a low-temperature low-pressure refrigerant, exits from the 21401 end and passes through the E end and the S end of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 215 of the second subsystem for gas-liquid separation from 21501, and the low-temperature low-pressure gaseous refrigerant exits from the 21502 end and enters the compressor 21 of the second subsystem through the air inlet 2101 of the compressor 21 of the second subsystem for compression, thereby completing the heating (no-injection enthalpy) cycle of the second subsystem.
When the first subsystem defrosts, the second subsystem heats normally. The economizer 26 of the second subsystem is used as an evaporator of the defrosting first subsystem, defrosting heat of the defrosting first subsystem is heat generated by supercooling the high-temperature liquid refrigerant of the second subsystem which works and heats the compressor 11 per se in the economizer 26 of the second subsystem, and the heating second subsystem and the defrosting first subsystem realize energy complementation so as to reasonably utilize system energy. And the first subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating can be ensured during defrosting of the whole system.
3.2 defrosting the second subsystem, heating the first subsystem (without enthalpy)
The D end and the C end of the four-way valve 12 of the first subsystem are communicated, the S end and the E end are communicated, the 11001 end and the 11003 end of the third three-way valve 110 of the first subsystem are communicated, the 1902 end and the 1901 end of the second three-way valve 19 of the first subsystem are communicated, the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem are communicated, and the auxiliary throttle valve 18 of the first subsystem is closed and is not communicated. The D end and the E end of the four-way valve 22 of the second subsystem are communicated, the S end and the C end are communicated, the 21001 end and the 21002 end of the third three-way valve 210 of the second subsystem are communicated, the 2303 end and the 2302 end of the first three-way valve 23 of the second subsystem are communicated, and the auxiliary path throttle valve 28 of the second subsystem is closed and is not communicated. When the second subsystem defrosts, the first subsystem heats (does not spray enthalpy).
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the end D and the end E of the four-way valve 22 of the second subsystem, enters the wind side fin heat exchanger 214 of the second subsystem from the end 21401 to release heat and defrost, is condensed into a high-temperature liquid refrigerant, exits from the end 21402 to pass through the second one-way valve 211 of the second subsystem, and then enters the economizer 26 of the second subsystem through the end 2601 to release heat and cool into a sub-cooled refrigerant. The subcooled refrigerant from the 2602 end passes through the main throttle 27 of the second subsystem for throttling and pressure reduction, passes through the 21001 and 21002 ends of the third three-way valve of the second subsystem, enters the economizer 16 of the first subsystem from the 1603 end for absorbing heat and evaporating into a low-temperature and low-pressure refrigerant, passes through the 1902 and 1901 ends of the second three-way valve 19 of the first subsystem after passing through the 1604 end, passes through the 2303 and 2302 ends of the first three-way valve 23 of the second subsystem, passes through the C and S ends of the four-way valve 22 of the second subsystem after passing through the 2302 end, enters the gas-liquid separator 215 of the second subsystem from the 21501 end for gas-liquid separation, and the low-temperature and low-pressure gaseous refrigerant passes through the air suction port 2101 of the compressor 21 of the second subsystem from the 21502 end for compression, thereby completing the defrosting cycle of the second subsystem.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the end D and the end C of the four-way valve 12 of the first subsystem, passes through the end 1301 and the end 1303 of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the end 0401, is discharged to water and condensed into a high-temperature liquid refrigerant, passes through the first one-way valve 15 of the first subsystem after exiting from the end 0402, and enters the economizer 16 of the first subsystem through the end 1601 to release heat and cool into a supercooled refrigerant. The subcooled refrigerant from the 1602 end passes through the main path throttle valve 17 of the first subsystem for throttling and pressure reduction, passes through the 11001 end and the 11003 end of the third three-way valve of the first subsystem, passes through the fourth one-way valve 113 of the first subsystem, enters the wind side fin heat exchanger 114 of the first subsystem from the 11402 end for absorbing heat from air and evaporating into a low-temperature low-pressure refrigerant, exits from the 11401 end and passes through the E end and the S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 115 of the first subsystem for gas-liquid separation from 11501, and the low-temperature low-pressure gaseous refrigerant exits from the 11502 end and enters the compressor 1101 of the first subsystem through the air suction port of the compressor 11 of the first subsystem for compression, so that the heating (no-injection enthalpy) cycle of the first subsystem.
When the second subsystem defrosts, the first subsystem heats normally. The economizer 16 of the first subsystem is used as an evaporator of the defrosting second subsystem, defrosting heat of the defrosting second subsystem is heat generated by supercooling the high-temperature liquid refrigerant of the first subsystem which is used for applying work by the compressor 21 and heating in the economizer 16 of the first subsystem, and the heating first subsystem and the defrosting second subsystem realize energy complementation so as to reasonably utilize system energy. And the second subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating can be ensured during defrosting of the whole system.
A second embodiment of the book utility model will be specifically described with reference to the schematic diagram of the second embodiment shown in fig. 2.
In fig. 2, 11 is a compressor of the first sub-system, 1101 is a compressor suction port of the first sub-system, 1102 is a compressor discharge port of the first sub-system, and 1103 is a compressor supplement port of the first sub-system; 12 is a four-way valve of the first subsystem; 13 is a first three-way valve of the first subsystem; 04 is a system water side heat exchanger (shared by all subsystems), 0401 is a connecting water side heat exchanger air pipe opening of the first subsystem, 0402 is a connecting water side heat exchanger liquid pipe opening of the first subsystem; 15 is a first one-way valve of the first subsystem; 16 is an economizer of the first subsystem, 1601 is an economizer main path inlet of the first subsystem, 1602 is an economizer main path outlet of the first subsystem, 1603 is an economizer auxiliary path inlet of the first subsystem, 1604 is an economizer auxiliary path outlet of the first subsystem; 17 is a main path throttle valve of the first subsystem; 18 is a bypass throttle valve of the first subsystem; 19 is a second three-way valve of the first subsystem; 110 is the ball valve of the first subsystem; 111 is a second one-way valve of the first subsystem; 112 is a third one-way valve of the first subsystem; 113 is a fourth one-way valve of the first subsystem; 114 is a third three-way valve of the first subsystem; 115 is a wind side fin heat exchanger of the first subsystem, 11501 is a wind side fin heat exchanger air pipe opening of the first subsystem, and 11502 is a wind side fin heat exchanger liquid pipe opening of the first subsystem; 116 is the gas-liquid separator of the first subsystem, 11601 is the gas-liquid separator inlet of the first subsystem, 11602 is the gas-liquid separator outlet of the first subsystem. 117 is a fifth one-way valve of the first subsystem.
Similarly, in fig. 2, 21 is a compressor of the second subsystem, 2101 is a compressor suction port of the second subsystem, 2102 is a compressor discharge port of the second subsystem, and 2103 is a compressor supplement port of the second subsystem; 22 is a four-way valve of the second subsystem; 23 is a first three-way valve of the second subsystem; 04 is a system water side heat exchanger (shared by all subsystems), 0403 is a connecting water side heat exchanger air pipe opening of the second subsystem, 0404 is a connecting water side heat exchanger liquid pipe opening of the second subsystem; 25 is a first one-way valve of the second subsystem; 26 is an economizer of the second subsystem, 2601 is an economizer main path inlet of the second subsystem, 2602 is an economizer main path outlet of the second subsystem, 2603 is an economizer auxiliary path inlet of the second subsystem, and 2604 is an economizer auxiliary path outlet of the second subsystem; 27 is a main path throttle valve of the second subsystem; 28 is a bypass throttle valve of the second subsystem; 29 is a second three-way valve of the second subsystem; 210 is the ball valve of the second subsystem; 211 is a second one-way valve of the second subsystem; 212 is a third one-way valve of the second subsystem; 213 is a fourth check valve of the second subsystem; 214 is a third three-way valve of the second subsystem; 215 is the air side fin heat exchanger of the second subsystem, 21501 is the air pipe opening of the air side fin heat exchanger of the second subsystem, and 21502 is the liquid pipe opening of the air side fin heat exchanger of the second subsystem; 216 is the gas-liquid separator of the second subsystem, 21601 is the gas-liquid separator inlet of the second subsystem, and 21602 is the gas-liquid separator outlet of the second subsystem. 217 is a fifth one-way valve of the second subsystem.
The three-way valve is used for communicating two ends of the three-way valve and disconnecting the third end. Taking the first three-way valve 13 of the first subsystem as an example, the following is described: when the ends 1301 and 1302 are communicated, the end 1303 is disconnected; when the ends 1301 and 1303 are communicated, the end 1302 is disconnected; when the 1302 and 1303 ends are connected, the 1301 end is disconnected. The rest is analogized in the same way.
The system has three basic modes of refrigeration, heating and defrosting, and the refrigerant circulation flow of each mode is described as follows:
1. refrigeration cycle:
the D end and the E end of the four-way valve 12 of the first subsystem are communicated, the S end and the C end are communicated, the ball valve 110 of the first subsystem is communicated in an open mode, the 11402 end and the 11403 end of the third three-way valve 114 of the first subsystem are communicated, the 1902 end and the 1903 end of the second three-way valve 19 of the first subsystem are communicated, the 1303 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the E end and the S end and the C end of the four-way valve 22 of the second subsystem are communicated, the ball valve 210 of the second subsystem is communicated in an open mode, the 21402 end and the 21403 end of the third three-way valve 214 of the second subsystem are communicated, the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem are communicated, and the 2301 end and the 2302. When in refrigeration, the two subsystems refrigerate independently.
High-temperature and high-pressure refrigerant working media discharged from an exhaust port 1102 of a compressor 11 of the first subsystem pass through a D end and an E end of a four-way valve 12 of the first subsystem, enter a wind side fin heat exchanger 115 of the first subsystem from an 11501 end to release heat to air and are condensed into high-temperature liquid refrigerants, are discharged from an 11502 end, pass through 11402 ends and 11403 ends of a third three-way valve 114 of the first subsystem, pass through a second one-way valve 111 of the first subsystem, and are divided into two paths of refrigerants of a main path and an auxiliary path. The main path high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through 1601 end to release heat and cool into super-cooled refrigerant. The subcooled refrigerant coming out of the 1602 end passes through a main path throttling valve 17 of the first subsystem for throttling and pressure reduction, and enters the water side heat exchanger 04 from the 0402 end through a third one-way valve 112 of the first subsystem for evaporation, heat absorption and refrigeration, the low-temperature low-pressure refrigerant coming out of the 0401 end passes through the 1303 end and the 1301 end of a first three-way valve 13 of the first subsystem, then enters the gas-liquid separator 116 of the first subsystem for gas-liquid separation from the 11601 end through the C end and the S end of a four-way valve 12 of the first subsystem, and the low-temperature low-pressure gaseous refrigerant comes out of the 11602 end and enters the compressor 11 of the first subsystem through an air suction port 1101 of the compressor 11 of the first subsystem for compression, so that a main. The high-temperature liquid refrigerant of the auxiliary circuit passes through the ball valve 110 of the first subsystem and then passes through the auxiliary throttle valve 18 of the first subsystem to be throttled and decompressed into a gas-liquid two-phase refrigerant, and the gas-liquid two-phase refrigerant enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate into a gas refrigerant. The gaseous refrigerant from the 1604 end passes through 1902 end and 1903 end of the second three-way valve 19 of the first sub-system, and then enters the compressor 11 of the first sub-system through the gas supplementing port 1103 of the compressor 11 of the first sub-system to be compressed by the fifth one-way valve 117 of the first sub-system, thereby completing the gas supplementing circulation of the auxiliary circuit. The above process constitutes a refrigeration cycle of the first subsystem.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the end D and the end E of the four-way valve 22 of the second subsystem, enters the wind side fin heat exchanger 215 of the second subsystem from the end 21501 to release heat to air and is condensed into a high-temperature liquid refrigerant, and then flows out of the end 21502 to pass through the ends 21402 and 21403 of the third three-way valve 214 of the second subsystem, passes through the second one-way valve 211 of the second subsystem, and is divided into two paths of refrigerant of a main path and a secondary path. The main path high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to release heat and be cooled into a supercooled refrigerant. The subcooled refrigerant coming out from the 2602 end passes through the throttle valve 27 of the main path of the second subsystem for throttling and pressure reduction, and enters the water side heat exchanger 04 from the 0404 end for evaporation, heat absorption and refrigeration, the low-temperature low-pressure refrigerant coming out from the 0403 end passes through the 2301 end and the 2302 end of the first three-way valve 23 of the second subsystem, then passes through the C end and the S end of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 216 of the second subsystem for gas-liquid separation through 21601 end, and the low-temperature low-pressure gaseous refrigerant comes out from the 21602 end and enters the compressor 21 of the second subsystem through the air suction port 2101 of the compressor 21 of the second subsystem for compression, thereby completing the main path refrigeration cycle. The high-temperature liquid refrigerant of the auxiliary path passes through the ball valve 210 of the second subsystem and then passes through the auxiliary path throttle valve 28 of the second subsystem to be throttled and decompressed into a gas-liquid two-phase refrigerant, and the gas-liquid two-phase refrigerant enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate into a gaseous refrigerant. The gaseous refrigerant from the end 2604 passes through the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem, and then passes through the fifth one-way valve 217 of the second subsystem and enters the compressor 21 of the second subsystem through the air supplement port 2103 of the compressor 21 of the second subsystem for compression, thereby completing the auxiliary air supplement circulation. The above process constitutes the refrigeration cycle of the second subsystem.
2. Heating circulation:
the D end and the C end of the four-way valve 12 of the first subsystem are communicated, the S end and the E end are communicated, the ball valve 110 of the first subsystem is communicated in an open mode, the 11402 end and the 11403 end of the third three-way valve 114 of the first subsystem are communicated, the 1902 end and the 1903 end of the second three-way valve 19 of the first subsystem are communicated, the 1303 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the C end and the S end and the E end of the four-way valve 22 of the second subsystem are communicated, the ball valve 210 of the second subsystem is communicated in an open mode, the 21402 end and the 21403 end of the third three-way valve 214 of the second subsystem are communicated, the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem are communicated, and the 2302 end and the 2301. When heating, the two subsystems heat independently.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the end D and the end C of the four-way valve 12 of the first subsystem, passes through the end 1301 and the end 1303 of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the end 0401, is discharged to water and condensed into high-temperature liquid refrigerant, passes through the first one-way valve 15 of the first subsystem after exiting from the end 0402, and is divided into two paths of refrigerant, namely a main path and an auxiliary path. The main path high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through 1601 end to release heat and cool into super-cooled refrigerant. The subcooled refrigerant coming out of the 1602 end passes through a main path throttling valve 17 of the first subsystem for throttling and pressure reduction, the subcooled refrigerant enters a wind side fin heat exchanger 115 of the first subsystem from an 11502 end and absorbs heat from air to be evaporated into a low-temperature low-pressure refrigerant, the subcooled refrigerant comes out of an 11501 end and passes through an E end and an S end of a four-way valve 12 of the first subsystem, the subcooled refrigerant enters a gas-liquid separator 116 of the first subsystem from an 11601 end for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant comes out of the 11602 end and enters a compressor 11 of the first subsystem through an air suction port 1101 of the compressor 11 of the first subsystem for compression, so that a main path heating cycle is completed. The high-temperature liquid refrigerant of the auxiliary circuit passes through the ball valve 110 of the first subsystem and then passes through the auxiliary throttle valve 18 of the first subsystem to be throttled and decompressed into a gas-liquid two-phase refrigerant, and the gas-liquid two-phase refrigerant enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate into a gas refrigerant. The gaseous refrigerant from the 1604 end passes through 1902 end and 1903 end of the second three-way valve 19 of the first sub-system, and then enters the compressor 11 of the first sub-system through the gas supplementing port 1103 of the compressor 11 of the first sub-system to be compressed by the fifth one-way valve 117 of the first sub-system, thereby completing the gas supplementing circulation of the auxiliary circuit. The above process constitutes a heating cycle of the first subsystem.
The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the end D and the end C of the four-way valve 22 of the second subsystem, passes through the end 2302 and the end 2301 of the first three-way valve 23 of the second subsystem, enters the water side heat exchanger 04 from the end 0403, is discharged to water and condensed into high-temperature liquid refrigerant, passes through the first one-way valve 25 of the second subsystem after exiting from the end 0404, and is then divided into two paths of refrigerant of a main path and a secondary path. The main path high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to release heat and be cooled into a supercooled refrigerant. The subcooled refrigerant from the 2602 end passes through the throttle valve 27 of the main path of the second subsystem for throttling and pressure reduction, the fourth one-way valve 213 of the second subsystem enters the wind side fin heat exchanger 215 of the second subsystem from the 21502 end to absorb heat from air and evaporate into a low-temperature and low-pressure refrigerant, the subcooled refrigerant from the 21501 end passes through the E end and the S end of the four-way valve 22 of the second subsystem to enter the gas-liquid separator 216 of the second subsystem from 21601 for gas-liquid separation, and the low-temperature and low-pressure gaseous refrigerant exits from the 21602 end to enter the compressor 21 of the second subsystem through the air inlet 2101 of the compressor 21 of the second subsystem for compression, thereby completing the main path heating cycle. The high-temperature liquid refrigerant of the auxiliary path passes through the ball valve 210 of the second subsystem and then passes through the auxiliary path throttle valve 28 of the second subsystem to be throttled and decompressed into a gas-liquid two-phase refrigerant, and the gas-liquid two-phase refrigerant enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate into a gas refrigerant. The gaseous refrigerant from the end 2604 passes through the 2902 end and the 2903 end of the second three-way valve 29 of the second subsystem, and then passes through the fifth one-way valve 217 of the second subsystem and enters the compressor 21 of the second subsystem through the air supplement port 2103 of the compressor 21 of the second subsystem for compression, thereby completing the auxiliary air supplement circulation. The above process constitutes a heating cycle of the second subsystem.
3. Defrosting circulation:
3.1, defrosting of the first subsystem and heating of the second subsystem (without enthalpy injection)
The D end and the E end of the four-way valve 12 of the first subsystem are communicated, the S end and the C end are communicated, the ball valve 110 of the first subsystem is closed and is not communicated, the 11402 end and the 11401 end of the third three-way valve 114 of the first subsystem are communicated, the 1302 end and the 1301 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the C end and the S end and the E end of the four-way valve 22 of the second subsystem are communicated, the ball valve 210 of the second subsystem is closed and is not communicated, the 21402 end and the 21403 end of the third three-way valve 214 of the second subsystem are communicated, the 2902 end and the 2901 end of the second three-way valve 29 of the second subsystem are communicated, and the 2302 end and the 2301 end of the first three-way valve. When the first subsystem defrosts, the second subsystem heats (does not inject enthalpy).
High-temperature and high-pressure refrigerant working medium discharged from an exhaust port 1102 of a compressor 11 of a first subsystem passes through a D end and an E end of a four-way valve 12 of the first subsystem, enters a wind side fin heat exchanger 115 of the first subsystem from an end 11501 to release heat and defrost, is condensed into high-temperature liquid refrigerant, passes through an end 11402 and an end 11401 of a third three-way valve 114 of the first subsystem from the end 11502, is throttled and depressurized into gas-liquid two-phase refrigerant through an auxiliary path throttle valve 28 of the second subsystem, enters an economizer 26 of the second subsystem from an end 2603 to absorb heat and evaporate into low-temperature and low-pressure refrigerant, passes through an end 2902 and an end 2901 of a second three-way valve 29 of the second subsystem after passing through an end 2604, passes through an end 1302 and an end 1301 of a first three-way valve 13 of the first subsystem, passes through an end C end and an end S end of the four-way valve 12 of the first subsystem from an end 1301, and enters a gas, the low-temperature and low-pressure gaseous refrigerant is discharged from the 11602 end and enters the compressor 11 of the first subsystem through the suction port 1101 of the compressor 11 of the first subsystem to be compressed, and therefore the defrosting cycle of the first subsystem is completed. The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 2102 of the compressor 21 of the second subsystem passes through the D end and the C end of the four-way valve 22 of the second subsystem, passes through the 2302 end and the 2301 end of the first three-way valve 23 of the second subsystem, enters the water side heat exchanger 04 from the 0403 end, is radiated and condensed to water to form high-temperature liquid refrigerant, is discharged from the 0404 end and passes through the first one-way valve 25 of the second subsystem, and the high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be radiated and cooled to form supercooled refrigerant. The subcooled refrigerant from the 2602 end passes through a main throttle valve 27 of the second subsystem for throttling and pressure reduction, a fourth one-way valve 213 of the second subsystem enters the wind side fin heat exchanger 215 of the second subsystem from the 21502 end to absorb heat from air and evaporate into a low-temperature and low-pressure refrigerant, the subcooled refrigerant from the 21501 end passes through the E end and the S end of a four-way valve 22 of the second subsystem, the subcooled refrigerant enters a gas-liquid separator 216 of the second subsystem from 21601 for gas-liquid separation, and the low-temperature and low-pressure gaseous refrigerant exits from the 21602 end and enters a compressor 21 of the second subsystem through an air inlet 2101 of the compressor 21 of the second subsystem for compression, so that the heating (no-injection enthalpy) cycle of the second subsystem.
When the first subsystem defrosts, the second subsystem heats normally. The economizer 26 of the second subsystem is used as an evaporator of the defrosting first subsystem, defrosting heat of the defrosting first subsystem is heat generated by supercooling the high-temperature liquid refrigerant of the second subsystem which works and heats the compressor 11 per se in the economizer 26 of the second subsystem, and the heating second subsystem and the defrosting first subsystem realize energy complementation so as to reasonably utilize system energy. And the first subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating can be ensured during defrosting of the whole system.
3.2 defrosting the second subsystem, heating the first subsystem (without enthalpy)
The D end and the C end of the four-way valve 12 of the first subsystem are communicated, the S end and the E end are communicated, the ball valve 110 of the first subsystem is closed and is not communicated, the 11402 end and the 11403 end of the third three-way valve 114 of the first subsystem are communicated, the 1902 end and the 1901 end of the second three-way valve 19 of the first subsystem are communicated, the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem are communicated, the D end and the E end of the four-way valve 22 of the second subsystem are communicated, the S end and the C end are communicated, the ball valve 210 of the second subsystem is closed and is not communicated, the 21402 end and the 21401 end of the third three-way valve 214 of the second subsystem are communicated, and the 2303 end and the 2302 end of the first three-. When the second subsystem defrosts, the first subsystem heats (does not spray enthalpy).
High-temperature and high-pressure refrigerant working medium discharged from an exhaust port 2102 of a compressor 21 of the second subsystem passes through a D end and an E end of a four-way valve 22 of the second subsystem, enters a wind side fin heat exchanger 215 of the second subsystem from a 21501 end to release heat and defrost, is condensed into high-temperature liquid refrigerant, passes through 21402 and 21401 ends of a third three-way valve 214 of the second subsystem from the 21502 end, is throttled and depressurized into gas-liquid two-phase refrigerant through an auxiliary throttle valve 18 of the first subsystem, enters an economizer 16 of the first subsystem from a 1603 end to absorb heat and evaporate into low-temperature and low-pressure refrigerant, passes through 1902 and 1901 ends of a second three-way valve 19 of the first subsystem after passing through 1604 end and 2303 and 2302 ends of a first three-way valve 23 of the second subsystem, passes through C and S ends of the four-way valve 22 of the second subsystem from a 2302 end, enters a gas-liquid separator 216 of the second subsystem from a 21601 end, the low-temperature and low-pressure gaseous refrigerant is discharged from the end 21602 and enters the compressor 21 of the second subsystem through the air suction port 2101 of the compressor 21 of the second subsystem to be compressed, and thus the defrosting cycle of the second subsystem is completed. The high-temperature high-pressure refrigerant working medium discharged from the exhaust port 1102 of the compressor 11 of the first subsystem passes through the end D and the end C of the four-way valve 12 of the first subsystem, passes through the end 1301 and the end 1303 of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the end 0401, is discharged to water and condensed into a high-temperature liquid refrigerant, passes through the first one-way valve 15 of the first subsystem after exiting from the end 0402, and enters the economizer 16 of the first subsystem through the end 1601 to release heat and cool into a supercooled refrigerant. The subcooled refrigerant from the 1602 end passes through a main path throttle valve 17 of the first subsystem for throttling and pressure reduction, and a fourth one-way valve 113 of the first subsystem, enters a wind side fin heat exchanger 115 of the first subsystem from an 11502 end, absorbs heat from air and evaporates into a low-temperature and low-pressure refrigerant, exits from an 11501 end, passes through an E end and an S end of a four-way valve 12 of the first subsystem, enters a gas-liquid separator 116 of the first subsystem from an 11601 end for gas-liquid separation, and a low-temperature and low-pressure gaseous refrigerant exits from an 11602 end and enters a compressor 11 of the first subsystem through an air suction port 1101 of the compressor 11 of the first subsystem for compression, so that the heating (no-injection enthalpy) circulation of the first subsystem is completed.
When the second subsystem defrosts, the first subsystem heats normally. The economizer 16 of the first subsystem is used as an evaporator of the defrosting second subsystem, defrosting heat of the defrosting second subsystem is heat generated by supercooling the high-temperature liquid refrigerant of the first subsystem which is used for applying work by the compressor 21 and heating in the economizer 16 of the first subsystem, and the heating first subsystem and the defrosting second subsystem realize energy complementation so as to reasonably utilize system energy. And the second subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating can be ensured during defrosting of the whole system.
It should be noted that, in the first and second embodiments, the three-way valve may be implemented by combining several two-way valves. The third embodiment shown in fig. 3 is described by taking an example in which the first three-way valve 13 of the first subsystem of the first embodiment shown in fig. 1 is replaced by two-way valves, namely a first two-way valve 119 and a second two-way valve 120, and the rest is the same as that of the first embodiment shown in fig. 1.
In the third embodiment, during the refrigeration cycle, the first two-way valve 119 of the first subsystem is opened and communicated, the second two-way valve 120 of the first subsystem is closed and not communicated, the states of other components are the same as those in the first embodiment, and the refrigerant circulation flow path is also the same as that in the first embodiment, and details are not described again.
Correspondingly, during the heating cycle, the first two-way valve 119 of the first subsystem is opened and communicated, the second two-way valve 120 of the first subsystem is closed and not communicated, the states of other components are the same as those in the first embodiment, and the refrigerant circulation flow path is also the same as that in the first embodiment, and will not be described again.
In the defrosting process, when the first subsystem defrosts and the second subsystem heats (does not spray enthalpy), the first two-way valve 119 of the first subsystem is closed and is not communicated, the second two-way valve 120 of the first subsystem is opened and is communicated, the states of other components are the same as those of the first embodiment, and the refrigerant circulation flow path is also the same as that of the first embodiment, and is not described again. When the second subsystem is defrosting and the first subsystem is heating (no enthalpy), the first two-way valve 119 of the first subsystem is opened and communicated, the second two-way valve 120 of the first subsystem is closed and not communicated, the states of other components are the same as those of the first embodiment, and the refrigerant circulation flow path is also the same as that of the first embodiment, and is not described again.
The fourth embodiment shown in fig. 4 is based on the first embodiment, and the two subsystems adopt the water side heat exchanger (indoor side heat exchanger) which is independently arranged, that is, the two subsystems do not share the integrated heat exchanger, and the working principle and the refrigerant flow direction thereof are similar to those of the first embodiment and are not described again. In the fourth embodiment, the heat absorption from the indoor heat exchanger is avoided during defrosting of the system, so that continuous heating of the whole air conditioning system unit is guaranteed, fluctuation of water temperature is reduced, and the use comfort of a user is improved.
The fifth embodiment shown in fig. 5 is based on the second embodiment, and the two subsystems adopt the water-side heat exchanger (indoor-side heat exchanger) which is independently arranged, that is, the two subsystems do not share the integrated heat exchanger, and the working principle and the refrigerant flow direction thereof are similar to those of the first embodiment and are not described again. In the fifth embodiment, the heat absorption from the indoor heat exchanger is also avoided during the defrosting of the system, so that the continuous heating of the whole air conditioning system unit is ensured, the fluctuation of the water temperature is reduced, and the use comfort of a user is improved.
The utility model also provides an air conditioning system, including at least one aforementioned air conditioning system unit to do not absorb the heat from indoor heat exchanger when realizing the system defrosting, thereby guarantee that whole air conditioning system unit heats in succession, reduce the temperature and fluctuate, improve user's use comfort.
Preferably, in the air conditioning system of the present invention, the indoor heat exchangers of all the air conditioning system units can be integrated into a total heat exchanger, and each subsystem corresponding to each air conditioning system unit on the total heat exchanger is provided with a corresponding refrigerant interface, so that on one hand, the volume of the whole air conditioning system can be effectively reduced, and the occupied area is reduced; on the other hand, the heat exchanger can also ensure that the heat of the main heat exchanger is always input in the defrosting process of part of subsystems, thereby ensuring the heating effect and improving the comfort.
From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects:
according to the air conditioning system unit and the air conditioning system of the utility model, the first subsystem and the second subsystem respectively defrost, in the defrosting process of the first subsystem, the auxiliary path of the second economizer is connected into the first compression cycle through the first defrosting pipeline so that the refrigerant of the first compression cycle does not pass through the first indoor heat exchanger any more, and the second subsystem heats normally; the defrosting process of the second subsystem is reversed; thereby ensuring the continuous heating of the whole air conditioning system unit, reducing the fluctuation of water temperature and improving the use comfort of users
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 (8)
1. An air conditioning system unit comprising a first subsystem and a second subsystem; wherein,
the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer, wherein the first compressor, the first outdoor heat exchanger, the first indoor heat exchanger and the first economizer are connected with each other to form a first compression cycle;
the second subsystem comprises a second compressor, a second outdoor heat exchanger, a second indoor heat exchanger and a second economizer, wherein the second compressor, the second outdoor heat exchanger, the second indoor heat exchanger and the second economizer are connected with each other to form a second compression cycle;
characterized in that the air conditioning system unit further comprises:
selectively connecting the auxiliary circuit of the second economizer to the first compression cycle so that the refrigerant of the first compression cycle does not pass through the first defrosting pipeline of the first indoor heat exchanger any more; and
and selectively switching the auxiliary circuit of the first economizer into the second compression cycle so that the refrigerant of the second compression cycle does not pass through the second defrosting pipeline of the second indoor heat exchanger any more.
2. Air conditioning system unit according to claim 1,
the first compression cycle having a first junction and a second junction between the first outdoor heat exchanger and the first indoor heat exchanger;
the second compression cycle having a third junction and a fourth junction between the second outdoor heat exchanger and the second indoor heat exchanger;
the inlet pipe of the first economizer comprises an inlet joint, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint; wherein the inlet end of the heating inlet branch pipe is connected with the first connection point, the inlet end of the cooling inlet branch pipe is connected with the second connection point, the outlet end of the main path inlet pipe is connected with the inlet end of the main path of the first economizer, the outlet end of the auxiliary path inlet pipe is connected with the auxiliary path inlet of the first economizer, and an auxiliary path throttling device is arranged on the auxiliary path inlet pipe in series;
the outlet pipe of the main path of the first economizer comprises an outlet main pipe, a heating outlet branch pipe and a refrigerating outlet branch pipe, wherein the heating outlet branch pipe and the refrigerating outlet branch pipe are connected with the outlet main pipe;
the inlet pipe of the second economizer comprises an inlet joint, a heating inlet branch pipe and a refrigerating inlet branch pipe, the outlet ends of which are respectively connected with the inlet joint, and a main path inlet pipe and an auxiliary path inlet pipe, the inlet ends of which are respectively connected with the inlet joint; wherein the inlet end of the heating inlet branch pipe is connected with the third contact, the inlet end of the cooling inlet branch pipe is connected with the fourth contact, the outlet end of the main path inlet pipe is connected with the inlet end of the main path of the second economizer, the outlet end of the auxiliary path inlet pipe is connected with the auxiliary path inlet of the second economizer, and an auxiliary path throttling device is arranged on the auxiliary path inlet pipe in series;
the exit tube of the main road of the second economizer comprises an outlet main tube and a heating outlet branch tube and a refrigerating outlet branch tube which are connected with the outlet main tube, wherein the outlet end of the heating outlet branch tube is connected with the fourth contact, the outlet end of the refrigerating outlet branch tube is connected with the third contact, the outlet main tube is provided with a main road throttling device in series, and the heating outlet branch tube and the refrigerating outlet branch tube are respectively provided with a one-way valve in series.
3. Air conditioning system unit according to claim 2,
the first defrosting pipeline comprises a first inlet pipe and a first outlet pipe, wherein the inlet end of the first inlet pipe is connected with the outlet end of the main path throttling device of the first economizer through a control valve, and the outlet end of the first inlet pipe is connected with the inlet end of the auxiliary path of the second economizer; the inlet end of the first outlet pipe is connected with the outlet end of the auxiliary path of the second economizer through a control valve, and the outlet end of the first outlet pipe is connected between the first indoor heat exchanger and the first compressor through a control valve;
the second defrosting pipeline comprises a second inlet pipe and a second outlet pipe, wherein the inlet end of the second inlet pipe is connected with the outlet end of the main path throttling device of the second economizer through a control valve, and the outlet end of the second inlet pipe is connected with the inlet end of the auxiliary path of the first economizer; the inlet end of the second outlet pipe is connected with the outlet end of the auxiliary path of the first economizer through a control valve, and the outlet end of the second outlet pipe is connected between the second indoor heat exchanger and the second compressor through a control valve.
4. Air conditioning system unit according to claim 2,
the auxiliary path inlet pipe of the first economizer is also provided with a control valve positioned upstream of the auxiliary path throttling device in series;
the auxiliary path inlet pipe of the second economizer is also provided with a control valve positioned upstream of the auxiliary path throttling device in series;
the first defrosting pipeline comprises a first inlet pipe and a first outlet pipe, wherein the inlet end of the first inlet pipe is connected with the refrigeration inlet branch pipe of the first economizer through a control valve, the outlet end of the first inlet pipe is connected between the auxiliary path throttling device of the auxiliary path inlet pipe of the second economizer and the control valve, the inlet end of the first outlet pipe is connected with the outlet end of the auxiliary path of the second economizer through a control valve, and the outlet end of the first outlet pipe is connected between the first indoor heat exchanger and the first compressor through a control valve;
the second defrosting pipeline comprises a second inlet pipe and a second outlet pipe, wherein the inlet end of the second inlet pipe is connected with the refrigeration inlet branch pipe of the second economizer through a control valve, and the outlet end of the first inlet pipe is connected between the auxiliary path throttling device of the auxiliary path inlet pipe of the first economizer and the control valve; the inlet end of the second outlet pipe is connected with the outlet end of the auxiliary path of the first economizer through a control valve, and the outlet end of the second outlet pipe is connected between the second indoor heat exchanger and the second compressor through a control valve.
5. Air conditioning system unit according to claim 3 or 4,
the control valve is a three-way control valve or a two-way control valve.
6. Air conditioning system unit according to any of claims 1 to 4,
the first indoor heat exchanger and the second indoor heat exchanger are integrated into an integrated heat exchanger, and the integrated heat exchanger is provided with a first refrigerant inlet and a first refrigerant outlet which are connected into the first compression cycle, and a second refrigerant inlet and a second refrigerant outlet which are connected into the second compression cycle.
7. Air conditioning system, characterized in that it comprises at least one air conditioning system unit according to any of claims 1 to 6.
8. The air conditioning system of claim 7,
the indoor heat exchangers of all the air conditioning system units are integrated into a total heat exchanger.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201621404316.8U CN206514563U (en) | 2016-12-20 | 2016-12-20 | Air conditioning system unit and air conditioning system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201621404316.8U CN206514563U (en) | 2016-12-20 | 2016-12-20 | Air conditioning system unit and air conditioning system |
Publications (1)
Publication Number | Publication Date |
---|---|
CN206514563U true CN206514563U (en) | 2017-09-22 |
Family
ID=59863546
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN201621404316.8U Active CN206514563U (en) | 2016-12-20 | 2016-12-20 | Air conditioning system unit and air conditioning system |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN206514563U (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106766332A (en) * | 2016-12-20 | 2017-05-31 | 珠海格力电器股份有限公司 | Air conditioning system unit and air conditioning system |
CN115978879A (en) * | 2023-03-21 | 2023-04-18 | 昆明理工大学 | High-efficient roast room-freezer coupled system |
-
2016
- 2016-12-20 CN CN201621404316.8U patent/CN206514563U/en active Active
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106766332A (en) * | 2016-12-20 | 2017-05-31 | 珠海格力电器股份有限公司 | Air conditioning system unit and air conditioning system |
CN106766332B (en) * | 2016-12-20 | 2023-05-30 | 珠海格力电器股份有限公司 | Air conditioning system unit and air conditioning system |
CN115978879A (en) * | 2023-03-21 | 2023-04-18 | 昆明理工大学 | High-efficient roast room-freezer coupled system |
CN115978879B (en) * | 2023-03-21 | 2023-06-13 | 昆明理工大学 | Efficient curing barn-freezer coupling system |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
ES2939186T3 (en) | air conditioning system | |
US11739991B2 (en) | Air conditioning system and control method for air conditioning system | |
CN107178833B (en) | Heat recovery external machine system and air conditioning system | |
CN109386986B (en) | Two-pipe heating recovery multi-split air conditioner system and air conditioner outdoor unit thereof | |
WO2019091240A1 (en) | Heating circulation system for air conditioning, and air conditioner | |
CN109386987B (en) | Two-pipe heating recovery multi-split air conditioner system and air conditioner outdoor unit thereof | |
CN206514563U (en) | Air conditioning system unit and air conditioning system | |
CN210832213U (en) | Air conditioner | |
CN106766332B (en) | Air conditioning system unit and air conditioning system | |
CN219037133U (en) | Multi-evaporator parallel defrosting air source heat pump single heat engine unit | |
EP3734199B1 (en) | Air-conditioner system | |
CN109386984B (en) | Two-pipe heating recovery multi-split air conditioner system and air conditioner outdoor unit thereof | |
CN112728800A (en) | Air conditioner | |
CN207702631U (en) | Air conditioner cooling cycle system and air conditioner | |
CN106440460B (en) | Supercooling system of air conditioner heat pump and working method of supercooling system | |
CN115751530A (en) | Air conditioning system, control method, control device, and computer-readable storage medium | |
CN214371045U (en) | Double-water-temperature water outlet variable-frequency air source heat pump system | |
CN210832268U (en) | Air conditioner indoor unit and air conditioner | |
CN209944563U (en) | Air conditioner | |
CN209944564U (en) | Air conditioner | |
CN209944565U (en) | Air conditioner | |
CN106705478B (en) | Hot gas bypass enhanced vapor injection air conditioning system | |
CN210089184U (en) | Enthalpy-increasing type cold and hot full-energy-efficiency recovery heat pump | |
CN208846601U (en) | A kind of cold water heat pump unit and air-conditioning equipment | |
CN207279844U (en) | Air conditioner |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
GR01 | Patent grant | ||
GR01 | Patent grant |