CN106766332B

CN106766332B - Air conditioning system unit and air conditioning system

Info

Publication number: CN106766332B
Application number: CN201611185047.5A
Authority: CN
Inventors: 魏峰; 赖瑜
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2016-12-20
Filing date: 2016-12-20
Publication date: 2023-05-30
Anticipated expiration: 2036-12-20
Also published as: CN106766332A

Abstract

The invention provides an air conditioning system unit and an air conditioning system. An air conditioning system unit according to the present invention includes 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 for supplementing air and increasing enthalpy to the first compressor which are mutually connected 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 which are mutually connected to form a second compression cycle, wherein the second economizer is used for supplementing air and increasing enthalpy for the second compressor; the air conditioning system unit further includes: selectively enabling an auxiliary circuit of the second economizer to be connected into the first compression cycle so that a refrigerant of the first compression cycle does not pass through a first defrosting pipeline of the first indoor heat exchanger any more; and selectively connecting the auxiliary circuit of the first economizer to the second compression cycle such that the refrigerant of the second compression cycle no longer passes through the second defrosting circuit of the second indoor heat exchanger. The invention can supply heat continuously when defrosting.

Description

Air conditioning system unit and air conditioning system

Technical Field

The invention relates to the field of air conditioners, in particular to an air conditioning system unit and an air conditioning system.

Background

The air-cooled heat pump cold-hot water unit is used as a cold-heat source of the central air-conditioning system, and has been developed in recent years due to the characteristics of convenient installation, simple operation, energy conservation, easy modularized integration and the like, and the application range of the air-cooled heat pump cold-hot water unit is widened continuously. The lowest environmental temperature of most of the conventional air-cooled heat pump hot and cold water units is 15 ℃ below zero at present, and in order to widen the heating operation range of the air-cooled air source heat pump, an air injection enthalpy-increasing technology is mostly adopted. The heating operation range of the air-cooled heat pump cold-hot water unit adopting the jet enthalpy increase can reach minus 25 ℃ to minus 30 ℃.

When the air-jet enthalpy-increasing air-cooled heat pump hot and cold water unit heats in winter, the heat exchange between the evaporation side fin heat exchanger and the air is easy to frost on the surfaces of fins, so that the heat exchange efficiency of the fins is influenced, and the capacity and the reliability of the unit are influenced. At present, reverse circulation defrosting by four-way valve reversing is commonly utilized, but the defrosting process needs to absorb heat from the water side, heating is stopped during defrosting, continuous heating cannot be performed, water temperature fluctuation is large, and the use comfort of users is seriously affected. The air-jet enthalpy-increasing air-cooled heat pump hot and cold water unit still does not solve the problem of continuous heating during defrosting.

Disclosure of Invention

The invention aims to provide an air conditioning system unit and an air conditioning system capable of continuously heating in a defrosting process.

The invention provides an air conditioning system unit, which comprises 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 for supplementing air and increasing enthalpy to the first compressor which are mutually connected 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 which are mutually connected to form a second compression cycle, wherein the second economizer is used for supplementing air and increasing enthalpy for the second compressor; the air conditioning system unit further includes: selectively enabling an auxiliary circuit of the second economizer to be connected into the first compression cycle so that a refrigerant of the first compression cycle does not pass through a first defrosting pipeline of the first indoor heat exchanger any more; and selectively connecting the auxiliary circuit of the first economizer to the second compression cycle such that the refrigerant of the second compression cycle no longer passes through the second defrosting circuit of the second indoor heat exchanger.

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 joint, the inlet end of the refrigerating inlet branch pipe is connected with the second joint, 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 the auxiliary path inlet pipe is connected with an auxiliary path 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 is connected with the outlet main pipe, the outlet end of the heating outlet branch pipe is connected with the second joint, the outlet end of the refrigerating outlet branch pipe is connected with the first joint, the outlet main pipe is provided with a main path throttling device in series, and the heating outlet branch pipe and the refrigerating outlet branch pipe are respectively provided with a check valve in series; 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 joint, the inlet end of the refrigerating inlet branch pipe is connected with the fourth joint, 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 the auxiliary path inlet pipe is connected with an auxiliary path throttling device in series; the outlet pipe of the main way of the second economizer comprises an outlet main pipe, a heating outlet branch pipe and a refrigerating outlet branch pipe, wherein the heating outlet branch pipe is connected with the outlet main pipe, the outlet end of the heating outlet branch pipe is connected with a fourth joint, the outlet end of the refrigerating outlet branch pipe is connected with a third joint, the outlet main pipe is connected in series with a main way throttling device, and check valves are respectively connected in series with the heating outlet branch pipe and the refrigerating outlet branch pipe.

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 way 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 way 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 way 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 way 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.

Further, a control valve positioned at the upstream of the auxiliary path throttling device is also arranged on the auxiliary path inlet pipe of the first economizer in series; a control valve positioned at the upstream of the auxiliary road throttling device is also arranged on the auxiliary road 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 way throttling device of an auxiliary way 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 way 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 the second economizer through a control valve, and the outlet end of the first inlet pipe is connected between an auxiliary pipeline throttling device of an auxiliary pipeline 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.

Further, 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 with a first compression cycle, and a second refrigerant inlet and a second refrigerant outlet which are connected with a second compression cycle.

The invention also provides an air conditioning system which comprises at least one air conditioning system unit.

Further, the indoor heat exchangers of all air conditioning system units are integrated into one total heat exchanger.

According to the air conditioning system unit and the air conditioning system, the first subsystem and the second subsystem are used for defrosting respectively, in the defrosting process of the first subsystem, the auxiliary circuit 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 is used for heating normally; the second subsystem defrosting process is reversed; thereby guaranteeing the continuous heating of the whole air conditioning system unit, reducing the fluctuation of water temperature and improving the use comfort of users.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:

Fig. 1 is a schematic diagram of a first embodiment of an air conditioning system unit according to the present invention;

fig. 2 is a schematic diagram of a second embodiment of an air conditioning system unit according to the present invention;

fig. 3 is a schematic diagram of a third embodiment of an air conditioning system unit according to the present invention;

fig. 4 is a schematic diagram of a fourth embodiment of an air conditioning system unit according to the present invention;

fig. 5 is a schematic diagram of a fifth embodiment of an air conditioning system unit according to the present invention.

Detailed Description

The invention will be described in detail below with reference to the drawings in connection 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; wherein the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer for supplementing air and increasing enthalpy to the first compressor which are mutually connected 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 which are mutually connected to form a second compression cycle, wherein the second economizer is used for supplementing air and increasing enthalpy for the second compressor; the air conditioning system unit further includes: selectively enabling an auxiliary circuit of the second economizer to be connected into the first compression cycle so that a refrigerant of the first compression cycle does not pass through a first defrosting pipeline of the first indoor heat exchanger any more; and selectively connecting the auxiliary circuit of the first economizer to the second compression cycle such that the refrigerant of the second compression cycle no longer passes through the second defrosting circuit of the second indoor heat exchanger. According to the air conditioning system unit and the air conditioning system, the first subsystem and the second subsystem are used for defrosting respectively, in the defrosting process of the first subsystem, the auxiliary circuit 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 is used for heating normally; the second subsystem defrosting process is reversed; i.e. when one subsystem is defrosted, the other subsystem heats up. The economizer of the heating subsystem is used as an evaporator of the defrosting subsystem, defrosting heat of the defrosting subsystem is generated by working of a compressor of the defrosting subsystem and heat released by supercooling of a high-temperature liquid refrigerant of the other heating subsystem, 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 guaranteed to continuously heat, water temperature fluctuation is reduced, and the use comfort of a user is improved.

In the present invention, the outdoor heat exchanger and the indoor heat exchanger are only functionally expressed, and the indoor heat exchanger is understood to be a heat exchanger that acts (cools or heats) indoors, and the outdoor heat exchanger is understood to be a heat exchanger that absorbs heat or dissipates heat outdoors, and does not refer to a specific installation location indoors or outdoors. In a small-sized domestic air-cooled heat pump hot and cold water unit or an air conditioner, an indoor heat exchanger is arranged indoors, and an outdoor heat exchanger is arranged outdoors. However, since the large-scale commercial air-cooled heat pump water chiller-heater unit is generally an integral unit, and is integrally installed outdoors, the indoor and outdoor units are not separated from each other from the installation position, in the large-scale 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 through the cold and hot water pipeline, thereby refrigerating and heating 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; the inlet end of the heating inlet branch pipe is connected with the first joint a, the inlet end of the refrigerating inlet branch pipe is connected with the second joint b, 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 the auxiliary path inlet pipe is connected with an auxiliary path 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 is connected with the outlet main pipe, the outlet end of the heating outlet branch pipe is connected with a second joint b, the outlet end of the refrigerating outlet branch pipe is connected with a first joint a, the outlet main pipe is provided with a main path throttling device in series, and the heating outlet branch pipe and the refrigerating outlet branch pipe are respectively provided with a check valve in series; 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 joint d, the inlet end of the refrigerating inlet branch pipe is connected with the fourth joint 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 outlet pipe of the main way of the second economizer comprises an outlet main pipe, a heating outlet branch pipe and a refrigerating outlet branch pipe, wherein the heating outlet branch pipe is connected with the outlet main pipe, the outlet end of the heating outlet branch pipe is connected with a fourth joint e, the outlet end of the refrigerating outlet branch pipe is connected with a third joint d, the outlet main pipe is connected in series with a main way throttling device, and check valves are respectively connected in series with the heating outlet branch pipe and the refrigerating outlet branch pipe.

In the present invention, as shown in fig. 1 and 2, the first indoor heat exchanger and the second indoor heat exchanger may be integrated into one 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. Compared with the mode that the two subsystems are respectively adopted to be the indoor heat exchangers in fig. 4 and 5, the indoor heat exchanger corresponding to the defrosting subsystem can be solved without heat input, namely, in the defrosting process, the heating subsystem supplies heat to the indoor heat exchanger shared by the two subsystems, so that the indoor temperature fluctuation of the whole air conditioning system unit can be effectively reduced, continuous heating is ensured, and comfortableness is improved.

The specific working principle of each embodiment of the invention is specifically described by taking a large commercial air-cooled heat pump hot and cold water unit as an example with reference to fig. 1 to 5.

A schematic diagram of a first embodiment system 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, 1103 is a compressor air supply 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 gas pipe orifice of the first subsystem connected with the water side heat exchanger, and 0402 is a liquid pipe orifice of the first subsystem connected with the water side heat exchanger; 15 is a first check valve of the first subsystem; 16 is the economizer of the first subsystem, 1601 is the economizer main line inlet of the first subsystem, 1602 is the economizer main line outlet of the first subsystem, 1603 is the economizer auxiliary line inlet of the first subsystem, 1604 is the economizer auxiliary line outlet of the first subsystem; 17 is a main path throttle valve of the first subsystem; 18 is a secondary path 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 the wind side fin heat exchanger (outdoor heat exchanger) of the first subsystem, 11401 is the wind side fin heat exchanger air nozzle of the first subsystem, 11402 is the wind side fin heat exchanger liquid nozzle 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, 11502 is the gas-liquid separator outlet of the first subsystem. 116 is the fifth one-way valve of the first subsystem.

Similarly, 21 in fig. 1 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 make-up 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 gas pipe orifice of the second subsystem connected with the water side heat exchanger, and 0404 is a liquid pipe orifice of the second subsystem connected with the water side heat exchanger; 25 is a first one-way valve of the second subsystem; 26 is the economizer of the second subsystem, 2601 is the economizer main path inlet of the second subsystem, 2602 is the economizer main path outlet of the second subsystem, 2603 is the economizer auxiliary path inlet of the second subsystem, 2604 is the economizer auxiliary path outlet of the second subsystem; 27 is the main throttle valve of the second subsystem; 28 is a secondary path 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 a second subsystem; 212 is a third check valve of the second subsystem; 213 is a fourth check valve of the second subsystem; 214 is the wind side fin heat exchanger of the second subsystem, 21401 is the wind side fin heat exchanger air nozzle of the second subsystem, 21402 is the wind side fin heat exchanger liquid nozzle 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 the fifth one-way valve of the second subsystem.

The three-way valve is used for connecting and disconnecting the third end of the three-way valve. Taking the first three-way valve 13 of the first subsystem as an example, the following is given: when the 1301 end and the 1302 end are connected, the 1303 end is disconnected; when the 1301 end and the 1303 end are communicated, the 1302 end is disconnected; when the 1302 and 1303 ends are connected, the 1301 end is disconnected. The rest and so on.

The system has three basic modes of refrigeration, heating and defrosting, and the refrigerant circulation flow of each mode is described as follows:

1. cooling mode:

the end D and the end E of the four-way valve 12 of the first subsystem are communicated, the end S and the end C are communicated, the end 11001 of the third three-way valve 110 of the first subsystem is communicated with the end 11003, the end 1902 of the second three-way valve 19 of the first subsystem is communicated with the end 1903 of the third three-way valve 19 of the first subsystem, the end 1303 of the first three-way valve 13 of the first subsystem is communicated with the end 1301 of the third three-way valve, the end D and the end E of the four-way valve 22 of the second subsystem are communicated with the end S and the end C, the end 21001 of the third three-way valve 210 of the second subsystem is communicated with the end 21003, the end 2902 of the second three-way valve 29 of the second subsystem is communicated with the end 2301 of the end 2302 of the first three-way valve 23 of the second subsystem. The two subsystems are mutually independent for refrigeration during refrigeration.

The high-temperature and 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 air-side fin heat exchanger 114 of the first subsystem from the end 11401, releases heat to air, condenses into a high-temperature liquid refrigerant, and exits from the end 11402 to pass through the second one-way valve 111 of the first subsystem, and then is divided into a main-way refrigerant and an auxiliary-way refrigerant. The main high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through the 1601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 1602 passes through the main-path throttle valve 17 of the first subsystem for throttle pressure reduction, passes through 11001 end and 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 0402 end for evaporation and heat absorption for refrigeration, passes through 1303 end and 1301 end of the first three-way valve 13 of the first subsystem from 0401 end, passes through C end and S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 115 of the first subsystem from 11501 end for gas-liquid separation, and passes through the air suction port 1101 of the compressor 11 of the first subsystem from 11502 end for compression, thereby completing the main-path refrigeration cycle. The high-temperature liquid refrigerant in the auxiliary way is throttled and depressurized by the auxiliary way throttle valve 18 of the first subsystem to be a gas-liquid two-phase refrigerant, and enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 1604 passes through 1902 and 1903 ends of the second three-way valve 19 of the first subsystem, and then enters the compressor 11 of the first subsystem through the fifth one-way valve 116 of the first subsystem via the air supplementing port 1103 of the compressor 11 of the first subsystem for compression, thereby completing the auxiliary air supplementing cycle. The above procedure constitutes a refrigeration cycle of the first subsystem.

The high-temperature and 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 air-side fin heat exchanger 214 of the second subsystem from the end 21401, releases heat to air, condenses into high-temperature liquid refrigerant, exits from the end 21402, passes through the second one-way valve 211 of the second subsystem, and is separated into a main-way refrigerant and an auxiliary-way refrigerant. The main high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 2602 end passes through main throttle 27 of second subsystem, passes through 21001 end and 21003 end of third three-way valve of second subsystem, passes through third one-way valve 212 of second subsystem, and enters water side heat exchanger 04 from 0404 end to evaporate and absorb heat to refrigerate, low-temperature low-pressure refrigerant from 0403 end passes through 2301 end and 2302 end of first three-way valve 23 of second subsystem, passes through C end and S end of four-way valve 22 of second subsystem, and enters gas-liquid separator 215 of second subsystem from 21501 to be separated, low-temperature low-pressure gaseous refrigerant from 21502 end enters air suction port 2101 of compressor 21 of second subsystem to be compressed, thereby completing main refrigeration cycle. The high-temperature liquid refrigerant in the auxiliary way is throttled and depressurized by an auxiliary way throttle valve 28 of the second subsystem to be a gas-liquid two-phase refrigerant, and enters an economizer 26 of the second subsystem from a 2603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 2604 end passes through 2902 end and 2903 end of the second three-way valve 29 of the second subsystem, and then enters the compressor 21 of the second subsystem for compression through the fifth one-way valve 216 of the second subsystem through the air compensating port 2103 of the compressor 21 of the second subsystem, thereby completing the auxiliary way air compensating cycle. The above procedure constitutes a refrigeration cycle of the second subsystem.

2. Heating cycle:

the end D and the end C of the four-way valve 12 of the first subsystem are communicated, the end S and the end E are communicated, the end 11001 of the third three-way valve 110 of the first subsystem is communicated with the end 11003, the end 1902 of the second three-way valve 19 of the first subsystem is communicated with the end 1903 of the third three-way valve 19 of the first subsystem, the end 1303 of the first three-way valve 13 of the first subsystem is communicated with the end 1301 of the third three-way valve, the end D and the end C of the four-way valve 22 of the second subsystem are communicated with the end S and the end E, the end 21001 of the third three-way valve 210 of the second subsystem is communicated with the end 21003, the end 2902 of the second three-way valve 29 of the second subsystem is communicated with the end 2301 of the end 2302 of the first three-way valve 23 of the second subsystem. And during heating, the two subsystems heat independently.

The high-temperature and 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 C end of the four-way valve 12 of the first subsystem, passes through the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the 0401 end, is discharged into water to be thermally condensed into high-temperature liquid refrigerant, exits from the 0402 end, passes through the first one-way valve 15 of the first subsystem, and is separated into two paths of refrigerants of a main path and an auxiliary path. The main high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through the 1601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main path throttle valve 17 of the first subsystem for throttle pressure reduction, passes through 11001 end and 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 air side fin heat exchanger 114 of the first subsystem from 11402 end for absorbing heat and evaporating into low-temperature low-pressure refrigerant from air, passes through E end and S end of the four-way valve 12 of the first subsystem from 11401 end, enters the gas-liquid separator 115 of the first subsystem from 11501 end for gas-liquid separation, and passes through the air suction port 1101 of the compressor 11 of the first subsystem for compression, thereby completing the main path heating cycle. The high-temperature liquid refrigerant in the auxiliary way is throttled and depressurized by the auxiliary way throttle valve 18 of the first subsystem to be a gas-liquid two-phase refrigerant, and enters the economizer 16 of the first subsystem from the 1603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 1604 passes through 1902 and 1903 ends of the second three-way valve 19 of the first subsystem, and then enters the compressor 11 of the first subsystem through the fifth one-way valve 116 of the first subsystem via the air supplementing port 1103 of the compressor 11 of the first subsystem for compression, thereby completing the auxiliary air supplementing cycle. The above-described process constitutes a heating cycle of the first subsystem.

The high-temperature and 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 from the end 0404, and is separated into two paths of refrigerants of a main path and an auxiliary path. The main high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 2602 end passes through main-path throttle valve 27 of second subsystem to be throttled and depressurized, passes through 21001 end and 21003 end of third three-way valve of second subsystem, passes through fourth one-way valve 213 of second subsystem, enters into air side fin heat exchanger 214 of second subsystem from 21402 end to absorb heat and evaporate into low-temperature low-pressure refrigerant, passes through E end and S end of four-way valve 22 of second subsystem from 21401 end, enters into gas-liquid separator 215 of second subsystem from 21501 to be separated from gas-liquid, and passes through air suction port 2101 of compressor 21 of second subsystem from 21502 end to enter into compressor 21 of second subsystem to be compressed, thus completing main-path heating cycle. The high-temperature liquid refrigerant in the auxiliary way is throttled and depressurized by an auxiliary way throttle valve 28 of the second subsystem to be a gas-liquid two-phase refrigerant, and enters an economizer 26 of the second subsystem from a 2603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 2604 end passes through 2902 end and 2903 end of the second three-way valve 29 of the second subsystem, and then enters the compressor 21 of the second subsystem for compression through the fifth one-way valve 216 of the second subsystem through the air compensating port 2103 of the compressor 21 of the second subsystem, thereby completing the auxiliary way air compensating cycle. The above-described process constitutes a heating cycle of the second subsystem.

3. Defrosting cycle:

3.1 defrosting the first subsystem and heating the second subsystem (without enthalpy injection)

The end D and the end E of the four-way valve 12 of the first subsystem are communicated, the end S and the end C are communicated, the end 11001 and the end 11002 of the third three-way valve 110 of the first subsystem are communicated, the end 1302 and the end 1301 of the first three-way valve 13 of the first subsystem are communicated, the auxiliary way throttle valve 18 of the first subsystem is closed and is not communicated, the end D and the end C of the four-way valve 22 of the second subsystem are communicated, the end S and the end E of the four-way valve 22 of the second subsystem are communicated, the end 21001 and the end 21003 of the third three-way valve 210 of the second subsystem are communicated, the end 2902 and the end 2901 of the second three-way valve 29 of the second subsystem are communicated, the end 2302 and the end 2301 of the first three-way valve 23 of the second subsystem are communicated, and the auxiliary way throttle valve 28 of the second subsystem is closed and is not communicated. While the first subsystem is defrosted, the second subsystem heats (does not spray enthalpy).

The high-temperature and 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 air-side fin heat exchanger 114 of the first subsystem from the end 11401 for defrosting, is condensed into high-temperature liquid refrigerant, passes through the second one-way valve 111 of the first subsystem from the end 11402, and enters the economizer 16 of the first subsystem from the end 1601 for cooling and heating to form supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main path throttle valve 17 of the first subsystem for throttle pressure reduction, passes through 11001 end and 11002 end of the third three-way valve of the first subsystem, enters the economizer 26 of the second subsystem from 2603 end for absorbing heat and evaporating into low-temperature low-pressure refrigerant, passes through 2902 end and 2901 end of the second three-way valve 29 of the second subsystem after exiting from 2604 end, passes through 1302 end and 1301 end of the first three-way valve 13 of the first subsystem, passes through C end and S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 115 of the first subsystem from 11501 end for gas-liquid separation, and enters the compressor 11 of the first subsystem for compression through the air suction port 1101 of the compressor 11 of the first subsystem from 11502 end for completing the defrosting cycle of the first subsystem.

The high-temperature and 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 to be subjected to heat release and condensation into high-temperature liquid refrigerant, exits from the 0404 end to pass through the first one-way valve 25 of the second subsystem, and enters the economizer 26 of the second subsystem from the 2601 end to be subjected to heat release and cooling into supercooled refrigerant. The supercooled refrigerant from 2602 end passes through main throttle valve 27 of second subsystem, passes through 21001 end and 21003 end of third three-way valve of second subsystem, passes through fourth one-way valve 213 of second subsystem, enters into air side fin heat exchanger 214 of second subsystem from 21402 end, absorbs heat and evaporates into low temperature low pressure refrigerant, passes through E end and S end of four-way valve 22 of second subsystem from 21401 end, enters into gas-liquid separator 215 of second subsystem from 21501, and enters into compressor 21 of second subsystem from 21502 end for compression, thereby completing heating (non-enthalpy injection) cycle of second subsystem.

When the first subsystem is defrosted, the second subsystem heats up normally. The economizer 26 of the second subsystem is used as an evaporator of a first defrosting subsystem, defrosting heat of the first defrosting subsystem is obtained from heat released by supercooling of a high-temperature liquid refrigerant of the second heating subsystem in the economizer 26 of the second subsystem by the compressor 11, and the second heating subsystem and the first defrosting subsystem realize energy complementation so as to reasonably utilize system energy. The first subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating during defrosting of the whole system is ensured.

3.2 defrosting the second subsystem, heating the first subsystem (no enthalpy injection)

The end D and the end C of the four-way valve 12 of the first subsystem are communicated, the end S and the end E are communicated, the end 11001 of the third three-way valve 110 of the first subsystem is communicated with the end 11003, the end 1902 of the second three-way valve 19 of the first subsystem is communicated with the end 1901, the end 1301 of the first three-way valve 13 of the first subsystem is communicated with the end 1303 of the first three-way valve 13 of the first subsystem, and the auxiliary passage throttle valve 18 of the first subsystem is closed and is not communicated. The end D and the end E of the four-way valve 22 of the second subsystem are communicated, the end S and the end C are communicated, the end 21001 and the end 21002 of the third three-way valve 210 of the second subsystem are communicated, the end 2303 and the end 2302 of the first three-way valve 23 of the second subsystem are communicated, and the auxiliary way throttle valve 28 of the second subsystem is closed and is not communicated. When the second subsystem is defrosted, the first subsystem heats (does not spray enthalpy).

The high-temperature and 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 air-side fin heat exchanger 214 of the second subsystem from the end 21401 to be subjected to heat release and defrosting, is condensed into high-temperature liquid refrigerant, passes through the second one-way valve 211 of the second subsystem from the end 21402, and enters the economizer 26 of the second subsystem from the end 2601 to be subjected to heat release and cooling to be subjected to supercooling refrigerant. The supercooled refrigerant from 2602 end passes through main throttle 27 of second subsystem, passes through 21001 end and 21002 end of third three-way valve of second subsystem, then enters economizer 16 of first subsystem from 1603 end to absorb heat and evaporate into low-temperature low-pressure refrigerant, and passes through 1902 end and 1901 end of second three-way valve 19 of first subsystem after exiting from 1604 end, passes through 2303 end and 2302 end of first three-way valve 23 of second subsystem, passes through C end and S end of four-way valve 22 of second subsystem after exiting from 2302 end, and enters gas-liquid separator 215 of second subsystem from 21501 end to separate gas from liquid, and low-temperature low-pressure gaseous refrigerant enters air suction port 2101 of compressor 21 of second subsystem from 21502 end to compress into compressor 21 of second subsystem, thereby completing defrosting cycle of second subsystem.

The high-temperature and 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 C end of the four-way valve 12 of the first subsystem, passes through the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the 0401 end to be subjected to heat release and condensation into high-temperature liquid refrigerant, exits from the 0402 end to pass through the first one-way valve 15 of the first subsystem, and enters the economizer 16 of the first subsystem from the 1601 end to be subjected to heat release and cooling into supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main path throttle valve 17 of the first subsystem for throttle pressure reduction, passes through 11001 end and 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 air side fin heat exchanger 114 of the first subsystem from 11402 end for absorbing heat and evaporating into low-temperature low-pressure refrigerant from air, passes through E end and S end of the four-way valve 12 of the first subsystem from 11401 end, enters the gas-liquid separator 115 of the first subsystem for gas-liquid separation from 11501, and enters the compressor 11 of the first subsystem for compression through the air suction port 1101 of the compressor 11 of the first subsystem from 11502 end, thereby completing the heating (non-enthalpy injection) cycle of the first subsystem.

When the second subsystem is defrosted, the first subsystem heats up normally. The economizer 16 of the first subsystem serves as an evaporator of a second defrosting subsystem, defrosting heat of the second defrosting subsystem is generated by working of the compressor 21 and heat released by supercooling of the high-temperature liquid refrigerant of the first heating subsystem in the economizer 16 of the first subsystem, and the first heating subsystem and the second defrosting subsystem realize energy complementation so as to reasonably utilize system energy. The second subsystem does not absorb heat from the water side heat exchanger 04 during defrosting, so that continuous heating during defrosting of the whole system is ensured.

The second embodiment of the present invention 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 subsystem, 1101 is a compressor suction port of the first subsystem, 1102 is a compressor discharge port of the first subsystem, 1103 is a compressor air supply 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 (shared by all subsystems), 0401 is a gas pipe orifice of the first subsystem connected with the water side heat exchanger, and 0402 is a liquid pipe orifice of the first subsystem connected with the water side heat exchanger; 15 is a first check valve of the first subsystem; 16 is the economizer of the first subsystem, 1601 is the economizer main line inlet of the first subsystem, 1602 is the economizer main line outlet of the first subsystem, 1603 is the economizer auxiliary line inlet of the first subsystem, 1604 is the economizer auxiliary line outlet of the first subsystem; 17 is a main path throttle valve of the first subsystem; 18 is a secondary path throttle valve of the first subsystem; 19 is a second three-way valve of the first subsystem; 110 is a 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 the wind side fin heat exchanger of the first subsystem, 11501 is the wind side fin heat exchanger air nozzle of the first subsystem, 11502 is the wind side fin heat exchanger liquid nozzle 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 the fifth one-way valve of the first subsystem.

Similarly, 21 in fig. 2 is the compressor of the second subsystem, 2101 is the compressor suction port of the second subsystem, 2102 is the compressor discharge port of the second subsystem, 2103 is the compressor supply 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 gas pipe orifice of the second subsystem connected with the water side heat exchanger, and 0404 is a liquid pipe orifice of the second subsystem connected with the water side heat exchanger; 25 is a first one-way valve of the second subsystem; 26 is the economizer of the second subsystem, 2601 is the economizer main path inlet of the second subsystem, 2602 is the economizer main path outlet of the second subsystem, 2603 is the economizer auxiliary path inlet of the second subsystem, 2604 is the economizer auxiliary path outlet of the second subsystem; 27 is the main throttle valve of the second subsystem; 28 is a secondary path throttle valve of the second subsystem; 29 is a second three-way valve of the second subsystem; 210 is a ball valve of the second subsystem; 211 is a second one-way valve of a second subsystem; 212 is a third check 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 wind side fin heat exchanger of the second subsystem, 21501 is the wind side fin heat exchanger air nozzle of the second subsystem, 21502 is the wind side fin heat exchanger liquid nozzle 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 the fifth one-way valve of the second subsystem.

1. refrigeration cycle:

the end D and the end E of the four-way valve 12 of the first subsystem are communicated, the end S and the end C are communicated, the ball valve 110 of the first subsystem is opened and communicated, the end 11402 and the end 11403 of the third three-way valve 114 of the first subsystem are communicated, the end 1902 and the end 1903 of the second three-way valve 19 of the first subsystem are communicated, the end 1303 and the end 1301 of the first three-way valve 13 of the first subsystem are communicated, the end D and the end E of the four-way valve 22 of the second subsystem are communicated, the end S and the end C are communicated, the ball valve 210 of the second subsystem is opened and communicated, the end 21402 and the end 21403 of the third three-way valve 214 of the second subsystem are communicated, the end 2902 and the end 2903 of the second three-way valve 29 of the second subsystem are communicated, and the end 2301 and the end 2302 of the first three-way valve 23 of the second subsystem are communicated. The two subsystems are mutually independent for refrigeration during refrigeration.

The high-temperature and 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 air-side fin heat exchanger 115 of the first subsystem from the end 11501, releases heat to air and condenses into a high-temperature liquid refrigerant, exits from the end 11502, passes through the

ends

11402 and 11403 of the third three-way valve 114 of the first subsystem, passes through the second one-way valve 111 of the first subsystem, and is separated into a main path refrigerant and an auxiliary path refrigerant. The main high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through the 1601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main-path throttle valve 17 of the first subsystem to be throttled and depressurized, and then enters the water side heat exchanger 04 from 0402 end to be evaporated, absorbed and refrigerated, the low-temperature low-pressure refrigerant from 0401 end passes through the 1303 end and 1301 end of the first three-way valve 13 of the first subsystem, then passes through the C end and S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 116 of the first subsystem from 11601 end to be separated from gas and liquid, and the low-temperature low-pressure gaseous refrigerant from 11602 end enters the compressor 11 of the first subsystem to be compressed through the air suction port 1101 of the compressor 11 of the first subsystem, thereby completing the main-path refrigeration cycle. The auxiliary high-temperature liquid refrigerant passes through the ball valve 110 of the first subsystem and then is throttled and depressurized into a gas-liquid two-phase refrigerant by the auxiliary 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 1604 passes through 1902 and 1903 ends of the second three-way valve 19 of the first subsystem, and then enters the compressor 11 of the first subsystem through the fifth one-way valve 117 of the first subsystem via the air supplementing port 1103 of the compressor 11 of the first subsystem for compression, thereby completing the auxiliary air supplementing cycle. The above procedure constitutes a refrigeration cycle of the first subsystem.

The high-temperature and 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 air-side fin heat exchanger 215 of the second subsystem from the end 21501, releases heat to air, condenses into a high-temperature liquid refrigerant, exits from the end 21502, passes 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 separated into a main path refrigerant and an auxiliary path refrigerant. The main high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 2602 end passes through the main-path throttle valve 27 of the second subsystem for throttle pressure reduction and the third check valve 212 of the second subsystem, the 0404 end enters the water side heat exchanger 04 for evaporation, absorption and refrigeration, the low-temperature low-pressure refrigerant from 0403 end passes through 2301 end and 2302 end of the first three-way valve 23 of the second subsystem, the C end and S end of the four-way valve 22 of the second subsystem, the 21601 enters the gas-liquid separator 216 of the second subsystem for gas-liquid separation, and the low-temperature low-pressure gaseous refrigerant from 21602 end enters the compressor 21 of the second subsystem for compression through the air suction port 2101 of the compressor 21 of the second subsystem, thereby completing the main-path refrigeration cycle. The auxiliary high-temperature liquid refrigerant passes through the ball valve 210 of the second subsystem and then is throttled and depressurized by the auxiliary throttle valve 28 of the second subsystem to be a gas-liquid two-phase refrigerant, and enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 2604 end passes through 2902 end and 2903 end of the second three-way valve 29 of the second subsystem, and then enters the compressor 21 of the second subsystem for compression through the fifth one-way valve 217 of the second subsystem through the air compensating port 2103 of the compressor 21 of the second subsystem, thereby completing the auxiliary air compensating cycle. The above procedure constitutes a refrigeration cycle of the second subsystem.

2. Heating cycle:

the end D and the end C of the four-way valve 12 of the first subsystem are communicated, the end S and the end E are communicated, the ball valve 110 of the first subsystem is opened and communicated, the end 11402 and the end 11403 of the third three-way valve 114 of the first subsystem are communicated, the end 1902 and the end 1903 of the second three-way valve 19 of the first subsystem are communicated, the end 1303 and the end 1301 of the first three-way valve 13 of the first subsystem are communicated, the end D and the end C of the four-way valve 22 of the second subsystem are communicated, the end S and the end E are communicated, the ball valve 210 of the second subsystem is opened and communicated, the end 21402 and the end 21403 of the third three-way valve 214 of the second subsystem are communicated, the end 2902 and the end 2903 of the second three-way valve 29 of the second subsystem are communicated, and the end 2302 and the end 2301 of the first three-way valve 23 of the second subsystem are communicated. And during heating, the two subsystems heat independently.

The high-temperature and 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 C end of the four-way valve 12 of the first subsystem, passes through the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the 0401 end, is discharged into water to be thermally condensed into high-temperature liquid refrigerant, exits from the 0402 end, passes through the first one-way valve 15 of the first subsystem, and is separated into two paths of refrigerants of a main path and an auxiliary path. The main high-temperature liquid refrigerant enters the economizer 16 of the first subsystem through the 1601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main-path throttle valve 17 of the first subsystem for throttle depressurization and the fourth check valve 113 of the first subsystem, enters the air-side fin heat exchanger 115 of the first subsystem from 11502 end, absorbs heat from air and evaporates into low-temperature low-pressure refrigerant, exits from 11501 end, passes through E end and S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 116 of the first subsystem from 11601 end for gas-liquid separation, and exits from 11602 end into 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 main-path heating cycle. The auxiliary high-temperature liquid refrigerant passes through the ball valve 110 of the first subsystem and then is throttled and depressurized into a gas-liquid two-phase refrigerant by the auxiliary 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 1604 passes through 1902 and 1903 ends of the second three-way valve 19 of the first subsystem, and then enters the compressor 11 of the first subsystem through the fifth one-way valve 117 of the first subsystem via the air supplementing port 1103 of the compressor 11 of the first subsystem for compression, thereby completing the auxiliary air supplementing cycle. The above-described process constitutes a heating cycle of the first subsystem.

The high-temperature and 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 from the end 0404, and is separated into two paths of refrigerants of a main path and an auxiliary path. The main high-temperature liquid refrigerant enters the economizer 26 of the second subsystem through the 2601 end to be subjected to heat release and cooling to be supercooled refrigerant. The supercooled refrigerant from 2602 end passes through the main-path throttle valve 27 of the second subsystem for throttle pressure reduction and the fourth check valve 213 of the second subsystem, enters the air-side fin heat exchanger 215 of the second subsystem from 21502 end, absorbs heat from air and evaporates into low-temperature low-pressure refrigerant, exits from 21501 end and passes through E end and S end of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 216 of the second subsystem from 21601 for gas-liquid separation, and exits from 21602 end and enters the compressor 21 of the second subsystem for compression through the air suction port 2101 of the compressor 21 of the second subsystem, thereby completing the main-path heating cycle. The auxiliary high-temperature liquid refrigerant passes through the ball valve 210 of the second subsystem and then is throttled and depressurized by the auxiliary throttle valve 28 of the second subsystem to be a gas-liquid two-phase refrigerant, and enters the economizer 26 of the second subsystem from the 2603 end to absorb heat and evaporate to be a gaseous refrigerant. The gaseous refrigerant from 2604 end passes through 2902 end and 2903 end of the second three-way valve 29 of the second subsystem, and then enters the compressor 21 of the second subsystem for compression through the fifth one-way valve 217 of the second subsystem through the air compensating port 2103 of the compressor 21 of the second subsystem, thereby completing the auxiliary air compensating cycle. The above-described process constitutes a heating cycle of the second subsystem.

3. Defrosting cycle:

The end D and the end E of the four-way valve 12 of the first subsystem are communicated, the end S and the end C of the four-way valve are communicated, the ball valve 110 of the first subsystem is closed and is not communicated, the end 11402 and the end 11401 of the third three-way valve 114 of the first subsystem are communicated, the end 1302 and the end 1301 of the first three-way valve 13 of the first subsystem are communicated, the end D and the end C of the four-way valve 22 of the second subsystem are communicated, the end S and the end E 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 end 21402 and the end 21403 of the third three-way valve 214 of the second subsystem are communicated, the end 2902 and the end 2901 of the second three-way valve 29 of the second subsystem are communicated, and the end 2302 and the end 2301 of the first three-way valve 23 of the second subsystem are communicated. While the first subsystem is defrosted, the second subsystem heats (does not spray enthalpy).

The high-temperature and 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 air-side fin heat exchanger 115 of the first subsystem from the end 11501 for defrosting, is condensed into high-temperature liquid refrigerant, exits from the end 11502, passes through the end 11402 and the end 11401 of the third three-way valve 114 of the first subsystem, is throttled and depressurized by the auxiliary way throttle valve 28 of the second subsystem to be gas-liquid two-phase refrigerant, enters the economizer 26 of the second subsystem from the end 2603 for absorbing heat and evaporating into low-temperature and low-pressure refrigerant, exits from the end 2604, passes through the end 2902 and the end 2901 of the second three-way valve 29 of the second subsystem, exits from the end 1301, passes through the end C and the end S of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 116 of the first subsystem from the end 11601, and enters the gas-liquid separator 116 of the first subsystem from the end 11602 to be gas-liquid separated, enters the air suction port 11 of the first subsystem, and is gasified and circulated from the air-suction port 11 of the first subsystem. The high-temperature and 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 to be subjected to heat release and condensation into high-temperature liquid refrigerant, exits from the 0404 end to pass through the first one-way valve 25 of the second subsystem, and enters the economizer 26 of the second subsystem from the 2601 end to be subjected to heat release and cooling into supercooled refrigerant. The supercooled refrigerant from 2602 end passes through the main throttle valve 27 of the second subsystem for throttle depressurization and the fourth check valve 213 of the second subsystem, enters the air-side fin heat exchanger 215 of the second subsystem from 21502 end, absorbs heat from air and evaporates into low-temperature low-pressure refrigerant, exits from 21501 end and passes through E end and 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 from 21601, and exits from 21602 end and enters the compressor 21 of the second subsystem for compression through the air suction port 2101 of the compressor 21 of the second subsystem, thereby completing the heating (non-enthalpy injection) cycle of the second subsystem.

The end D and the end C of the four-way valve 12 of the first subsystem are communicated, the end S and the end E are communicated, the ball valve 110 of the first subsystem is closed and is not communicated, the end 11402 and the end 11403 of the third three-way valve 114 of the first subsystem are communicated, the end 1902 and the end 1901 of the second three-way valve 19 of the first subsystem are communicated, the end 1301 and the end 1303 of the first three-way valve 13 of the first subsystem are communicated, the end D and the end E of the four-way valve 22 of the second subsystem are communicated, the end S and the end C are communicated, the ball valve 210 of the second subsystem is closed and is not communicated, the end 21402 and the end 21401 of the third three-way valve 214 of the second subsystem are communicated, and the end 2303 and the end 2302 of the first three-way valve 23 of the second subsystem are communicated. When the second subsystem is defrosted, the first subsystem heats (does not spray enthalpy).

The high-temperature and 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 air-side fin heat exchanger 215 of the second subsystem from the end 21501 for defrosting, is condensed into high-temperature liquid refrigerant, exits from the end 21502 and passes through the end 21402 and the end 21401 of the third three-way valve 214 of the second subsystem, is throttled and depressurized by the auxiliary way throttle valve 18 of the first subsystem to be gas-liquid two-phase refrigerant, enters the economizer 16 of the first subsystem from the end 1603 for absorbing heat and evaporating into low-temperature and low-pressure refrigerant, exits from the end 1604 and passes through the end 1902 and the end 1901 of the second three-way valve 19 of the first subsystem, exits from the end 2302 and passes through the end C and the end S of the four-way valve 22 of the second subsystem, enters the gas-liquid separator 216 of the second subsystem from the end 21601, and enters the gas-liquid separator 216 of the second subsystem from the end 21601 to be gas-liquid separator of the second subsystem, and enters the air-liquid separator 216 of the second subsystem from the air suction port 21 of the second subsystem from the end 21602 of the second subsystem to be defrosted, and enters the compressor 21 of the second subsystem for compressing and circulating into the compressor 2101 of the second subsystem. The high-temperature and 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 C end of the four-way valve 12 of the first subsystem, passes through the 1301 end and the 1303 end of the first three-way valve 13 of the first subsystem, enters the water side heat exchanger 04 from the 0401 end to be subjected to heat release and condensation into high-temperature liquid refrigerant, exits from the 0402 end to pass through the first one-way valve 15 of the first subsystem, and enters the economizer 16 of the first subsystem from the 1601 end to be subjected to heat release and cooling into supercooled refrigerant. The supercooled refrigerant from 1602 end passes through the main throttle valve 17 of the first subsystem for throttle depressurization and the fourth check valve 113 of the first subsystem, enters the air-side fin heat exchanger 115 of the first subsystem from 11502 end, absorbs heat from air and evaporates into low-temperature low-pressure refrigerant, exits from 11501 end, passes through E end and S end of the four-way valve 12 of the first subsystem, enters the gas-liquid separator 116 of the first subsystem for gas-liquid separation from 11601, and exits from 11602 end and enters the compressor 11 of the first subsystem for compression through the air suction port 1101 of the compressor 11 of the first subsystem, thereby completing the heating (non-enthalpy injection) cycle of the first subsystem.

It should be noted that, in the first embodiment and the second embodiment, the three-way valve may be implemented by a combination of several two-way valves. The third embodiment shown in fig. 3 is described below by taking the first three-way valve 13 of the first subsystem of the first embodiment shown in fig. 1 replaced by two-way valves, namely, the first two-way valve 119 and the second two-way valve 120, respectively, and the other parts are the same as 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 for communication, the second two-way valve 120 of the first subsystem is closed for non-communication, other components are in the same state 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.

Accordingly, during the heating cycle, the first two-way valve 119 of the first subsystem is opened and connected, the second two-way valve 120 of the first subsystem is closed and not connected, 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 will not be described again.

In the defrosting process, when the first subsystem is defrosted and the second subsystem is heated (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 communicated, other components are in the same state as the first embodiment, and a refrigerant circulation flow path is also the same as the first embodiment and is not repeated. When the second subsystem is defrosted and the first subsystem is heated (not enthalpy is sprayed), 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, other components and parts are in the same state as those of the first embodiment, and the refrigerant circulation flow path is the same as that of the first embodiment, and will not be repeated.

In the fourth embodiment shown in fig. 4, based on the first embodiment, two subsystems are independently provided with a water side heat exchanger (an indoor side heat exchanger), that is, the two subsystems do not share an integrated heat exchanger, and the working principle and the refrigerant flow direction of the integrated heat exchanger are similar to those of the first embodiment, and are not repeated. In the fourth embodiment, it is also possible to realize that heat is not absorbed from the indoor heat exchanger when the system is defrosted, thereby ensuring continuous heating of the entire air conditioning system unit, reducing water temperature fluctuation, and improving user comfort.

In the fifth embodiment shown in fig. 5, based on the second embodiment, two subsystems are independently provided with a water side heat exchanger (indoor side heat exchanger), that is, the two subsystems do not share an integrated heat exchanger, and the working principle and the refrigerant flow direction are similar to those of the first embodiment, and are not repeated. In the fifth embodiment, it is also possible to realize that heat is not absorbed from the indoor heat exchanger when the system is defrosted, thereby ensuring continuous heating of the entire air conditioning system unit, reducing water temperature fluctuation, and improving user comfort.

The invention also provides an air conditioning system which comprises at least one air conditioning system unit, so that heat is not absorbed from the indoor heat exchanger when the system is defrosted, the whole air conditioning system unit is ensured to continuously heat, water temperature fluctuation is reduced, and the use comfort of a user is improved.

Preferably, in the air conditioning system of the present invention, the indoor heat exchangers of all air conditioning system units can be integrated into one total heat exchanger, and the total heat exchanger is provided with corresponding refrigerant interfaces corresponding to each subsystem of each air conditioning system unit, so that on one hand, the volume of the whole air conditioning system can be effectively reduced, and the occupied area can be reduced; on the other hand, the total heat exchanger can be guaranteed to have heat input all the time in the defrosting process of part of the subsystems, so that the heating effect is guaranteed, and the comfort is improved.

From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:

according to the air conditioning system unit and the air conditioning system, the first subsystem and the second subsystem are used for defrosting respectively, in the defrosting process of the first subsystem, the auxiliary circuit 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 is used for heating normally; the second subsystem defrosting process is reversed; thereby ensuring continuous heating of the whole air conditioning system unit, reducing water temperature fluctuation and improving the use comfort of users

The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. An air conditioning system unit includes a first subsystem and a second subsystem; wherein, the liquid crystal display device comprises a liquid crystal display device,

the first subsystem comprises a first compressor, a first outdoor heat exchanger, a first indoor heat exchanger and a first economizer which are mutually connected to form a first compression cycle, wherein the first economizer is used for supplementing air and increasing enthalpy for the first compressor;

The second subsystem comprises a second compressor, a second outdoor heat exchanger, a second indoor heat exchanger and a second economizer which are mutually connected to form a second compression cycle, wherein the second economizer is used for supplementing air and increasing enthalpy for the second compressor;

characterized in that the air conditioning system unit further comprises:

optionally, the auxiliary circuit of the second economizer is connected to the first compression cycle such that the refrigerant of the first compression cycle no longer passes through the first defrosting circuit of the first indoor heat exchanger; and

optionally, the auxiliary circuit of the first economizer is connected to the second compression cycle such that the refrigerant of the second compression cycle no longer passes through the second defrosting circuit of the second indoor heat exchanger;

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 joint, the inlet end of the refrigerating inlet branch pipe is connected with the second joint, 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 outlet end of the heating outlet branch pipe is connected with the second joint, the outlet end of the refrigerating outlet branch pipe is connected with the first joint, the outlet main pipe is provided with a main path throttling device in series, and the heating outlet branch pipe and the refrigerating outlet branch pipe are respectively provided with a one-way valve in series;

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 joint, the inlet end of the refrigerating inlet branch pipe is connected with the fourth joint, 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 outlet pipe of the main path of the second 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 outlet end of the heating outlet branch pipe is connected with the fourth joint, the outlet end of the refrigerating outlet branch pipe is connected with the third joint, the outlet main pipe is serially connected with a main path throttling device, and the heating outlet branch pipe and the refrigerating outlet branch pipe are respectively serially connected with a one-way valve;

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 pipeline 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 pipeline 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.

2. An air conditioning system unit according to claim 1, wherein,

A control valve positioned at the upstream of the auxiliary road throttling device is also arranged on the auxiliary road inlet pipe of the first economizer in series;

a control valve positioned at the upstream of the auxiliary road throttling device is also arranged on the auxiliary road 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 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 way throttling device of the auxiliary way 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 way 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 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 way throttling device of the auxiliary way 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.

3. An air conditioning system unit according to claim 1, wherein,

the control valve is a three-way control valve or a two-way control valve.

4. An air conditioning system unit according to any of claims 1 to 3, characterized in that,

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 with the first compression cycle, and a second refrigerant inlet and a second refrigerant outlet which are connected with the second compression cycle.

5. An air conditioning system comprising at least one air conditioning system unit according to any of claims 1 to 4.

6. An air conditioning system according to claim 5, wherein,

all the indoor heat exchangers of the air conditioning system units are integrated into one total heat exchanger.