CN112128852B - Double-condensation-temperature heat pump system and control method - Google Patents

Abstract

The heat pump system comprises a compressor, a first heat source heat exchanger, a second heat source heat exchanger, a first use side heat exchanger and a second use side heat exchanger, wherein the first use side heat exchanger can be communicated with a first exhaust pipeline, and the second use side heat exchanger can be communicated with a second exhaust pipeline; or the first and second use side heat exchangers can be respectively communicated to the suction line of the compressor. According to the double condensing temperature control method, double condensing temperatures can be provided, power consumption of the compressor is reduced, and system efficiency is improved; in winter, according to the double condensing temperature, the heat source heat exchanger can supply heat and water to meet different demands, and the heat source heat exchangers of two different heat sources can fully utilize energy sources according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate; the indoor heating performance or the heating water performance is improved, the normal heating or hot water requirement is met, and the energy efficiency is greatly improved.

Description

Double-condensation-temperature heat pump system and control method

Technical Field

The disclosure relates to the technical field of air conditioners, in particular to a double-condensation-temperature heat pump system and a control method.

Background

The prior art patent provides a circulation system with dual condensing temperatures, including one evaporator, two condensers, the compressor having dual discharge ports. The system reduces the condensing temperature of part of refrigerant, reduces the power consumption of the vapor compression refrigeration/heat pump compressor and improves the efficiency of the vapor compression refrigeration/heat pump system by increasing the number of the exhaust pressure of the compressors in the single refrigerant loop. However, the system is used for heating in winter or refrigerating in summer, can not be switched in winter and summer, is simple to control, and can not be flexibly adjusted when the actual load is changeable.

Because the heat pump system in the prior art has the problems that the indoor heating performance or the heating water performance is lower due to unstable heat source in winter, the normal heat supply or hot water requirement cannot be met, the energy efficiency is lower and the like, the double-condensation-temperature heat pump system and the control method are researched and designed.

Disclosure of Invention

Therefore, the technical problem to be solved by the present disclosure is mainly to overcome the defects that in the heat pump system in the prior art, the indoor heating performance or the heating water performance is low due to unstable heat source in winter, the normal heating or hot water requirement cannot be met, and the energy efficiency is low, so as to provide a dual condensation temperature heat pump system and a control method.

In order to solve the above-described problems, the present disclosure provides a dual condensing temperature heat pump system, wherein:

the heat exchanger comprises a compressor, a first heat source heat exchanger, a second heat source heat exchanger, a first use side heat exchanger and a second use side heat exchanger, wherein the refrigerant exchanges heat with the first heat source in the first heat source heat exchanger, the refrigerant exchanges heat with the second heat source in the second heat source heat exchanger, the compressor comprises a first exhaust port, a second exhaust port and an air suction port, the first exhaust port is communicated with a first exhaust pipeline, the second exhaust port is communicated with a second exhaust pipeline, the air suction port is communicated with an air suction pipeline, and the first use side heat exchanger can be communicated to the first exhaust pipeline and the second use side heat exchanger can be communicated to the second exhaust pipeline; or the first use side heat exchanger and the second use side heat exchanger can be respectively communicated to a suction pipeline of the compressor.

In some embodiments, further comprising a first four-way valve having a first end in communication with a first discharge line of the compressor;

the second end of the first four-way valve is communicated with a first branch, the first branch is provided with the first use side heat exchanger, and the first branch is provided with a ninth control valve;

The third end of the first four-way valve is communicated with the air suction pipeline through a second branch, and a second control valve is arranged on the second branch;

the fourth end of the first four-way valve is communicated with the third branch, one end of the first heat source heat exchanger is communicated with the third branch through the fourth branch, an eleventh control valve is arranged on the fourth branch, one end of the second heat source heat exchanger is communicated with the third branch through the fifth branch, and a fourth control valve is arranged on the fifth branch.

In some embodiments, further comprising a second four-way valve, a fifth end of the second four-way valve in communication with a second discharge line of the compressor;

the sixth end of the second four-way valve is communicated with a sixth branch, the sixth branch is provided with the second use side heat exchanger, and the sixth branch is provided with a fourth control valve;

the seventh end of the second four-way valve is communicated with the air suction pipeline, and a third control valve is arranged on the air suction pipeline and between the joint of the air suction pipeline and the second branch and the second four-way valve;

the eighth end of the second four-way valve is communicated with a seventh branch, the seventh branch is communicated to the fifth branch and is positioned between the fourth control valve and the second heat source heat exchanger, and a sixth control valve is further arranged on the fifth branch and is positioned between the joint of the fifth branch and the seventh branch and the second heat source heat exchanger.

In some embodiments, the other end of the first use side heat exchanger is communicated with one end of an eighth branch, the other end of the second use side heat exchanger is communicated with one end of a ninth branch, a first throttling device is arranged on the eighth branch, and a third throttling device is arranged on the ninth branch;

the other end of the first heat source heat exchanger is communicated with one end of a tenth branch, the other end of the eighth branch is communicated to the tenth branch, the other end of the ninth branch is communicated to the tenth branch, a thirteenth control valve is arranged at the position between the position, where the tenth branch is connected with the eighth branch and the first heat source heat exchanger, and a twelfth control valve is arranged at the position between the position, where the tenth branch is connected with the ninth branch and the position, where the tenth branch is connected with the ninth branch.

In some embodiments, the eighth branch and the ninth branch are further communicated through an eleventh branch, and an eighth control valve is disposed on the eleventh branch.

In some embodiments, a twelfth branch is further disposed in a connection position between the ninth branch and the tenth branch, one end of the twelfth branch is connected to the other end of the second heat source heat exchanger, and a fifth control valve is disposed on the twelfth branch.

In some embodiments, the flash evaporator is connected and arranged on the eighth branch and is positioned between the junction of the flash evaporator and the tenth branch and the first throttling device, a second throttling device is further arranged on the eighth branch and between the junction of the flash evaporator and the tenth branch and the flash evaporator, a gas supplementing pipeline of the flash evaporator is communicated to a gas supplementing port of the compressor, and a first control valve is arranged on the gas supplementing pipeline.

In some embodiments, a thirteenth branch is further communicatively disposed between the first branch and the sixth branch, and a tenth control valve is further disposed on the thirteenth branch.

In some embodiments, the first heat source is an air source and the second heat source is a water source.

The present disclosure also provides a control method of the dual condensing temperature heat pump system according to any one of the preceding claims, characterized in that: and controlling the double condensation temperature heat pump system to operate in at least one of a heating mode, a water heating mode, a heat recovery mode and a refrigerating mode.

In some embodiments, when in heating mode, controlling the refrigerant to exchange heat with a first heat source in the first heat source heat exchanger and/or controlling the refrigerant to exchange heat with a second heat source in the second heat source heat exchanger;

And when in the refrigeration mode, controlling the refrigerant to exchange heat with the first heat source in the first heat source heat exchanger and/or controlling the refrigerant to exchange heat with the second heat source in the second heat source heat exchanger.

In some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger is above a preset temperature:

and when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

the system starts a heating mode I, controls to open a first control valve, open a second control valve, open a third control valve, open a ninth control valve, open a twelfth control valve, open a fourth control valve, open a fifth control valve, open a sixth control valve and open a seventh control valve, controls to close the eighth control valve, close the tenth control valve, close the eleventh control valve and close the thirteenth control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and heats the room only through the second heat source heat exchanger.

In some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger is below a preset temperature:

and when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

the system starts a heating mode II, controls to open a first control valve, open a second control valve, open a third control valve, open a ninth control valve, open an eleventh control valve, open a thirteenth control valve, open a fourth control valve, open a fifth control valve and open a sixth control valve, controls to close the eighth control valve, close the tenth control valve, close the twelfth control valve and close the seventh control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and heats the room through the first heat source heat exchanger and the second heat source heat exchanger.

In some embodiments, in the heating mode, and when the second heat source heat exchanger is not available:

And when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

the system starts a heating mode III, controls to open a first control valve, a second control valve, a third control valve, a ninth control valve, an eleventh control valve, a twelfth control valve, a thirteenth control valve, a fourth control valve and a seventh control valve, controls to close the eighth control valve, the tenth control valve, the fifth control valve and the sixth control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and heats the room only through the first heat source heat exchanger.

In some embodiments, in the cooling mode, and while the first heat source heat exchanger is releasing heat, the second heat source heat exchanger is also releasing heat for heat recovery:

and when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

The system starts a refrigeration mode I, controls to open a first control valve, open a second control valve, open a third control valve, open a ninth control valve, open an eleventh control valve, open a thirteenth control valve, open a fourth control valve, open a fifth control valve and open a sixth control valve, controls to close the eighth control valve, close the tenth control valve, close the twelfth control valve and close the seventh control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and simultaneously refrigerates the indoor space through the first heat source heat exchanger and the second heat source heat exchanger.

In some embodiments, in the cooling mode, and only when the first heat source heat exchanger is rejecting heat, the second heat source heat exchanger is not operating, and heat recovery is not performed:

and when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

The system starts a refrigeration mode II, controls to open a first control valve, open a second control valve, open a third control valve, open a ninth control valve, open an eleventh control valve, open a thirteenth control valve, open a twelfth control valve, open a fourth control valve and open a seventh control valve, controls to close the eighth control valve, close the tenth control valve, close the fifth control valve and close the sixth control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and refrigerates the room only through the first heat source heat exchanger.

In some embodiments, in the cooling mode, and only when the second heat source heat exchanger (8) is exothermic for heat recovery:

and when including the first control valve, the second control valve, the third control valve, the fourth control valve, the fifth control valve, the sixth control valve, the seventh control valve, the eighth control valve, the ninth control valve, the tenth control valve, the eleventh control valve, the twelfth control valve, the thirteenth control valve, and including the first throttle device, the second throttle device, and the third throttle device at the same time:

the system starts a refrigeration mode III, controls to open a first control valve, open a second control valve, open a third control valve, open a ninth control valve, open a twelfth control valve, open a fourth control valve, open a fifth control valve, open a sixth control valve and open a seventh control valve, controls to close the eighth control valve, close the tenth control valve, close the thirteenth control valve and close the eleventh control valve, opens a first throttling device and a second throttling device, opens a third throttling device, and only cools the indoor through the second heat source heat exchanger.

The double-condensation-temperature heat pump system and the control method provided by the disclosure have the following beneficial effects:

1. according to the heat pump type air conditioner, the two exhaust ports and the two pipelines are adopted, the two use side heat exchangers can be communicated to the first exhaust pipeline and the second exhaust pipeline one by one respectively, so that double condensation temperatures can be effectively formed to conduct condensation heat release, heating effects of different temperature working conditions can be met when the use side (indoor) heats, energy sources are saved, energy efficiency is improved, and heat release of different condensation temperatures is conducted through two different heat sources when the use side (indoor) refrigerates, the capability of conducting condensation heat release at the heat sources of different temperatures can be effectively improved, heat recovery is conducted, and the energy efficiency of a system is effectively improved; the single-suction double-row compressor is adopted in the method, double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, the double condensing temperature can be provided, so that heat can be supplied, water can be supplied, and different requirements can be met. The heat source heat exchangers of two different heat sources can be switched according to different heat source conditions, and are suitable for the condition that the heat source conditions are unstable in winter, and the energy sources are fully utilized according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate; the second heat source heat exchanger can realize heat recovery in summer, and can recover part of energy, so that the effect of fully utilizing energy is achieved; the indoor heating performance or the heating water performance is effectively improved, the requirements of normal heat supply or hot water are met, and the energy efficiency is greatly improved;

2. According to the four-way valve and the electromagnetic valve, different circulation modes of the system can be realized under different operation conditions, double condensation temperature heating can be realized in winter, one heat source can be utilized for refrigeration or two heat sources can be utilized for refrigeration simultaneously in summer, the operation energy efficiency of the system is improved, the system is enabled to operate optimally, and the problem that the system cannot achieve optimal operation under different operation conditions is solved; the two evaporators and the two condensers can realize different combination modes such as independent operation, simultaneous operation and the like, and the circulation mode can be flexibly selected according to actual requirements.

Drawings

FIG. 1 is a system diagram of a dual condensing temperature heat pump system of the present disclosure;

fig. 2 is a system diagram of a dual condensing temperature heat pump system of an alternative embodiment of the present disclosure.

The reference numerals are expressed as:

1. a first use side heat exchanger; 21. a first control valve; 22. a second control valve; 23. a third control valve; 3. a compressor; 31. a first exhaust port; 32. a second exhaust port; 33. an air suction port; 34. an air supplementing port; 41. a first throttle device; 42. a second throttle device; 43. a third throttling device; 5. a flash evaporator; 6. a first heat source heat exchanger; 71. a fourth control valve; 72. a fifth control valve; 73. a sixth control valve; 74. a seventh control valve; 8. a second heat source heat exchanger; 91. an eighth control valve; 92. a ninth control valve; 93. a tenth control valve; 94. an eleventh control valve; 95. a twelfth control valve; 951. a thirteenth control valve; 10. a second use side heat exchanger; 11. a first four-way valve; 111. a first end; 112. a second end; 113. a third end; 114. a fourth end; 12. a second four-way valve; 121. a fifth end; 122. a sixth end; 123. a seventh end; 124. an eighth end;

100. An air suction line; 200. an air supplementing pipeline; 301. a first exhaust line; 302. a second exhaust line; 401. a first branch; 402. a second branch; 403. a third branch; 404. a fourth branch; 405. a fifth branch; 406. a sixth branch; 407. a seventh branch; 408. an eighth branch; 409. a ninth branch; 410. a tenth branch; 411. an eleventh branch; 412. a twelfth leg; 413. thirteenth branch.

Detailed Description

As shown in fig. 1-2, the present disclosure provides a dual condensing temperature heat pump system, wherein:

comprising a compressor 3, a first heat source heat exchanger 6 (preferably an outdoor first heat exchanger), a second heat source heat exchanger 8 (preferably an outdoor second heat exchanger), a first use side heat exchanger 1 (preferably an indoor first heat exchanger) and a second use side heat exchanger 10 (preferably an indoor second heat exchanger), the refrigerant exchanging heat with the first heat source in the first heat source heat exchanger 6, the refrigerant exchanging heat with the second heat source in the second heat source heat exchanger 8, the compressor 3 comprising a first exhaust port 31 and a second exhaust port 32 and an intake port 33, the first exhaust port 31 being in communication with a first exhaust line 301, the second exhaust port 32 being in communication with a second exhaust line 302, the intake port 33 being in communication with an intake line 100, the first use side heat exchanger 1 being communicable to the first exhaust line 301, and the second use side heat exchanger 10 being communicable to the second exhaust line 302; or the first use side heat exchanger 1 and the second use side heat exchanger 10 can be respectively connected to the suction line 100 of the compressor.

According to the heat pump type air conditioner, the two exhaust ports and the two pipelines are adopted, the two use side heat exchangers can be communicated to the first exhaust pipeline and the second exhaust pipeline one by one respectively, so that double condensation temperatures can be effectively formed to conduct condensation heat release, heating effects of different temperature working conditions can be met when the use side (indoor) heats, energy sources are saved, energy efficiency is improved, and heat release of different condensation temperatures is conducted through two different heat sources when the use side (indoor) refrigerates, the capability of conducting condensation heat release at the heat sources of different temperatures can be effectively improved, heat recovery is conducted, and the energy efficiency of a system is effectively improved; the single-suction double-row compressor is adopted in the method, double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, the double condensing temperature can be provided, so that heat can be supplied, water can be supplied, and different requirements can be met. The heat source heat exchangers of two different heat sources can be switched according to different heat source conditions, and are suitable for the condition that the heat source conditions are unstable in winter, and the energy sources are fully utilized according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate; the second heat source heat exchanger can realize heat recovery in summer, and can recover part of energy, so that the effect of fully utilizing energy is achieved; effectively improves the indoor heating performance or the heating water performance, meets the requirements of normal heat supply or hot water, and greatly improves the energy efficiency.

In some embodiments, the compressor further comprises a first four-way valve 11, wherein a first end 111 of the first four-way valve 11 is communicated with a first exhaust pipeline 301 of the compressor 3;

the second end 112 of the first four-way valve 11 is communicated with a first branch 401, the first branch 401 is provided with the first use side heat exchanger 1, and the first branch 401 is provided with a ninth control valve 92;

the third end 113 of the first four-way valve 11 is communicated to the air suction pipeline 100 through a second branch 402, and a second control valve 22 is arranged on the second branch 402;

the fourth end 114 of the first four-way valve 11 is communicated with the third branch 403, one end of the first heat source heat exchanger 6 is communicated with the third branch 403 through a fourth branch 404, an eleventh control valve 94 is arranged on the fourth branch 404, one end of the second heat source heat exchanger 8 is communicated with the third branch 403 through a fifth branch 405, and a seventh control valve 74 is arranged on the fifth branch 405.

According to the system, through the control of the first four-way valve and the control valve (preferably the electromagnetic valve), different circulation modes of the system can be realized under different operation conditions, double condensation temperature heating can be realized in winter, one heat source can be utilized for refrigeration or two heat sources can be utilized for refrigeration simultaneously in summer, the operation energy efficiency of the system is improved, the system is enabled to operate optimally, and the problem that the system cannot operate optimally under different operation conditions is solved; the two evaporators and the two condensers can realize different combination modes such as independent operation, simultaneous operation and the like, and the circulation mode can be flexibly selected according to actual requirements.

In some embodiments, the compressor further comprises a second four-way valve 12, wherein a fifth end 121 of the second four-way valve 12 is communicated with a second exhaust pipeline 302 of the compressor 3;

the sixth end 122 of the second four-way valve 12 is communicated with a sixth branch 406, the sixth branch 406 is provided with the second use side heat exchanger 10, and the sixth branch 406 is provided with a fourth control valve 71;

the seventh end 123 of the second four-way valve 12 is communicated with the air suction pipeline 100, and a third control valve 23 is further arranged on the air suction pipeline 100 and between the junction with the second branch 402 and the second four-way valve 12;

the eighth end 124 of the second four-way valve 12 is communicated with a seventh branch 407, the seventh branch 407 is communicated to the fifth branch 405 and is located between the seventh control valve 74 and the second heat source heat exchanger 8, and a sixth control valve 73 is further disposed on the fifth branch 405 and is located between the junction with the seventh branch 407 and the second heat source heat exchanger 8.

The control of the second four-way valve and the control valve (preferably an electromagnetic valve) enables the first use side heat exchanger, the first exhaust port and the first heat source heat exchanger to be communicated through the first four-way valve, the second four-way valve is communicated with the second use side heat exchanger, the second exhaust port and the second heat source heat exchanger, and the two four-way valves can be mutually connected, so that different circulation modes of the system are further realized, double condensation temperature heating can be realized in winter, one heat source can be utilized for refrigerating or two heat sources can be utilized for refrigerating simultaneously in summer, the operation energy efficiency of the system is improved, the system is made to operate optimally, and the problem that the system cannot achieve optimal operation under different working conditions is solved; the two evaporators and the two condensers can realize different combination modes such as independent operation, simultaneous operation and the like, and the circulation mode can be flexibly selected according to actual requirements.

In some embodiments, the other end of the first usage-side heat exchanger 1 is communicated with one end of an eighth branch line 408, the other end of the second usage-side heat exchanger 10 is communicated with one end of a ninth branch line 409, the eighth branch line 408 is provided with a first throttling device 41, and the ninth branch line 409 is provided with a third throttling device 43;

the other end of the first heat source heat exchanger 6 is communicated with one end of a tenth branch 410, the other end of an eighth branch 408 is communicated to the tenth branch 410, the other end of a ninth branch 409 is communicated to the tenth branch 410, a thirteenth control valve 951 is arranged on the tenth branch 410 at a position between the position where the tenth branch 408 is connected to the first heat source heat exchanger 6, and a twelfth control valve 95 is arranged on the tenth branch 410 at a position between the position where the tenth branch 409 is connected to the ninth branch 409 and the position where the tenth branch 409 is connected to the tenth branch 409.

Through the setting of eighth branch road and ninth branch road, can set up first use side heat exchanger and second use side heat exchanger effectively respectively and carry out the condensation heat transfer of two condensing temperature under the heating mode to it is different to form the heating temperature that obtains at first use side and the heating temperature that obtains at the second use side, and the condensing temperature that obtains from first and second heat source heat exchanger is different under the cooling mode, and the heat of release is different, improves energy efficiency utilization ratio. The first throttling means and the third throttling means enable an effective throttling of the refrigerant in the piping of the first use side heat exchanger and an effective throttling of the refrigerant in the piping of the second use side heat exchanger.

In some embodiments, the eighth branch 408 and the ninth branch 409 are further communicated through an eleventh branch 411, and an eighth control valve 91 is disposed on the eleventh branch 411. The second use side heat exchanger 10 can be short-circuited under control by the eleventh branch, so as to meet the use requirements of more working conditions.

In some embodiments, a twelfth branch 412 is further disposed in communication with the connection position of the ninth branch 409 and the tenth branch 410, one end of the twelfth branch 412 is connected to the other end of the second heat source heat exchanger 8, and a fifth control valve 72 is disposed on the twelfth branch 412. The ninth branch can be effectively communicated with the second heat source heat exchanger through the twelfth branch, so that the first and the second using side heat exchangers are effectively connected with the second heat source heat exchanger to form a loop, and heat absorption, heating or heat release and refrigeration are carried out from the second heat source heat exchanger.

In some embodiments, the evaporator further comprises a flash evaporator 5, the flash evaporator 5 is connected to the eighth branch 408 and located between the connection point of the tenth branch 410 and the first throttling device 41, a second throttling device 42 is further provided on the eighth branch 408 and between the connection point of the tenth branch 410 and the flash evaporator 5, the air supplementing pipeline 200 of the flash evaporator 5 is communicated to the air supplementing port 34 of the compressor 3, and the air supplementing pipeline 200 is provided with a first control valve 21. The flash evaporator can supplement air and increase enthalpy when the first use side heat exchanger heats, improves the enthalpy value and improves the heating efficiency.

In some embodiments, a thirteenth branch 413 is further disposed in communication between the first branch 401 and the sixth branch 406, and a tenth control valve 93 is further disposed on the thirteenth branch 413. The first branch and the sixth branch can be effectively communicated through the thirteenth branch, and the situation is suitable for the situation that the first branch and the sixth branch are communicated to the air suction pipeline through one pipeline, so that the diversity of different control of different working conditions is met.

In some embodiments, the first heat source is an air source and the second heat source is a water source. The double heat sources comprise, but are not limited to, an air source and a water source, and natural energy sources are fully utilized, so that the effects of energy conservation and emission reduction are achieved.

The present disclosure also provides a control method of the dual condensing temperature heat pump system of any one of the preceding claims, wherein: and controlling the double condensation temperature heat pump system to operate in at least one of a heating mode, a water heating mode, a heat recovery mode and a refrigerating mode.

The system comprises two evaporators, two condensers, one compressor, two four-way valves, an electromagnetic valve, a throttling device and the like. In summer, the double condensing temperature can be provided, the power consumption of the compressor is reduced, the system efficiency is improved, and the heat recovery function can be realized; in winter, according to the double condensing temperature provided, the system can supply heat and water, meet different requirements, realize refrigeration, heating, hot water supply and heat recovery, and improve the equipment utilization rate. The single-suction double-row compressor is adopted in the method, double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, according to the double condensing temperature provided, heat can be supplied, and water can also be supplied, so that different requirements are met. The double heat sources are adopted in winter, the switching can be performed according to different heat source conditions, and the method is suitable for the condition that the heat source conditions are unstable in winter.

One heat source can be used for heating in winter or two heat sources can be used for heating simultaneously. According to the characteristics of different heat sources, the energy sources are fully utilized, so that the system is stable, energy-saving and efficient to operate.

Under different operation conditions, the system can realize different combination modes such as independent operation, simultaneous operation and the like by controlling the four-way reversing valve and the electromagnetic valve, and the two evaporators and the two condensers can flexibly select a circulation mode according to actual requirements.

In some embodiments, when in heating mode, the refrigerant is controlled to exchange heat with a first heat source in the first heat source heat exchanger 6 (absorb heat from the first heat source for supplying heat to the room), and/or the refrigerant is controlled to exchange heat with a second heat source in the second heat source heat exchanger 8 (absorb heat from the second heat source for supplying heat to the room);

in the cooling mode, the refrigerant is controlled to exchange heat with a first heat source in the first heat source heat exchanger 6 (release heat from the first heat source for cooling the room), and/or the refrigerant is controlled to exchange heat with a second heat source in the second heat source heat exchanger 8 (release heat from the second heat source for cooling the room).

This is a form of control of several preferred modes of operation of the heat pump system of the present disclosure, namely a heating mode, a preferred control action in a cooling mode.

When the system is operated in winter, different operation control can be performed according to different heat source temperatures:

heating mode I:

in some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger 8 is higher than a preset temperature:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the heating mode one, and controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the twelfth control valve 95, open the fourth control valve 71, open the fifth control valve 72, open the sixth control valve 73, open the seventh control valve 74, control to close the eighth control valve 91, close the tenth control valve 93, close the eleventh control valve 94, close the thirteenth control valve 951, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and heat the room only by the second heat source heat exchanger 8.

When the second heat source has higher temperature and more heat, the system requirement can be met only by using the second heat source heat exchanger 8 as the heat source side. The system cycle for this condition is as follows: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the twelfth control valve 95, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74 are opened, the eighth control valve 91, the tenth control valve 93, the eleventh control valve 94, the thirteenth control valve 951 are closed, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are opened. The refrigerant releases heat in the first use side heat exchanger 1 and the second use side heat exchanger 10 respectively, then flows through the first use side heat exchanger 1, is throttled by the first throttle device 41 and the second throttle device 42, enters the second heat source heat exchanger 8 through the twelfth control valve 95 and the fifth control valve 72, flows through the second use side heat exchanger 10, enters the second heat source heat exchanger 8 through the third throttle device 43 and the fifth control valve 72, absorbs heat in the second heat source heat exchanger 8, and after absorbing heat, the refrigerant passes through the sixth control valve 73, part of the refrigerant enters the compressor 3 through the second four-way valve 12 to be compressed, and part of the refrigerant enters the compressor 3 through the seventh control valve 74 and the first four-way valve 11 to be compressed, and the compressor comprises two exhaust ports adapting to different exhaust pressures. A part of the refrigerant is discharged from one exhaust port, enters the first use side heat exchanger 1 through the first four-way valve 11 and the ninth control valve 92 to perform the next cycle, and another part of the refrigerant is discharged from the other exhaust port, enters the second use side heat exchanger 10 through the second four-way valve 12 and the fourth control valve 71 to perform the next cycle. The refrigerant has different condensing temperatures and different heat supply temperatures in the first use side heat exchanger 1 and the second use side heat exchanger 10. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.

Heating mode II:

in some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger 8 is below a preset temperature:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the heating mode two, controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the eleventh control valve 94, open the thirteenth control valve 951, open the fourth control valve 71, open the fifth control valve 72, open the sixth control valve 73, control to close the eighth control valve 91, close the tenth control valve 93, close the twelfth control valve 95, close the seventh control valve 74, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and simultaneously heat the room through the first heat source heat exchanger 6 and the second heat source heat exchanger 8.

At lower second heat source temperatures, less heat, the second heat source heat exchanger 8 and the first heat source heat exchanger 6 are required to operate in combination to meet the heat requirements of the system. The system cycle is as follows: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the thirteenth control valve 951, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73 are opened, the eighth control valve 91, the tenth control valve 93, the twelfth control valve 95, the seventh control valve 74 are closed, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are opened. Part of the refrigerant releases heat in the first use side heat exchanger 1, after the heat release, the refrigerant throttles by the first throttling device 41 and the second throttling device 42, then enters the first heat source heat exchanger 6 through the thirteenth control valve 951 to absorb heat, and after the heat absorption, the refrigerant enters the compressor 3 to be compressed through the eleventh control valve 94 and the first four-way valve 11. The other part of the refrigerant releases heat in the second use side heat exchanger 10, the refrigerant after releasing heat is throttled by the third throttling device 43, then enters the second heat source heat exchanger 8 through the fifth control valve 72 to absorb heat, and after absorbing heat, enters the compressor 3 to be compressed through the sixth control valve 73 and the second four-way valve 12. A part of the compressed refrigerant is discharged from one exhaust port, enters the first use side heat exchanger 1 through the first four-way valve 11 and the ninth control valve 92 to perform the next cycle, and another part of the compressed refrigerant is discharged from the other exhaust port, enters the second use side heat exchanger 10 through the second four-way valve 12 and the fourth control valve 71 to perform the next cycle. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.

Heating mode III:

in some embodiments, in heating mode, and when the second heat source heat exchanger 8 is not available:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the heating mode three, and controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the eleventh control valve 94, open the twelfth control valve 95, open the thirteenth control valve 951, open the fourth control valve 71, open the seventh control valve 74, control to close the eighth control valve 91, close the tenth control valve 93, close the fifth control valve 72, close the sixth control valve 73, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and heat the room only by the first heat source heat exchanger 6.

When the second heat source is not available, the first heat source heat exchanger 6 needs to be used alone as the heat source side. The system cycle for this condition is as follows: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951, the fourth control valve 71, the seventh control valve 74 are opened, the eighth control valve 91, the tenth control valve 93, the fifth control valve 72, the sixth control valve 73 are closed, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are opened. The refrigerant releases heat in the first use side heat exchanger 1 and the second use side heat exchanger 10, the refrigerant flowing through the first use side heat exchanger 1 is throttled by the first throttling device 41 and the second throttling device 42, then enters the first heat source heat exchanger 6 through the thirteenth control valve 951, the refrigerant flowing through the second use side heat exchanger 10 is throttled by the third throttling device 43, then enters the first heat source heat exchanger 6 through the twelfth control valve 95 and the thirteenth control valve 951, all the refrigerant absorbs heat in the first heat source heat exchanger 6, the refrigerant absorbs heat after passing through the eleventh control valve 94, a part of the refrigerant enters the compressor 3 through the first four-way valve 11, and the other part of the refrigerant enters the compressor 3 through the seventh control valve 74 and the second four-way valve 12 for compression. A part of the compressed refrigerant is discharged from one exhaust port, enters the first use side heat exchanger 1 through the first four-way valve 11 and the ninth control valve 92 to perform the next cycle, and another part of the compressed refrigerant is discharged from the other exhaust port, enters the second use side heat exchanger 10 through the second four-way valve 12 and the fourth control valve 71 to perform the next cycle. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.

When the first and second use side heat exchangers 1 and 10 do not need to be operated simultaneously, the refrigerant may flow through only one of the use side heat exchangers by closing the ninth or fourth control valve 92 or 71. At this time, the first heat source heat exchanger 6 and the second heat source heat exchanger 8 may be operated independently and may be operated simultaneously.

Summer cooling mode one:

in some embodiments, in the cooling mode, and while the first heat source heat exchanger 6 is releasing heat, the second heat source heat exchanger 8 is also releasing heat for heat recovery:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the first cooling mode, and controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the eleventh control valve 94, open the thirteenth control valve 951, open the fourth control valve 71, open the fifth control valve 72, open the sixth control valve 73, control to close the eighth control valve 91, close the tenth control valve 93, close the twelfth control valve 95, close the seventh control valve 74, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and cool the room through the first heat source heat exchanger 6 and the second heat source heat exchanger 8.

When the system is operated in summer, the operation control is as follows:

heat is released in the first heat source heat exchanger 6 and the second heat source heat exchanger 8, and a part of the heat is recovered in the second heat source heat exchanger 8. The system cycle for this condition is as follows: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the thirteenth control valve 951, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73 are opened, the eighth control valve 91, the tenth control valve 93, the twelfth control valve 95, the seventh control valve 74 are closed, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are opened. A part of the refrigerant absorbs heat in the first use side heat exchanger 1, and the refrigerant after absorbing heat enters the compressor 3 to be compressed through the ninth control valve 92 and the first four-way valve 11. The other part of the refrigerant absorbs heat in the second use side heat exchanger 10, and the refrigerant after absorbing heat enters the compressor 3 to be compressed through the fourth control valve 71 and the second four-way valve 12. A part of the compressed refrigerant is discharged from one exhaust port, enters the first heat source heat exchanger 6 through the first four-way valve 11 and the eleventh control valve 94 to release heat, enters the second throttling device 42 and the first throttling device 41 through the thirteenth control valve 951 to be throttled, and then enters the first use side heat exchanger 1 to perform the next cycle. The other part of the refrigerant is discharged from the other exhaust port, enters the second heat source heat exchanger 8 through the second four-way valve 12 and the sixth control valve 73 to release heat, the second heat source heat exchanger 8 recovers the heat, and the released refrigerant enters the third throttling device 43 through the fifth control valve 72 to be throttled and then enters the second use side heat exchanger 10 to be subjected to the next cycle. In this cycle, the indoor side has a single evaporation temperature and the outdoor side has a double condensation temperature.

And a second refrigeration mode:

in some embodiments, in the cooling mode, and only when the first heat source heat exchanger 6 is rejecting heat, the second heat source heat exchanger 8 is not operating, and no heat recovery is performed:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the second cooling mode, and controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the eleventh control valve 94, open the thirteenth control valve 951, open the twelfth control valve 95, open the fourth control valve 71, open the seventh control valve 74, control to close the eighth control valve 91, close the tenth control valve 93, close the fifth control valve 72, close the sixth control valve 73, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and cool the room only by the first heat source heat exchanger 6.

When heat is released only in the first heat source heat exchanger 6 and heat recovery is not performed, both the refrigerant paths from the two discharge ports of the compressor 3 flow into the first heat source heat exchanger 6 to release heat and do not flow into the second heat source heat exchanger 8. The specific flow is not described in detail.

And a refrigeration mode III:

in some embodiments, in the cooling mode, and only when the second heat source heat exchanger 8 is exothermic for heat recovery:

and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included at the same time, and the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the refrigeration mode three, and controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the twelfth control valve 95, open the fourth control valve 71, open the fifth control valve 72, open the sixth control valve 73, open the seventh control valve 74, control to close the eighth control valve 91, close the tenth control valve 93, close the thirteenth control valve 951, close the eleventh control valve 94, open the first throttle device 41 and open the second throttle device 42, open the third throttle device 43, and cool the room only by the second heat source heat exchanger 8.

When the heat is released in the second heat source heat exchanger 8 and the second heat source heat exchanger 8 recovers the whole heat, at this time, both the two paths of refrigerant from the two exhaust ports of the compressor 3 flow into the second heat source heat exchanger 8 to release the heat, and do not flow into the first heat source heat exchanger 6. The specific flow is not described in detail.

When the first and second use side heat exchangers 1, 10 do not need to be operated simultaneously, the refrigerant can be caused to flow through only one of the use side heat exchangers by closing the second and third throttling means 42, 43. At this time, the first heat source heat exchanger 6 and the second heat source heat exchanger 8 may be operated independently and may be operated simultaneously.

The foregoing description of the preferred embodiments of the present disclosure is not intended to limit the present disclosure, but is to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the present disclosure. The foregoing is merely a preferred embodiment of the present disclosure, and it should be noted that, for a person of ordinary skill in the art, several improvements and modifications can be made without departing from the technical principles of the present disclosure, and these improvements and modifications should also be considered as the protection scope of the present disclosure.

Claims (3)

1. A dual condensing temperature heat pump system, characterized by:

The heat exchanger comprises a compressor (3), a first heat source heat exchanger (6), a second heat source heat exchanger (8), a first use side heat exchanger (1) and a second use side heat exchanger (10), wherein refrigerant exchanges heat with the first heat source in the first heat source heat exchanger (6), refrigerant exchanges heat with the second heat source in the second heat source heat exchanger (8), the compressor (3) comprises a first exhaust port (31) and a second exhaust port (32) and an air suction port (33), the first exhaust port (31) is communicated with a first exhaust pipeline (301), the second exhaust port (32) is communicated with a second exhaust pipeline (302), the air suction port (33) is communicated with an air suction pipeline (100), the first use side heat exchanger (1) can be communicated with the first exhaust pipeline (301), and the second use side heat exchanger (10) can be communicated with the second exhaust pipeline (302); or the first use side heat exchanger (1) and the second use side heat exchanger (10) can be respectively communicated to a suction pipeline (100) of the compressor; the compressor also comprises a first four-way valve (11), wherein a first end (111) of the first four-way valve (11) is communicated with a first exhaust pipeline (301) of the compressor (3);

the second end (112) of the first four-way valve (11) is communicated with a first branch (401), the first use side heat exchanger (1) is arranged on the first branch (401), and a ninth control valve (92) is arranged on the first branch (401);

The third end (113) of the first four-way valve (11) is communicated to the air suction pipeline (100) through a second branch (402), and a second control valve (22) is arranged on the second branch (402);

a fourth end (114) of the first four-way valve (11) is communicated with a third branch (403), one end of the first heat source heat exchanger (6) is communicated to the third branch (403) through a fourth branch (404), an eleventh control valve (94) is arranged on the fourth branch (404), one end of the second heat source heat exchanger (8) is communicated to the third branch (403) through a fifth branch (405), and a seventh control valve (74) is arranged on the fifth branch (405);

the compressor also comprises a second four-way valve (12), wherein a fifth end (121) of the second four-way valve (12) is communicated with a second exhaust pipeline (302) of the compressor (3);

the sixth end (122) of the second four-way valve (12) is communicated with a sixth branch (406), the second use side heat exchanger (10) is arranged on the sixth branch (406), and a fourth control valve (71) is arranged on the sixth branch (406);

a seventh end (123) of the second four-way valve (12) is communicated with the air suction pipeline (100), and a third control valve (23) is arranged on the air suction pipeline (100) and between the joint of the air suction pipeline and the second branch (402) and the second four-way valve (12);

An eighth end (124) of the second four-way valve (12) is communicated with a seventh branch (407), the seventh branch (407) is communicated to the fifth branch (405) and is positioned between the seventh control valve (74) and the second heat source heat exchanger (8), and a sixth control valve (73) is also arranged on the fifth branch (405) and is positioned between the joint of the fifth branch (407) and the second heat source heat exchanger (8);

the other end of the first use side heat exchanger (1) is communicated with one end of an eighth branch (408), the other end of the second use side heat exchanger (10) is communicated with one end of a ninth branch (409), a first throttling device (41) is arranged on the eighth branch (408), and a third throttling device (43) is arranged on the ninth branch (409);

the other end of the first heat source heat exchanger (6) is communicated with one end of a tenth branch (410), the other end of the eighth branch (408) is communicated to the tenth branch (410), the other end of the ninth branch (409) is communicated to the tenth branch (410), a thirteenth control valve (951) is arranged on the tenth branch (410) at a position between the joint of the tenth branch (408) and the first heat source heat exchanger (6), and a twelfth control valve (95) is arranged on the tenth branch (410) at a position between the joint of the tenth branch (409) and the joint of the ninth branch (409);

The eighth branch (408) and the ninth branch (409) are also communicated through an eleventh branch (411), and an eighth control valve (91) is arranged on the eleventh branch (411);

a twelfth branch (412) is further arranged at the connection position of the ninth branch (409) and the tenth branch (410) in a communicating manner, one end of the twelfth branch (412) is communicated with the other end of the second heat source heat exchanger (8), and a fifth control valve (72) is arranged on the twelfth branch (412);

the flash evaporator (5) is connected to the eighth branch (408) and located between the joint of the flash evaporator (5) and the tenth branch (410) and the first throttling device (41), a second throttling device (42) is further arranged between the joint of the eighth branch (408) and the tenth branch (410) and the flash evaporator (5), a gas supplementing pipeline (200) of the flash evaporator (5) is communicated to a gas supplementing port (34) of the compressor (3), and a first control valve (21) is arranged on the gas supplementing pipeline (200);

a thirteenth branch (413) is further communicated between the first branch (401) and the sixth branch (406), and a tenth control valve (93) is further arranged on the thirteenth branch (413);

When in a heating mode, controlling the refrigerant to exchange heat with a first heat source in the first heat source heat exchanger (6) and/or controlling the refrigerant to exchange heat with a second heat source in the second heat source heat exchanger (8);

in the cooling mode, controlling the refrigerant to exchange heat with a first heat source in the first heat source heat exchanger (6) and/or controlling the refrigerant to exchange heat with a second heat source in the second heat source heat exchanger (8);

in heating mode, and when the temperature of the second heat source heat exchanger (8) is higher than a preset temperature: the system starts a heating mode I, controls to open a first control valve (21), a second control valve (22), a third control valve (23), a ninth control valve (92), a twelfth control valve (95), a fourth control valve (71), a fifth control valve (72), a sixth control valve (73) and a seventh control valve (74), controls to close an eighth control valve (91), close a tenth control valve (93), close an eleventh control valve (94), close a thirteenth control valve (951), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and heats the room only through the second heat source heat exchanger (8); or,

In heating mode, and when said second heat source heat exchanger (8) is not available: the system starts a heating mode III, controls to open a first control valve (21), a second control valve (22), a third control valve (23), a ninth control valve (92), an eleventh control valve (94), a twelfth control valve (95), a thirteenth control valve (951), a fourth control valve (71) and a seventh control valve (74), controls to close the eighth control valve (91), close the tenth control valve (93), close the fifth control valve (72) and close the sixth control valve (73), opens a first throttling device (41) and a second throttling device (42), opens a third throttling device (43), and heats the room only through the first heat source heat exchanger (6); or,

in a cooling mode, and only when the first heat source heat exchanger (6) is rejecting heat, the second heat source heat exchanger (8) is not operating and heat recovery is not performed: the system starts a refrigeration mode II, controls to open a first control valve (21), open a second control valve (22), open a third control valve (23), open a ninth control valve (92), open an eleventh control valve (94), open a thirteenth control valve (951), open a twelfth control valve (95), open a fourth control valve (71), open a seventh control valve (74), control to close an eighth control valve (91), close a tenth control valve (93), close a fifth control valve (72), close a sixth control valve (73), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and refrigerate the indoor space only through the first heat source heat exchanger (6); or,

In the cooling mode, and only when the second heat source heat exchanger (8) is releasing heat for heat recovery: the system starts a refrigeration mode III, controls to open a first control valve (21), open a second control valve (22), open a third control valve (23), open a ninth control valve (92), open a twelfth control valve (95), open a fourth control valve (71), open a fifth control valve (72), open a sixth control valve (73), open a seventh control valve (74), control to close an eighth control valve (91), close a tenth control valve (93), close a thirteenth control valve (951), close an eleventh control valve (94), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and refrigerate the indoor space only through the second heat source heat exchanger (8).

2. The dual condensing temperature heat pump system according to claim 1, wherein:

the first heat source is an air source, and the second heat source is a water source.

3. A control method of a double condensing temperature heat pump system according to any one of claims 1-2, characterized by: controlling the double condensing temperature heat pump system to operate in at least one mode of a heating mode, a water heating mode, a heat recovery mode and a refrigerating mode;

When in a heating mode, controlling the refrigerant to exchange heat with a first heat source in the first heat source heat exchanger (6) and/or controlling the refrigerant to exchange heat with a second heat source in the second heat source heat exchanger (8);

in the cooling mode, controlling the refrigerant to exchange heat with a first heat source in the first heat source heat exchanger (6) and/or controlling the refrigerant to exchange heat with a second heat source in the second heat source heat exchanger (8);

in heating mode, and when the temperature of the second heat source heat exchanger (8) is higher than a preset temperature: the system starts a heating mode I, controls to open a first control valve (21), a second control valve (22), a third control valve (23), a ninth control valve (92), a twelfth control valve (95), a fourth control valve (71), a fifth control valve (72), a sixth control valve (73) and a seventh control valve (74), controls to close an eighth control valve (91), close a tenth control valve (93), close an eleventh control valve (94), close a thirteenth control valve (951), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and heats the room only through the second heat source heat exchanger (8); or,

In heating mode, and when said second heat source heat exchanger (8) is not available: the system starts a heating mode III, controls to open a first control valve (21), a second control valve (22), a third control valve (23), a ninth control valve (92), an eleventh control valve (94), a twelfth control valve (95), a thirteenth control valve (951), a fourth control valve (71) and a seventh control valve (74), controls to close the eighth control valve (91), close the tenth control valve (93), close the fifth control valve (72) and close the sixth control valve (73), opens a first throttling device (41) and a second throttling device (42), opens a third throttling device (43), and heats the room only through the first heat source heat exchanger (6); or,

in a cooling mode, and only when the first heat source heat exchanger (6) is rejecting heat, the second heat source heat exchanger (8) is not operating and heat recovery is not performed: the system starts a refrigeration mode II, controls to open a first control valve (21), open a second control valve (22), open a third control valve (23), open a ninth control valve (92), open an eleventh control valve (94), open a thirteenth control valve (951), open a twelfth control valve (95), open a fourth control valve (71), open a seventh control valve (74), control to close an eighth control valve (91), close a tenth control valve (93), close a fifth control valve (72), close a sixth control valve (73), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and refrigerate the indoor space only through the first heat source heat exchanger (6); or,

In the cooling mode, and only when the second heat source heat exchanger (8) is releasing heat for heat recovery: the system starts a refrigeration mode III, controls to open a first control valve (21), open a second control valve (22), open a third control valve (23), open a ninth control valve (92), open a twelfth control valve (95), open a fourth control valve (71), open a fifth control valve (72), open a sixth control valve (73), open a seventh control valve (74), control to close an eighth control valve (91), close a tenth control valve (93), close a thirteenth control valve (951), close an eleventh control valve (94), open a first throttling device (41) and a second throttling device (42), open a third throttling device (43), and refrigerate the indoor space only through the second heat source heat exchanger (8).