CN213334690U

CN213334690U - Double-evaporation-temperature heat pump system

Info

Publication number: CN213334690U
Application number: CN202022005445.2U
Authority: CN
Inventors: 荆莹; 王强; 陈晨
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-09-14
Filing date: 2020-09-14
Publication date: 2021-06-01
Anticipated expiration: 2030-09-14

Abstract

The invention provides a double-evaporation-temperature heat pump system which 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 a first cylinder of the compressor is communicated with a first air suction pipeline, a second cylinder of the compressor is communicated with a second air suction pipeline, the first use side heat exchanger can be communicated to the first air suction pipeline, and the second use side heat exchanger can be communicated to the second air suction pipeline; or the first and second usage-side heat exchangers can be communicated to a discharge pipeline of the compressor respectively. According to the method, double evaporation temperatures can be effectively formed for evaporation, so that energy is saved, and the system energy efficiency is improved; the two heat source heat exchangers with different heat sources can fully utilize energy according to the characteristics of different heat sources, so that the indoor heating capacity can be effectively improved during defrosting, the requirement of an indoor environment is met to the maximum degree, and the system energy efficiency is improved.

Description

Double-evaporation-temperature heat pump system

Technical Field

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

Background

When the air conditioning system operates in a heating condition, the temperature of refrigerant flowing through the heat exchanger of the outdoor unit is very low, which can cause the frosting phenomenon of the heat exchanger of the outdoor unit. This phenomenon may seriously deteriorate the heat exchange of the outdoor unit heat exchanger, thereby affecting the heating performance of the entire air conditioning system. Defrosting of the heat exchanger of the outdoor unit of the air conditioning system is particularly important. During defrosting, continuous indoor heating is ensured firstly, and extra energy consumption is reduced to the greatest extent.

The existing double-evaporation temperature system mainly aims at improving the energy efficiency during refrigeration, is not applied to a plurality of technical schemes in the heating field, and is few and few in technology for realizing the functions of double-evaporation temperature heating, defrosting uninterrupted heating and the like. Chinese patent No. CN208620489U provides a system with double evaporation temperatures and capable of realizing defrosting heating without stopping, the system includes 5 heat exchangers, when defrosting heating without stopping is realized, an outdoor heat exchanger that needs defrosting is used as a condenser, one indoor heat exchanger is used as another condenser, and an outdoor heat exchanger that does not need defrosting is used as an evaporator to perform system circulation. When the system is used for defrosting, only one indoor heat exchanger is available, the other heat exchanger is in an idle state, the requirement cannot be met when the heat demand is high, and the indoor comfort is influenced.

Because the heat pump system among the prior art has the indoor heat production volume when defrosting lower, so can not satisfy the demand scheduling problem of indoor environment, consequently this disclosure research designs a two evaporating temperature heat pump system.

SUMMERY OF THE UTILITY MODEL

Therefore, the technical problem to be solved by the present disclosure is to overcome the defect that the heat pump system in the prior art has low indoor heating capacity during defrosting, so that the requirement of indoor environment cannot be met, thereby providing a dual-evaporation temperature heat pump system.

In order to solve the above problem, the present disclosure provides a dual evaporation temperature heat pump system, wherein:

the compressor comprises a first air cylinder and a second air cylinder, wherein the first air cylinder is communicated with a first air suction pipeline, the second air cylinder is communicated with a second air suction pipeline, the first use-side heat exchanger can be communicated to the first air suction pipeline, and the second use-side heat exchanger can be communicated to the second air suction pipeline; or the first usage-side heat exchanger and the second usage-side heat exchanger can be communicated to a discharge pipeline of the compressor respectively.

In some embodiments, a third control valve is disposed on the first suction pipeline, a second control valve is disposed on the second suction pipeline, and the heat pump system further includes a first branch, one end of the first branch communicates with the first suction pipeline, the other end of the first branch communicates with the second suction pipeline, and a first control valve is disposed on the first branch.

In some embodiments, the first heat source heat exchanger includes a first segmented heat exchanging portion and a second segmented heat exchanging portion, the heat pump system further includes a second branch, a third branch, a fourth branch, and a fifth branch, the second branch and the third branch are disposed in parallel, the second branch penetrates the first segmented heat exchanging portion, the third branch penetrates the second segmented heat exchanging portion, the fourth branch and the fifth branch are disposed in parallel, the fourth branch penetrates the first segmented heat exchanging portion, and the fifth branch penetrates the second segmented heat exchanging portion;

the second branch is provided with a fourth control valve, the third branch is provided with a fifth control valve, the fourth branch is provided with a sixth control valve, the fifth branch is provided with a seventh control valve, and refrigerants in the second branch, the third branch, the fourth branch and the fifth branch can respectively exchange heat with the first heat source in the first heat source heat exchanger.

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

the second end of the four-way valve is communicated with a seventh branch, one end of the fourth branch and one end of the fifth branch are converged to a sixth branch, the sixth branch is communicated with the seventh branch, and an eighth control valve is arranged on the sixth branch;

the third end of the four-way valve is communicated to the first air suction pipeline;

the fourth end of the four-way valve is communicated with an eighth branch, one end of the second branch and one end of the third branch are converged and communicated to a ninth branch, the ninth branch is communicated with the eighth branch, and a seventeenth control valve is arranged on the ninth branch.

In some embodiments, the branch where the first usage-side heat exchanger is located is a tenth branch, the branch where the second usage-side heat exchanger is located is an eleventh branch, one end of the tenth branch and one end of the eleventh branch are communicated to the seventh branch, an eleventh control valve is arranged on the tenth branch, and a twelfth control valve is arranged on the eleventh branch.

In some embodiments, the device further comprises a twelfth branch and a thirteenth branch, one end of the twelfth branch is communicated with the other end of the tenth branch, one end of the thirteenth branch is communicated with the other end of the eleventh branch, the other end of the twelfth branch is communicated with the other end of the thirteenth branch through a fourteenth branch, a first throttling device is arranged on the twelfth branch, and a second throttling device is arranged on the thirteenth branch; the other end of the second branch and the other end of the third branch are merged and communicated to the fifteenth branch, the fifteenth branch is communicated with the fourteenth branch, and a fourteenth control valve is arranged on the fourteenth branch.

In some embodiments, the tenth branch and the eleventh branch are further communicated through a sixteenth branch, and a tenth control valve is disposed on the sixteenth branch.

In some embodiments, a seventeenth branch is further arranged at a position where the thirteenth branch is connected with the fourteenth branch, one end of the seventeenth branch is communicated to the second heat source heat exchanger and is led out through an eighteenth branch, the other end of the eighteenth branch is communicated to the eighth branch, refrigerant in the seventeenth branch exchanges heat with the second heat source in the second heat source heat exchanger, a fifteenth control valve is arranged on the seventeenth branch, and a sixteenth control valve is arranged on the eighteenth branch.

In some embodiments, the heat exchanger further comprises a nineteenth branch, one end of the nineteenth branch is communicated to the eleventh branch, the other end of the nineteenth branch is communicated to the second suction pipeline, so that the second use-side heat exchanger can be communicated to the second suction pipeline, one end of the second suction pipeline is communicated to the second cylinder, the other end of the second suction pipeline is communicated to the eighteenth branch, a second control valve is arranged on the second suction pipeline, a thirteenth control valve is arranged on the nineteenth branch, and the other end of the nineteenth branch is communicated to a position, between the second control valve and the compressor, on the second suction pipeline.

In some embodiments, the other end of the fourth branch and the other end of the fifth branch are merged to a twentieth branch, one end of the twentieth branch is communicated to the second heat source heat exchanger and is led out through a twenty-first branch, the other end of the twenty-first branch is communicated to the eighth branch, the refrigerant in the twentieth branch exchanges heat with the second heat source in the second heat source heat exchanger, a third throttling device is arranged on the twentieth branch, and a ninth control valve is arranged on the twenty-first branch.

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

The double-evaporation-temperature heat pump system provided by the disclosure has the following beneficial effects:

1. according to the air cylinder system, the two air cylinders and the two air suction pipelines are adopted, the two using side heat exchangers can be communicated to the first air suction pipeline and the second air suction pipeline one to one, double evaporation temperatures can be effectively formed for evaporation, so that the refrigerating effect under different temperature working conditions is met when the using side (indoor) is used for refrigerating, the energy is saved, the energy efficiency is improved, and the heat absorption at different evaporation temperatures is carried out through the two different heat sources when the using side (indoor) is used for heating, so that the capability of evaporating and absorbing heat from the heat sources at different temperatures can be effectively improved, and the system energy efficiency is effectively improved; the two heat source heat exchangers with different heat sources can be switched according to different heat source conditions when defrosting is not needed, the heat source heat exchangers are suitable for the condition that the heat source conditions in winter are unstable, energy sources are fully utilized according to the characteristics of different heat sources, and the heat source heat exchangers can be used as heat sources of defrosting section heat exchangers when defrosting is needed, so that the energy sources are fully utilized, and the system can stably, energy-saving and efficiently run; the second heat source heat exchanger can realize heat recovery in summer, and recover partial energy, thereby achieving the effect of fully utilizing energy; the indoor heating capacity during defrosting is effectively improved, the requirement of the indoor environment is met to the maximum extent, and the system energy efficiency is improved;

2. the system circulation overcomes the defect that the room temperature is reduced when the existing heat pump is defrosted, and the heat exchanger needing defrosting outdoors is defrosted in a sectional mode by adopting the sectional heat exchanger, so that uninterrupted heating and defrosting are realized, and the room temperature is not obviously reduced in the defrosting process. According to the control system, different circulation modes of the system can be realized under different operation working conditions through the control of the four-way valve and the electromagnetic valve, double-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration can be realized in summer, one heat source can be used for heating in winter or two heat sources can be simultaneously used for heating, the operation energy efficiency of the system is improved, the system can operate optimally, and the problem that the system cannot operate optimally under different working conditions is solved.

Drawings

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

The reference numerals are represented 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; 41. a first throttling device; 42. a second throttling device; 43. a third throttling means; 5. a four-way valve; 51. a first end; 52. a second end; 53. a third end; 54. a fourth end; 6. a first heat source heat exchanger; 61. a first sectional heat exchanging portion; 62. a second sectional heat exchanging part; 71. a fourth control valve; 72. a fifth control valve; 73. a sixth control valve; 74. a seventh control valve; 75. an eighth control valve; 76. a ninth control valve; 8. a second heat source heat exchanger; 91. a tenth control valve; 92. an eleventh control valve; 93. a twelfth control valve; 94. a thirteenth control valve; 95. a fourteenth control valve; 96. a fifteenth control valve; 97. a sixteenth control valve; 98. a seventeenth control valve; 10. a second use-side heat exchanger;

100. a first suction line; 200. a second aspiration line; 300. an exhaust line; 401. a first branch; 402. a second branch circuit; 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 branch; 413. a thirteenth branch; 414. a fourteenth branch; 415. a fifteenth branch circuit; 416. a sixteenth branch; 417. a seventeenth branch; 418. an eighteenth branch; 419. a nineteenth branch; 420. a twentieth branch; 421. the twenty-first branch.

Detailed Description

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

the heat exchanger comprises 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), wherein refrigerant exchanges heat with a first heat source in the first heat source heat exchanger 6, and refrigerant exchanges heat with a second heat source in the second heat source heat exchanger 8, the compressor 3 comprises a first cylinder and a second cylinder, the first cylinder is communicated with a first air suction pipeline 100, the second cylinder is communicated with a second air suction pipeline 200, the first use side heat exchanger 1 can be communicated to the first air suction pipeline 100, and the second use side heat exchanger 10 can be communicated to the second air suction pipeline 200; alternatively, the first and second use-

side heat exchangers

1 and 10 may be connected to the discharge line 300 of the compressor, respectively.

The utility model provides another kind can realize two evaporating temperature heating, can realize the incessant heating function's of defrosting system again, and adopts two heat sources heat supply winter, improves equipment utilization and system efficiency, improves indoor travelling comfort.

According to the air cylinder system, the two air cylinders and the two air suction pipelines are adopted, the two using side heat exchangers can be communicated to the first air suction pipeline and the second air suction pipeline one to one, double evaporation temperatures can be effectively formed for evaporation, so that the refrigerating effect under different temperature working conditions is met when the using side (indoor) is used for refrigerating, the energy is saved, the energy efficiency is improved, and the heat absorption at different evaporation temperatures is carried out through the two different heat sources when the using side (indoor) is used for heating, so that the capability of evaporating and absorbing heat from the heat sources at different temperatures can be effectively improved, and the system energy efficiency is effectively improved; the two heat source heat exchangers with different heat sources can be switched according to different heat source conditions when defrosting is not needed, the heat source heat exchangers are suitable for the condition that the heat source conditions in winter are unstable, energy sources are fully utilized according to the characteristics of different heat sources, and the heat source heat exchangers can be used as heat sources of defrosting section heat exchangers when defrosting is needed, so that the energy sources are fully utilized, and the system can stably, energy-saving and efficiently run; the second heat source heat exchanger can realize heat recovery in summer, and recover partial energy, thereby achieving the effect of fully utilizing energy; the indoor heating capacity can be effectively improved during defrosting, the requirement of the indoor environment is met to the maximum degree, and the energy efficiency is improved.

In some embodiments, a third control valve 23 is disposed on the first suction line 100, a second control valve 22 is disposed on the second suction line 200, and the heat pump system further includes a first branch 401, one end of the first branch 401 is communicated with the first suction line 100, the other end of the first branch 401 is communicated with the second suction line 200, and a first control valve 21 is disposed on the first branch 401. The third control valve that sets up on can controlling this suction pipeline through first breathing pipe, the second control valve on the second suction pipeline can control this suction pipeline, can feed through two suction pipelines through first branch road for the suction pressure of two cylinders equals, in order to adapt to the different operating mode of breathing in.

In some embodiments, the first heat source heat exchanger 6 includes a first segmented heat exchanging portion 61 and a second segmented heat exchanging portion 62, the heat pump system further includes a second branch 402, a third branch 403, a fourth branch 404 and a fifth branch 405, the second branch 402 and the third branch 403 are arranged in parallel, the second branch 402 penetrates the first segmented heat exchanging portion 61, the third branch 403 penetrates the second segmented heat exchanging portion 62, the fourth branch 404 and the fifth branch 405 are arranged in parallel, the fourth branch 404 penetrates the first segmented heat exchanging portion 61, and the fifth branch 405 penetrates the second segmented heat exchanging portion 62;

a fourth control valve 71 is arranged on the second branch 402, a fifth control valve 72 is arranged on the third branch 403, a sixth control valve 73 is arranged on the fourth branch 404, a seventh control valve 74 is arranged on the fifth branch 405, and the refrigerants in the second branch 402, the third branch 403, the fourth branch 404 and the fifth branch 405 can exchange heat with the first heat source in the first heat source heat exchanger 6.

The system circulation overcomes the defect that the room temperature is reduced when the existing heat pump is defrosted, and the heat exchanger needing defrosting outdoors is defrosted in a sectional mode by adopting the sectional heat exchanger, so that uninterrupted heating and defrosting are realized, and the room temperature is not obviously reduced in the defrosting process.

In some embodiments, further comprising a four-way valve 5, a first end 51 of said four-way valve 5 being in communication with a discharge line 300 of said compressor 3;

the second end 52 of the four-way valve 5 is communicated with a seventh branch 407, one end of the fourth branch 404 and one end of the fifth branch 405 are merged to a sixth branch 406, the sixth branch 406 is communicated with the seventh branch 407, and the sixth branch 406 is provided with an eighth control valve 75;

the third end 53 of the four-way valve 5 is communicated to the first air suction pipeline 100;

the fourth end 54 of the four-way valve 5 is communicated with an eighth branch 408, one end of the second branch 402 and one end of the third branch 403 are merged and communicated to a ninth branch 409, the ninth branch 409 is communicated with the eighth branch 408, and the ninth branch 409 is provided with a seventeenth control valve 98.

According to the system, through the control of the four-way valve and the control valve (preferably the electromagnetic valve), different circulation modes of the system can be realized under different operation working conditions, double-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration can be realized in summer, one heat source can be used for heating or two heat sources can be simultaneously used for heating in winter, the operation energy efficiency of the system is improved, the system can operate optimally, and the problem that the system cannot operate optimally under different working conditions is solved.

The system comprises a first heat source heat exchanger, a second heat source heat exchanger, a first use side heat exchanger, a second use side heat exchanger, a compressor, a four-way valve, a throttling device (preferably an electronic expansion valve), a control valve (preferably a solenoid valve) and the like. The first heat source heat exchanger belongs to a sectional heat exchanger, when the heat exchanger needs defrosting in winter, one section of the heat exchanger can be used as a condenser for defrosting, the other section of the heat exchanger can be used as an evaporator for heating, after the defrosting of one section of the heat exchanger is finished, the two sections of the heat exchanger can be switched, and the defrosting of the other section of the heat exchanger is carried out until the defrosting of the two sections of the heat exchanger is finished. Therefore, uninterrupted heating and defrosting are realized, and the room temperature is not obviously reduced in the defrosting process.

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 valve and the control valve, the two evaporators and the two condensers, can realize double-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration in summer, can utilize one heat source to heat in winter or simultaneously utilize two heat sources to heat, improves the operation energy efficiency of the system and enables the system to operate optimally.

In some embodiments, the first usage-side heat exchanger 1 is located in a tenth branch 410, the second usage-side heat exchanger 10 is located in an eleventh branch 411, one end of the tenth branch 410 is communicated with one end of the eleventh branch 411 and communicated to the seventh branch 407, an eleventh control valve 92 is disposed on the tenth branch 410, and a twelfth control valve 93 is disposed on the eleventh branch 411. Through the setting of tenth branch road and eleventh branch road, can effectively set up first user side heat exchanger and second user side heat exchanger respectively and carry out the evaporation heat transfer of two evaporating temperature under the refrigeration mode to the refrigeration temperature that formation acquireed at first user side is different with the refrigeration temperature that acquirees at the second user side, and the evaporating temperature that acquires under the heating mode from first and second heat source heat exchanger is different, and the heat that acquires is different, improves the efficiency utilization ratio.

In some embodiments, a twelfth branch 412 and a thirteenth branch 413 are further included, one end of the twelfth branch 412 is communicated with the other end of the tenth branch 410, one end of the thirteenth branch 413 is communicated with the other end of the eleventh branch 411, the other end of the twelfth branch 412 is communicated with the other end of the thirteenth branch 413 through a fourteenth branch 414, a first throttling device 41 is disposed on the twelfth branch 412, and a second throttling device 42 is disposed on the thirteenth branch 413; the other end of the second branch 402 and the other end of the third branch 403 are merged and communicated to the fifteenth branch 415, the fifteenth branch 415 is communicated with the fourteenth branch 414, and the fourteenth branch 414 is provided with a fourteenth control valve 95. The first throttling device and the second throttling device can be arranged on the twelfth branch and the thirteenth branch in a one-to-one correspondence mode respectively, so that the refrigerant in the pipeline of the first using side heat exchanger can be effectively throttled, the refrigerant in the pipeline of the second using side heat exchanger can be effectively throttled, the refrigerant is communicated with the refrigerant in the pipeline of the second using side heat exchanger through the fourteenth branch and communicated to the junction of the two parallel branches of the first heat source heat exchanger through the fifteenth branch, the first using side heat exchanger and the second using side heat exchanger are effectively connected with the first heat source heat exchanger to form a loop, and heat absorption heating or heat release cooling is performed on the first heat source heat exchanger.

In some embodiments, the tenth branch 410 and the eleventh branch 411 are further communicated through a sixteenth branch 416, and a tenth control valve 91 is disposed on the sixteenth branch 416. The setting through the sixteenth branch road can carry out the control effect of short circuit to second user side heat exchanger 10 to satisfy the user demand of more operating modes.

In some embodiments, a seventeenth branch 417 is further disposed in the thirteenth branch 413 and the fourteenth branch 414, one end of the seventeenth branch 417 is connected to the second heat source heat exchanger 8 and passes through an eighteenth branch 418, the other end of the eighteenth branch 418 is connected to the eighth branch 408, the refrigerant in the seventeenth branch 417 exchanges heat with the second heat source in the second heat source heat exchanger 8, a fifteenth control valve 96 is disposed on the seventeenth branch 417, and a sixteenth control valve 97 is disposed on the eighteenth branch 418. The thirteenth branch can be effectively communicated to the second heat source heat exchanger through the seventeenth branch and communicated to the compressor through the eighteenth branch, so that the first and second use-side heat exchangers are effectively connected with the second heat source heat exchanger to form a loop, and heat absorption and heating or heat release and cooling are carried out from the second heat source heat exchanger.

In some embodiments, a nineteenth branch 419 is further included, the nineteenth branch 419 has one end connected to the eleventh branch 411 and the other end connected to the second suction line 200, so that the second usage-side heat exchanger 10 can be connected to the second suction line 200, the second suction line 200 has one end connected to the second cylinder and the other end connected to the eighteenth branch 418, a second control valve 22 is disposed on the second suction line 200, a thirteenth control valve 94 is disposed on the nineteenth branch 419, and the other end of the nineteenth branch 419 is connected to a position between the second control valve 22 and the compressor on the second suction line 200. Can communicate the eleventh branch road that second user side heat exchanger was located back to the second through setting up the nineteenth branch road effectively and inhale the pipeline in, this kind of condition is applicable to the second and uses the side heat exchanger and be in under the refrigeration mode, can inhale the pipeline with first user side heat exchanger and second respectively through first pipeline and the second of breathing in and communicate to two different cylinders of compressor, effectively realize different evaporating temperature's refrigeration effect, improve energy utilization, satisfy indoor different refrigerating temperature's demand.

In some embodiments, the other end of the fourth branch 404 and the other end of the fifth branch 405 are merged to a twentieth branch 420, one end of the twentieth branch 420 is connected to the second heat source heat exchanger 8 and is led out through a twenty-first branch 421, the other end of the twenty-first branch 421 is connected to the eighth branch 408, the refrigerant in the twentieth branch 420 exchanges heat with the second heat source in the second heat source heat exchanger 8, a third throttling device 43 is arranged on the twentieth branch 420, and a ninth control valve 76 is arranged on the twenty-first branch 421. The pipeline of the first heat source heat exchanger can be communicated to the second heat source heat exchanger for heat exchange through the arrangement of the twentieth branch, the condition is suitable for the condition that a certain subsection part in the first heat source heat exchanger is frosted or needs to be defrosted, the subsection part is defrosted by absorbing heat from the second heat source heat exchanger, and the other subsection part can also continuously absorb heat to meet the requirement of heating at the use side.

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

The present disclosure also provides a control method of a dual evaporating temperature heat pump system as in any one of the preceding claims, wherein: and controlling the double-evaporation-temperature heat pump system to switch between heating non-defrosting, heating defrosting and refrigerating operation modes.

In some embodiments, the refrigerant is controlled to exchange heat with a first heat source in the first heat source heat exchanger 6 and/or the refrigerant is controlled to exchange heat with a second heat source in the second heat source heat exchanger 8 when heating is not defrosting;

when heating and defrosting are carried out, 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;

and when in a 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.

This is the control form of several preferred operation modes of the heat pump system of this disclosure, namely, the preferred control action in heating not defrosting, heating defrosting simultaneously and cooling mode.

The system can realize refrigeration, heating and heat recovery, and improve the utilization rate of equipment.

When the system operates in winter, the defrosting mode can be divided into a control strategy of a defrosting mode and a control strategy of heating without defrosting according to whether defrosting is needed:

the defrosting mode system control strategy is as follows:

the first mode is as follows: in some embodiments, in the heating and defrosting mode, and when the first heat source heat exchanger 6 and the second heat source heat exchanger 8 are both operating for heating the room and the first heat source heat exchanger 6 needs defrosting,

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 75, the ninth control valve 76, the tenth control valve 91, the eleventh control valve 92, the twelfth control valve 93, the thirteenth control valve 94, the fourteenth control valve 95, the fifteenth control valve 96, the sixteenth control valve 97, the seventeenth control valve 98 are included together, and the first throttling means 41, the second throttling means 42, and the third throttling means 43 are included:

the system starts the first defrosting mode, and controls to open the second control valve 22, open the third control valve 23, open the eleventh control valve 92, open the twelfth control valve 93, open the fifteenth control valve 96, open the seventeenth control valve 98, open the fifth control valve 72, open the sixth control valve 73, open the eighth control valve 75 and open the ninth control valve 76, and controls to close the first control valve 21, close the tenth control valve 91, close the thirteenth control valve 94, close the fourteenth control valve 95, close the sixteenth control valve 97, close the fourth control valve 71 and close the seventh control valve 74, and opens the first throttling device 41, opens the second throttling device 42 and opens the third throttling device 43.

The first mode is as follows: when the first heat source heat exchanger 6 and the second heat source heat exchanger 8 both perform heating and the first heat source heat exchanger 6 needs defrosting, the system starts a defrosting mode one, and the system cycle of the working condition is as follows: the refrigerant flowing out of the discharge port of the compressor 3 passes through the four-way valve 5, and a portion of the refrigerant passes through the eleventh control valve 92 and the twelfth control valve 93 and enters the first usage-side heat exchanger 1 and the second usage-side heat exchanger 10, respectively, and releases heat, and the refrigerant flowing through the first usage-side heat exchanger 1 is throttled by the first throttling device 41 and enters the first heat source heat exchanger 6 through the fifth control valve 72, and the portion of the refrigerant absorbs heat in the first heat source heat exchanger 6 and passes through the seventeenth control valve 98 after absorbing heat. The refrigerant flowing through the second usage-side heat exchanger 10 is throttled by the second throttling device 42, enters the second heat source heat exchanger 8 through the fifteenth control valve 96 to absorb heat, and enters one independent cylinder of the compressor 3 through the second control valve 22 to be compressed. And the other part of the refrigerant which comes out of the exhaust port of the compressor 3 and passes through the four-way valve 5 enters the other section of the first heat source heat exchanger 6 through the eighth control valve 75 and the sixth control valve 73, the part of the refrigerant releases heat and defrosts in the first heat source heat exchanger 6, after releasing heat, the part of the refrigerant is throttled by the third throttling device 43 and then enters the second heat source heat exchanger 8 to absorb heat, after absorbing heat, the part of the refrigerant passes through the ninth control valve 76, is mixed with the refrigerant passing through the seventeenth control valve 98 and then enters the other independent cylinder of the compressor 3 through the four-way valve 5 and the third control valve 23 to be compressed, and after being compressed, all the refrigerants. After defrosting of one section of the first heat source heat exchanger 6 is finished, the other section of the first heat source heat exchanger 6 can be defrosted by adjusting the fourth control valve 71, the fifth control valve 72, the sixth control valve 73 and the seventh control valve 74.

And a second mode: in some embodiments, in the heating and defrosting mode, and when only the first heat source heat exchanger 6 is operating for heating the room and the first heat source heat exchanger 6 needs defrosting,

the system starts the second defrosting mode, and controls to open the first control valve 21, open the third control valve 23, open the eleventh control valve 92, open the twelfth control valve 93, open the fourteenth control valve 95, open the seventeenth control valve 98, open the fifth control valve 72, open the sixth control valve 73, open the eighth control valve 75, and open the ninth control valve 76, and controls to close the second control valve 22, close the tenth control valve 91, close the thirteenth control valve 94, close the fifteenth control valve 96, close the sixteenth control valve 97, close the fourth control valve 71, and close the seventh control valve 74, open the first throttling device 41, open the second throttling device 42, and open the third throttling device 43.

And a second mode: when the first heat source heat exchanger 6 is independently used for heating and defrosting is needed, the system starts a second defrosting mode, and the system under the working condition circulates as follows: the refrigerant flowing out of the discharge port of the compressor 3 passes through the four-way valve 5, a part of the refrigerant passes through the eleventh control valve 92 and the twelfth control valve 93 and enters the first use side heat exchanger 1 and the second use side heat exchanger 10 respectively to release heat, the refrigerant flowing through the first use side heat exchanger 1 is throttled by the first throttling device 41, the refrigerant flowing through the second use side heat exchanger 10 is throttled by the second throttling device 42 and passes through the fourteenth control valve 95, the refrigerant is mixed with the refrigerant throttled by the first throttling device 41 and enters the first heat source heat exchanger 6 through the fifth control valve 72, and the refrigerant absorbs heat in the first heat source heat exchanger 6 and passes through the seventeenth control valve 98 after absorbing heat. And the other part of the refrigerant which comes out of the exhaust port of the compressor 3 and passes through the four-way valve 5 enters the other section of the first heat source heat exchanger 6 through the eighth control valve 75 and the sixth control valve 73, the part of the refrigerant releases heat and defrosts in the first heat source heat exchanger 6, after releasing heat, the part of the refrigerant is throttled by the third throttling device 43 and then enters the second heat source heat exchanger 8 to absorb heat, after absorbing heat, the part of the refrigerant passes through the ninth control valve 76, is mixed with the refrigerant passing through the seventeenth control valve 98 and then enters two independent parallel cylinders of the compressor 3 through the four-way valve 5, the third control valve 23 and the first control valve 21 to be compressed, and after being compressed, the refrigerant is. After defrosting of one section of the first heat source heat exchanger 6 is finished, the other section of the first heat source heat exchanger 6 can be defrosted by adjusting the fourth control valve 71, the fifth control valve 72, the sixth control valve 73 and the seventh control valve 74.

When only the second heat source heat exchanger 8 performs heating, the first heat source heat exchanger 6 does not operate, and defrosting is not required.

The control strategy when only heating is needed without defrosting is as follows:

the first mode is as follows:

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

and when the system is started without defrosting, only the heating mode one is needed, the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the eleventh control valve 92 is controlled to be opened, the twelfth control valve 93 is controlled to be opened, the fourteenth control valve 95 is controlled to be opened, the fifteenth control valve 96 is controlled to be opened, the third control valve 23 is controlled to be closed, the tenth control valve 91 is controlled to be closed, the thirteenth control valve 94 is controlled to be closed, the sixteenth control valve 97 is controlled to be closed, the seventeenth control valve 98 is controlled to be closed, the fourth control valve 71 is closed, the fifth control valve 72 is closed, the sixth control valve 73 is closed, the seventh control valve 74 is closed, the eighth control valve 75 is closed, the ninth control valve 76 is closed, the first throttling device 41 is opened, the second throttling device 42 is opened, the third throttling device 43 is closed, and indoor heating is.

The first mode is as follows: when the temperature of the second heat source is high and the heat quantity is large, 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 refrigerant releases heat in the first and second usage-

side heat exchangers

1 and 10, respectively, the refrigerant flowing through the first usage-side heat exchanger 1 is throttled by the first throttling device 41, enters the second heat source heat exchanger 8 through the fourteenth and fifteenth control valves 95 and 96, the refrigerant flowing through the second usage-side heat exchanger 10 is throttled by the second throttling device 42, enters the second heat source heat exchanger 8 through the fifteenth control valve 96, all the refrigerant absorbs heat in the second heat source heat exchanger 8, the refrigerant absorbing heat enters the two independent parallel cylinders of the compressor 3 through the second and first control valves 22 and 21, is compressed, is discharged through the same exhaust port, enters the first and second usage-

side heat exchangers

1 and 10 through the four-way valve 5, the eleventh control valve 92, and the twelfth control valve 93, respectively, and undergoes the next cycle. In this cycle, the indoor side has a single condensing temperature and the outdoor side has a single evaporating temperature.

Defrosting is not needed, and a heating mode II is adopted:

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

and when the system is started and defrosting is not needed, only the heating mode II is needed, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the eleventh control valve 92 is controlled to be opened, the twelfth control valve 93 is controlled to be opened, the fifteenth control valve 96 is controlled to be opened, the fourth control valve 71 is controlled to be opened, the fifth control valve 72 is controlled to be opened, the seventeenth control valve 98 is controlled to be opened, the first control valve 21 is controlled to be closed, the tenth control valve 91 is closed, the thirteenth control valve 94 is controlled to be closed, the fourteenth control valve 95 is controlled to be closed, the sixteenth control valve 97 is closed, the sixth control valve 73 is closed, the seventh control valve 74 is closed, the eighth control valve 75 is closed, the ninth control valve 76 is closed, the first throttling device 41 is opened, the second throttling device 42 is opened, the third throttling device 43 is closed, and indoor heating is carried out through the.

And a second mode: when the temperature of the second heat source is lower and the heat quantity is less, the combined operation of the second heat source heat exchanger 8 and the first heat source heat exchanger 6 is required to meet the heat quantity required by the system. The system circulation process is as follows: a part of the refrigerant releases heat in the first usage-side heat exchanger 1, and after releasing heat, the refrigerant is throttled by the first throttling device 41, then enters the first heat source heat exchanger 6 through the fourth control valve 71 and the fifth control valve 72 to absorb heat, and after absorbing heat, enters one independent cylinder of the compressor 3 through the seventeenth control valve 98, the four-way valve 5 and the third control valve 23 to be compressed. Another part of the refrigerant releases heat in the second usage-side heat exchanger 10, and after releasing the heat, the refrigerant is throttled by the second throttling device 42, then enters the second heat source heat exchanger 8 through the fifteenth control valve 96 to absorb the heat, and enters another independent cylinder of the compressor 3 through the second control valve 22 to be compressed. The two compressed refrigerants are discharged from the discharge port, and enter the first and second use

side heat exchangers

1 and 10 through the four-way valve 5, the eleventh control valve 92, and the twelfth control valve 93, respectively, to perform the next cycle. In this cycle, the indoor side has a single condensing temperature and the outdoor side has a dual evaporating temperature.

Mode three of defrosting and heating is not required:

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

and the system is started without defrosting and only needs a heating mode III, namely, the first control valve 21 is controlled to be opened, the third control valve 23 is controlled to be opened, the eleventh control valve 92 is controlled to be opened, the twelfth control valve 93 is controlled to be opened, the fourteenth control valve 95 is controlled to be opened, the fourth control valve 71 is controlled to be opened, the fifth control valve 72 is controlled to be opened, the seventeenth control valve 98 is controlled to be opened, the second control valve 22 is controlled to be closed, the tenth control valve 91 is closed, the thirteenth control valve 94 is controlled to be opened, the fifteenth control valve 96 is controlled to be closed, the sixteenth control valve 97 is closed, the sixth control valve 73 is closed, the seventh control valve 74 is closed, the eighth control valve 75 is closed, the ninth control valve 76 is closed, the first throttling device 41 is opened, the second throttling device 42 is opened, the third throttling device 43 is closed, and indoor heating.

And a third mode: when the second heat source is not available, it is necessary to use the first heat source heat exchanger 6 alone as the heat source side. The system cycle for this condition is as follows: the refrigerant releases heat in the first and second usage-

side heat exchangers

1 and 10, respectively, the refrigerant flowing through the first usage-side heat exchanger 1 is throttled by the first throttling device 41, then enters the first heat source heat exchanger 6 through the fourth and fifth control valves 71 and 72, the refrigerant flowing through the second usage-side heat exchanger 10 is throttled by the second throttling device 42, then enters the first heat source heat exchanger 6 through the fourteenth, fourth and fifth control valves 95, 71 and 72, all the refrigerant absorbs heat in the first heat source heat exchanger 6, the refrigerant after absorbing heat enters the two independent parallel cylinders of the compressor 3 through the seventeenth, four-way, third and first control valves 5 and 21, is compressed, is discharged through the same exhaust port, and enters the first usage-side heat exchanger 1, through the four-way valve 5, the eleventh and twelfth control valves 92 and 93, respectively, In the second usage-side heat exchanger 10, the next cycle is performed. In this cycle, the indoor side has a single condensing temperature and the outdoor side has a single evaporating temperature.

When the first and second usage-

side heat exchangers

1 and 10 do not need to be operated simultaneously, the refrigerant may be caused to flow through only one of the usage-side heat exchangers by closing the eleventh or twelfth control valve 92 or 93. In this case, the first heat source heat exchanger 6 and the second heat source heat exchanger 8 may be operated independently or simultaneously.

When the system operates in summer, the first heat source heat exchanger and the second heat source heat exchanger can perform different operation control as the cold source side:

the first mode is as follows:

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

the system starts the first cooling mode, the third control valve 23 is controlled to be opened, the eleventh control valve 92 is controlled to be opened, the thirteenth control valve 94 is controlled to be opened, the fourteenth control valve 95 is controlled to be opened, the seventeenth control valve 98 is controlled to be opened, the fourth control valve 71 is controlled to be opened, the fifth control valve 72 is controlled to be opened, the first control valve 21 is controlled to be closed, the second control valve 22 is controlled to be closed, the twelfth control valve 93 is controlled to be closed, the tenth control valve 91 is controlled to be closed, the fifteenth control valve 96 is controlled to be closed, the sixteenth control valve 97 is closed, the sixth control valve 73 is closed, the seventh control valve 74 is closed, the eighth control valve 75 is closed, the ninth control valve 76 is controlled to be closed, the first throttling device 41 is opened, the second throttling device 42 is opened, the third throttling device 43 is closed, and the indoor.

The first mode is as follows: only the first heat source heat exchanger 6 releases heat, and heat recovery is not performed. The system cycle for this condition is as follows: a part of the refrigerant absorbs heat in the first usage-side heat exchanger 1, and the refrigerant having absorbed heat enters one of the independent cylinders of the compressor 3 through the eleventh control valve 92, the four-way valve 5, and the third control valve 23 to be compressed. Another part of the refrigerant absorbs heat in the second usage-side heat exchanger 10, and the refrigerant after absorbing heat is introduced into another independent cylinder of the compressor 3 through the thirteenth control valve 94 to be compressed. All the compressed refrigerant enters the first heat source heat exchanger 6 through the four-way valve 5 and the seventeenth control valve 98 to release heat. The heat-released refrigerant passes through the fourth control valve 71 and the fifth control valve 72, and a part of the refrigerant enters the first expansion device 41 to be expanded, and then enters the first usage-side heat exchanger 1 to perform the next cycle. Another part of the refrigerant passes through the fourteenth control valve 95, enters the second throttling means 42 for throttling, and then enters the second using-side heat exchanger 10 for the next cycle. In this cycle, the indoor side has a double evaporation temperature and the outdoor side has a single condensation temperature.

Summer mode two:

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 the system starts the second cooling mode, and controls to open the third control valve 23, open the eleventh control valve 92, open the thirteenth control valve 94, open the fifteenth control valve 96, open the sixteenth control valve 97, open the seventeenth control valve 98, open the fourth control valve 71 and open the fifth control valve 72, and controls to close the first control valve 21, close the second control valve 22, close the twelfth control valve 93, close the fourteenth control valve 95, close the tenth control valve 91, close the sixth control valve 73, close the seventh control valve 74, close the eighth control valve 75 and close the ninth control valve 76, and opens the first throttling device 41 and opens the second throttling device 42, and closes the third throttling device 43, and simultaneously cools the indoor space through the first heat source heat exchanger 6 and the second heat source heat exchanger 8.

And a second mode: heat is released in the first heat source heat exchanger 6 and the second heat source heat exchanger 8, and part of the heat is recovered by the second heat source heat exchanger 8. The system cycle for this condition is as follows: a part of the refrigerant absorbs heat in the first usage-side heat exchanger 1, and the refrigerant having absorbed heat enters one of the independent cylinders of the compressor 3 through the eleventh control valve 92, the four-way valve 5, and the third control valve 23 to be compressed. Another part of the refrigerant absorbs heat in the second usage-side heat exchanger 10, and the refrigerant after absorbing heat is introduced into another independent cylinder of the compressor 3 through the thirteenth control valve 94 to be compressed. All the compressed refrigerant is discharged through the four-way valve 5, a part of the refrigerant enters the first heat source heat exchanger 6 through the seventeenth control valve 98 to release heat, and the refrigerant after heat release enters the first throttling device 41 through the fourth control valve 71 and the fifth control valve 72 to be throttled, and then enters the first use-side heat exchanger 1 to perform the next cycle. Another part of the refrigerant enters the second heat source heat exchanger 8 through the sixteenth control valve 97 to release heat, the second heat source heat exchanger 8 recovers the part of the heat, and the refrigerant after heat release enters the second throttling device 42 through the fifteenth control valve 96 to be throttled and then enters the second use side heat exchanger 10 to perform the next cycle. In this cycle, the indoor side has a double evaporation temperature and the outdoor side has a single condensation temperature.

Summer mode three:

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

the system starts the cooling mode three, and controls to open the third control valve 23, open the eleventh control valve 92, open the thirteenth control valve 94, open the fourteenth control valve 95, open the fifteenth control valve 96, open the sixteenth control valve 97, control to close the first control valve 21, close the second control valve 22, close the twelfth control valve 93, close the tenth control valve 91, close the seventeenth control valve 98, close the fourth control valve 71, close the fifth control valve 72, close the sixth control valve 73, close the seventh control valve 74, close the eighth control valve 75, close the ninth control valve 76, open the first throttling device 41 and open the second throttling device 42, close the third throttling device 43, and cool the indoor space only through the second heat source heat exchanger 8.

And a third mode: heat is released in the second heat source heat exchanger 8, and the second heat source heat exchanger 8 recovers the whole heat. The system cycle for this condition is as follows: a part of the refrigerant absorbs heat in the first usage-side heat exchanger 1, and the refrigerant having absorbed heat enters one of the independent cylinders of the compressor 3 through the eleventh control valve 92, the four-way valve 5, and the third control valve 23 to be compressed. Another part of the refrigerant absorbs heat in the second usage-side heat exchanger 10, and the refrigerant after absorbing heat is introduced into another independent cylinder of the compressor 3 through the thirteenth control valve 94 to be compressed. All the compressed refrigerant is discharged through the four-way valve 5, enters the second heat source heat exchanger 8 through the sixteenth control valve 97 to release heat, and the second heat source heat exchanger 8 recovers the heat. The heat-released refrigerant flows through the fifteenth control valve 96, and a part of the heat-released refrigerant enters the first throttling device 41 through the fourteenth control valve 95, is throttled, and then enters the first usage-side heat exchanger 1, and is subjected to the next cycle. Another part of the refrigerant enters the second throttling means 42 for throttling and then enters the second using-side heat exchanger 10 for the next cycle. In this cycle, the indoor side has a double evaporation temperature and the outdoor side has a single condensation temperature.

When the first and second usage-

side heat exchangers

1 and 10 do not need to be operated simultaneously, the refrigerant can flow through only one of the usage-side heat exchangers by closing the first and

second throttling devices

41 and 42. In this case, the first heat source heat exchanger 6 and the second heat source heat exchanger 8 may be operated independently or simultaneously.

The present disclosure is to be considered as limited only by the preferred embodiments and not limited to the specific embodiments described herein, and all changes, equivalents and modifications that come within the spirit and scope of the disclosure are desired to be protected. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the technical principle of the present disclosure, and these improvements and modifications should also be considered as the protection scope of the present disclosure.

Claims

1. A dual evaporating temperature heat pump system, comprising:

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 a first heat source in the first heat source heat exchanger (6), and refrigerant exchanges heat with a second heat source in the second heat source heat exchanger (8), the compressor (3) comprises a first cylinder and a second cylinder, the first cylinder is communicated with a first air suction pipeline (100), the second cylinder is communicated with a second air suction pipeline (200), the first use side heat exchanger (1) can be communicated to the first air suction pipeline (100), and the second use side heat exchanger (10) can be communicated to the second air suction pipeline (200); or the first usage-side heat exchanger (1) and the second usage-side heat exchanger (10) can be respectively communicated to a discharge pipeline (300) of the compressor.

2. The dual evaporating temperature heat pump system of claim 1, wherein:

the heat pump system is characterized in that a third control valve (23) is arranged on the first air suction pipeline (100), a second control valve (22) is arranged on the second air suction pipeline (200), the heat pump system further comprises a first branch (401), one end of the first branch (401) is communicated with the first air suction pipeline (100), the other end of the first branch (401) is communicated with the second air suction pipeline (200), and a first control valve (21) is arranged on the first branch (401).

3. The dual evaporating temperature heat pump system of claim 1 or 2, wherein:

the first heat source heat exchanger (6) comprises a first segmented heat exchanging portion (61) and a second segmented heat exchanging portion (62), the heat pump system further comprises a second branch (402), a third branch (403), a fourth branch (404) and a fifth branch (405), the second branch (402) and the third branch (403) are arranged in parallel, the second branch (402) penetrates through the first segmented heat exchanging portion (61), the third branch (403) penetrates through the second segmented heat exchanging portion (62), the fourth branch (404) and the fifth branch (405) are arranged in parallel, the fourth branch (404) penetrates through the first segmented heat exchanging portion (61), and the fifth branch (405) penetrates through the second segmented heat exchanging portion (62);

the second branch (402) is provided with a fourth control valve (71), the third branch (403) is provided with a fifth control valve (72), the fourth branch (404) is provided with a sixth control valve (73), the fifth branch (405) is provided with a seventh control valve (74), and refrigerants in the second branch (402), the third branch (403), the fourth branch (404) and the fifth branch (405) can exchange heat with the first heat source in the first heat source heat exchanger (6) respectively.

4. The dual evaporating temperature heat pump system of claim 3, wherein:

the compressor further comprises a four-way valve (5), wherein a first end (51) of the four-way valve (5) is communicated with a discharge pipeline (300) of the compressor (3);

a second end (52) of the four-way valve (5) is communicated with a seventh branch (407), one end of the fourth branch (404) and one end of the fifth branch (405) are merged to a sixth branch (406), the sixth branch (406) is communicated with the seventh branch (407), and an eighth control valve (75) is arranged on the sixth branch (406);

a third end (53) of the four-way valve (5) is communicated to the first air suction pipeline (100);

the fourth end (54) of the four-way valve (5) is communicated with an eighth branch (408), one end of the second branch (402) and one end of the third branch (403) are converged and communicated to a ninth branch (409), the ninth branch (409) is communicated with the eighth branch (408), and a seventeenth control valve (98) is arranged on the ninth branch (409).

5. The dual evaporating temperature heat pump system of claim 4, wherein:

the branch where the first use side heat exchanger (1) is located is a tenth branch (410), the branch where the second use side heat exchanger (10) is located is an eleventh branch (411), one end of the tenth branch (410) is communicated with one end of the eleventh branch (411) and communicated to the seventh branch (407), an eleventh control valve (92) is arranged on the tenth branch (410), and a twelfth control valve (93) is arranged on the eleventh branch (411).

6. The dual evaporating temperature heat pump system of claim 5, wherein:

the device is characterized by further comprising a twelfth branch (412) and a thirteenth branch (413), wherein one end of the twelfth branch (412) is communicated with the other end of the tenth branch (410), one end of the thirteenth branch (413) is communicated with the other end of the eleventh branch (411), the other end of the twelfth branch (412) is communicated with the other end of the thirteenth branch (413) through a fourteenth branch (414), a first throttling device (41) is arranged on the twelfth branch (412), and a second throttling device (42) is arranged on the thirteenth branch (413); the other end of the second branch (402) and the other end of the third branch (403) are merged and communicated to a fifteenth branch (415), the fifteenth branch (415) is communicated with the fourteenth branch (414), and a fourteenth control valve (95) is arranged on the fourteenth branch (414).

7. The dual evaporating temperature heat pump system of claim 6, wherein:

the tenth branch (410) and the eleventh branch (411) are communicated through a sixteenth branch (416), and a tenth control valve (91) is arranged on the sixteenth branch (416).

8. The dual evaporating temperature heat pump system of claim 6, wherein:

a seventeenth branch (417) is further arranged at a position where the thirteenth branch (413) and the fourteenth branch (414) are connected, one end of the seventeenth branch (417) is communicated with the second heat source heat exchanger (8) and passes through an eighteenth branch (418), the other end of the eighteenth branch (418) is communicated with the eighth branch (408), refrigerant in the seventeenth branch (417) exchanges heat with the second heat source in the second heat source heat exchanger (8), a fifteenth control valve (96) is arranged on the seventeenth branch (417), and a sixteenth control valve (97) is arranged on the eighteenth branch (418).

9. The dual evaporating temperature heat pump system of claim 8, wherein:

the system further comprises a nineteenth branch (419), one end of the nineteenth branch (419) is communicated to the eleventh branch (411), the other end of the nineteenth branch is communicated to the second suction pipeline (200), so that the second use-side heat exchanger (10) can be communicated to the second suction pipeline (200), one end of the second suction pipeline (200) is communicated to the second cylinder, the other end of the second suction pipeline is communicated to the eighteenth branch (418), a second control valve (22) is arranged on the second suction pipeline (200), a thirteenth control valve (94) is arranged on the nineteenth branch (419), and the other end of the nineteenth branch (419) is communicated to a position, between the second control valve (22) and the compressor, on the second suction pipeline (200).

10. The dual evaporating temperature heat pump system of any one of claims 4-9, wherein:

the other end of the fourth branch (404) and the other end of the fifth branch (405) are merged to a twentieth branch (420), one end of the twentieth branch (420) is communicated to the second heat source heat exchanger (8) and is led out through a twenty-first branch (421), the other end of the twenty-first branch (421) is communicated to the eighth branch (408), refrigerant in the twentieth branch (420) exchanges heat with the second heat source in the second heat source heat exchanger (8), a third throttling device (43) is arranged on the twentieth branch (420), and a ninth control valve (76) is arranged on the twenty-first branch (421).

11. The dual evaporating temperature heat pump system of claim 1, wherein:

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