CN112128851B

CN112128851B - Double-evaporation-temperature heat pump system and control method

Info

Publication number: CN112128851B
Application number: CN202010960415.9A
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: 2024-04-12
Anticipated expiration: 2040-09-14
Also published as: CN112128851A

Abstract

The present disclosure provides a dual evaporation temperature heat pump system and a control method, the dual evaporation temperature heat pump system includes 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, a first cylinder of the compressor is communicated with a first air suction pipeline, a second 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 and second use side heat exchangers can be respectively communicated to the discharge line of the compressor. According to the method and the device, double evaporation temperatures can be effectively formed for evaporation, energy sources are saved, and energy efficiency of a system is improved; 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 indoor heating capacity can be effectively improved during defrosting, the maximum degree meets the requirements of indoor environment, and the energy efficiency of the system is improved.

Description

Double-evaporation-temperature heat pump system and control method

Technical Field

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

Background

When the air conditioning system operates in a heating working condition, the temperature of the refrigerant flowing through the heat exchanger of the outdoor unit is very low, and the frosting phenomenon of the heat exchanger of the outdoor unit can be caused. This phenomenon may seriously deteriorate heat exchange of the outdoor unit heat exchanger, thereby affecting heating performance of the entire air conditioning system. Defrosting the heat exchanger of the outdoor unit of the air conditioning system is particularly important. In the defrosting process, indoor continuous heating is ensured, and additional 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 more in technical scheme applied to the heating field, and can realize the functions of double-evaporation temperature heating, defrosting, uninterrupted heating and the like, so that the number of technologies is less. The patent of China patent No. CN208620489U provides a system which has double evaporation temperatures and can realize continuous defrosting and heating, the system comprises 5 heat exchangers, when continuous defrosting and heating is realized, an outdoor heat exchanger which needs defrosting is used as a condenser, one indoor heat exchanger is used as another condenser, and an outdoor heat exchanger which does not need defrosting is used as an evaporator to carry out system circulation. When defrosting, only one indoor heat exchanger is available, the other heat exchanger is in an idle state, the system cannot meet the requirement when more heat is needed, and indoor comfort is affected.

Because the heat pump system in the prior art has the problems that the indoor heating capacity is low during defrosting, so that the requirements of indoor environment cannot be met, and the like, the double-evaporation-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 defect that the indoor heating amount is low when the heat pump system in the prior art is used for defrosting, so that the indoor environment requirement cannot be met, thereby providing a dual-evaporation-temperature heat pump system and a control method.

In order to solve the above-described problems, the present disclosure provides a dual evaporating 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 cylinder and a second cylinder, the first cylinder is communicated with a first air suction pipeline, the second cylinder is communicated with a second air suction pipeline, the first use side heat exchanger can be communicated with the first air suction pipeline, and the second use side heat exchanger can be communicated with the second air suction pipeline; or the first and second use side heat exchangers can be respectively communicated to the exhaust pipeline of the compressor.

In some embodiments, the first air suction pipe is provided with a third control valve, the second air suction pipe is provided with a second control valve, and the heat pump system further comprises a first branch, one end of the first branch is communicated with the first air suction pipe, the other end of the first branch is communicated with the second air suction pipe, and the first branch is provided with a first control valve.

In some embodiments, the first heat source heat exchanger comprises a first segmented heat exchange portion and a second segmented heat exchange portion, the heat pump system further comprises a second leg, a third leg, a fourth leg, and a fifth leg, the second leg and the third leg are disposed in parallel, and the second leg extends through the first segmented heat exchange portion, the third leg extends through the second segmented heat exchange portion, the fourth leg and the fifth leg are disposed in parallel, the fourth leg extends through the first segmented heat exchange portion, and the fifth leg extends through the second segmented heat exchange 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 the refrigerants in the second branch, the third branch, the fourth branch and the fifth branch can exchange heat with the first heat source in the first heat source heat exchanger respectively.

In some embodiments, the compressor further comprises 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 with 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 use side heat exchanger is located is a tenth branch, the branch where the second use side heat exchanger is located is an eleventh branch, one end of the tenth branch is communicated with one end of the eleventh branch and is communicated to the seventh branch, an eleventh control valve is disposed on the tenth branch, and a twelfth control valve is disposed on the eleventh branch.

In some embodiments, the device further comprises a twelfth branch and a thirteenth branch, wherein 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 and the other end of the thirteenth branch are communicated 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 is converged with the other end of the third branch and is 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 in communication through a sixteenth branch, and a tenth control valve is disposed on the sixteenth branch.

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

In some embodiments, the method 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 air suction pipeline, so that the second use side heat exchanger can be communicated to the second air suction pipeline, one end of the second air suction pipeline is communicated to the second cylinder, the other end of the second air suction pipeline is communicated to the eighteenth branch, a second control valve is arranged on the second air 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, located between the second control valve and the compressor, on the second air suction pipeline.

In some embodiments, the other end of the fourth branch and the other end of the fifth branch are converged 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 twentieth first branch, the other end of the twentieth 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 twentieth first 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 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 operation modes of heating without defrosting, heating and defrosting and refrigerating.

In some embodiments, when heating does not defrost, 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;

when heating and defrosting, 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 and defrosting mode, and both the first heat source heat exchanger and the second heat source heat exchanger are operated for heating indoor and when defrosting is required for the first heat source heat exchanger:

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, the fourteenth control valve, the fifteenth control valve, the sixteenth control valve, the seventeenth control valve, and including the first throttle means, the second throttle means, and the third throttle means at the same time:

the system starts a defrosting mode I, controls to open a second control valve, open a third control valve, open an eleventh control valve, open a twelfth control valve, open a fifteenth control valve, open a seventeenth control valve, open a fifth control valve, open a sixth control valve, open an eighth control valve and open a ninth control valve, and controls to close the first control valve, close the eleventh control valve, close the thirteenth control valve, close the fourteenth control valve, close the sixteenth control valve, close the fourth control valve and close the seventh control valve, open the first throttling device, open the second throttling device and open the third throttling device.

In some embodiments, in a heating and defrosting mode, and only when the first heat source heat exchanger is operating to heat an indoor and the first heat source heat exchanger requires defrosting,

the system starts a defrosting mode II, controls to open a first control valve, open a third control valve, open an eleventh control valve, open a twelfth control valve, open a fourteenth control valve, open a seventeenth control valve, open a fifth control valve, open a sixth control valve, open an eighth control valve and open a ninth control valve, and controls to close the second control valve, close the eleventh control valve, close the thirteenth control valve, close the fifteenth control valve, close the sixteenth control valve, close the fourth control valve and close the seventh control valve, open the first throttling device, open the second throttling device and open the third throttling device.

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

the system is started and only needs heating mode one without defrosting, the first control valve is controlled to be opened, the second control valve is opened, the eleventh control valve is opened, the twelfth control valve is opened, the fourteenth control valve is opened, the fifteenth control valve is opened, the third control valve is controlled to be closed, the eleventh control valve is controlled to be closed, the thirteenth control valve is closed, the sixteenth control valve is closed, the seventeenth control valve is closed, the fourth control valve is closed, the fifth control valve is closed, the sixth control valve is closed, the seventh control valve is closed, the eighth control valve is closed, the ninth control valve is closed, the first throttling device and the second throttling device are opened, the third throttling device is closed, and indoor heating is performed only through the second heat source heat exchanger.

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

and the system is started and only needs to heat the mode II without defrosting, the second control valve is controlled to be opened, the third control valve is opened, the eleventh control valve is opened, the twelfth control valve is opened, the fifteenth control valve is opened, the fourth control valve is opened, the fifth control valve is opened, the seventeenth control valve is opened, the first control valve is controlled to be closed, the eleventh control valve is closed, the thirteenth control valve is closed, the fourteenth control valve is closed, the sixteenth control valve is closed, the sixth control valve is closed, the seventh control valve is closed, the eighth control valve is closed, the ninth control valve is closed, the first throttling device and the second throttling device are opened, the third throttling device is closed, and meanwhile, the indoor heating is performed through the first heat source heat exchanger and the second heat source heat exchanger.

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

and the system is started and only needs to heat the mode III without defrosting, and controls to open a first control valve, a third control valve, an eleventh control valve, a twelfth control valve, a fourteenth control valve, a fourth control valve, a fifth control valve and a seventeenth control valve, close a second control valve, an eleventh control valve, a thirteenth control valve, a fifteenth control valve, a sixteenth control valve, a sixth control valve, a seventh control valve, an eighth control valve and a ninth control valve, a first throttling device and a second throttling device and a third throttling device are opened, and the indoor heating is performed only through the first 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:

the system starts a refrigeration mode I, controls to open a third control valve, open an eleventh control valve, open a thirteenth control valve, open a fourteenth control valve, open a seventeenth control valve, open a fourth control valve and open a fifth control valve, controls to close a first control valve, close a second control valve, close a twelfth control valve, close the eleventh control valve, close the fifteenth control valve, close a sixteenth control valve, close a sixth control valve, close a seventh control valve, close an eighth control valve and close a ninth control valve, opens a first throttling device and opens a second throttling device, closes a third throttling device, and only uses the first heat source heat exchanger to refrigerate indoor space.

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:

the system starts a second refrigerating mode, controls to open a third control valve, open an eleventh control valve, open a thirteenth control valve, open a fifteenth control valve, open a sixteenth control valve, open a seventeenth control valve, open a fourth control valve and open a fifth control valve, controls to close a first control valve, close a second control valve, close a twelfth control valve, close a fourteenth control valve, close an eleventh control valve, close a sixth control valve, close a seventh control valve, close an eighth control valve and close a ninth control valve, opens a first throttling device and opens a second throttling device, closes a third throttling device, and simultaneously refrigerates indoor 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 second heat source heat exchanger is exothermic for heat recovery:

the system starts a refrigeration mode III, controls to open a third control valve, open an eleventh control valve, open a thirteenth control valve, open a fourteenth control valve, open a fifteenth control valve and open a sixteenth control valve, controls to close the first control valve, close the second control valve, close the twelfth control valve, close the eleventh control valve, close the seventeenth control valve, close the fourth control valve, close the fifth control valve, close the sixth control valve, close the seventh control valve, close the eighth control valve and close the ninth control valve, opens the first throttling device and opens the second throttling device, closes the third throttling device, and only uses the second heat source heat exchanger to refrigerate indoor.

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

1. according to the dual-evaporation-temperature-resistant air conditioner, the two air cylinders and the two air suction pipelines are adopted, and the two using side heat exchangers can be communicated to the first air suction pipeline and the second air suction pipeline one to one respectively, so that dual evaporation temperatures can be effectively formed for evaporation, the refrigeration effect of different temperature working conditions can be met when the using side (indoor) is used for refrigeration, energy sources are saved, the energy efficiency is improved, and when the using side (indoor) is used for heating, the heat absorption of different evaporation temperatures is carried out by two different heat sources, the evaporation heat absorption capacity of the heat sources with different temperatures can be effectively improved, and the energy efficiency of a system 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, so that the system is suitable for the condition of unstable heat source conditions in winter, fully utilizes energy according to the characteristics of different heat sources, can be used as heat sources of the heat exchanger of the defrosting section when defrosting is needed, fully utilizes the energy, and 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 capacity can be effectively improved during defrosting, the maximum degree meets the requirements of indoor environment, and the energy efficiency of the system is improved;

2. The system circulation overcomes the defect that the room temperature is reduced when the existing heat pump is used for defrosting, and the heat exchanger which needs to be defrosted outdoors is used for sectionally defrosting by adopting the sectionalized heat exchanger, so that uninterrupted heating defrosting is realized, and the room temperature is ensured not to be obviously reduced in the defrosting process. According to the control system, through the control of the four-way valve and the electromagnetic valve, different circulation modes of the system can be realized under different operation conditions, double-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration can be realized in summer, one heat source can be utilized for heating or two heat sources can be utilized for heating simultaneously in winter, 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.

Drawings

Fig. 1 is a system diagram of a dual evaporating temperature heat pump system 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; 41. a first throttle device; 42. a second throttle device; 43. a third throttling device; 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 segmented heat exchange portion; 62. a second segmented heat exchange portion; 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 suction line; 300. an 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. a thirteenth branch; 414. a fourteenth branch; 415. a fifteenth branch; 416. a sixteenth branch; 417. seventeenth branch; 418. an eighteenth branch; 419. nineteenth branch; 420. a twentieth branch; 421. and a twenty-first branch.

Detailed Description

As shown in fig. 1, the present disclosure provides a dual evaporating 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 and the refrigerant exchanging heat with the second heat source in the second heat source heat exchanger 8, the compressor 3 comprising a first cylinder and a second cylinder, the first cylinder being in communication with a first suction line 100, the second cylinder being in communication with a second suction line 200, the first use side heat exchanger 1 being communicable to the first suction line 100, and the second use side heat exchanger 10 being communicable to the second suction line 200; or the first use side heat exchanger 1 and the second use side heat exchanger 10 can be respectively communicated to the discharge line 300 of the compressor.

The present disclosure proposes another system capable of realizing both double evaporating temperature heating and defrosting uninterrupted heating, and adopts double heat sources to supply heat in winter, so as to raise equipment utilization rate and system energy efficiency and indoor comfort.

According to the dual-evaporation-temperature-resistant air conditioner, the two air cylinders and the two air suction pipelines are adopted, and the two using side heat exchangers can be communicated to the first air suction pipeline and the second air suction pipeline one to one respectively, so that dual evaporation temperatures can be effectively formed for evaporation, the refrigeration effect of different temperature working conditions can be met when the using side (indoor) is used for refrigeration, energy sources are saved, the energy efficiency is improved, and when the using side (indoor) is used for heating, the heat absorption of different evaporation temperatures is carried out by two different heat sources, the evaporation heat absorption capacity of the heat sources with different temperatures can be effectively improved, and the energy efficiency of a system 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, so that the system is suitable for the condition of unstable heat source conditions in winter, fully utilizes energy according to the characteristics of different heat sources, can be used as heat sources of the heat exchanger of the defrosting section when defrosting is needed, fully utilizes the energy, and 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 capacity can be effectively improved during defrosting, the maximization degree meets the requirements of indoor environments, and the energy efficiency is improved.

In some embodiments, the first air suction pipeline 100 is provided with a third control valve 23, the second air suction pipeline 200 is provided with a second control valve 22, and 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 the first branch 401 is provided with a first control valve 21. The third control valve arranged on the first air suction pipeline can control the air suction pipeline, the second control valve arranged on the second air suction pipeline can control the air suction pipeline, and the first branch can communicate the two air suction pipelines, so that the air suction pressures of the two air cylinders are equal to adapt to different air suction working conditions.

In some embodiments, the first heat source heat exchanger 6 includes a first segmented heat exchange portion 61 and a second segmented heat exchange portion 62, the heat pump system further includes a second leg 402, a third leg 403, a fourth leg 404, and a fifth leg 405, the second leg 402 and the third leg 403 are disposed in parallel, and the second leg 402 extends through the first segmented heat exchange portion 61, the third leg 403 extends through the second segmented heat exchange portion 62, the fourth leg 404 and the fifth leg 405 are disposed in parallel, the fourth leg 404 extends through the first segmented heat exchange portion 61, and the fifth leg 405 extends through the second segmented heat exchange 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 the refrigerant 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 used for defrosting, and the heat exchanger which needs to be defrosted outdoors is used for sectionally defrosting by adopting the sectionalized heat exchanger, so that uninterrupted heating defrosting is realized, and the room temperature is ensured not to be obviously reduced in the defrosting process.

In some embodiments, 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;

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 converged 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;

The third end 53 of the four-way valve 5 is communicated with 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 communicated to a ninth branch 409 in a converging way, 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 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-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration can be realized in summer, one heat source can be utilized for heating or two heat sources can be utilized for heating simultaneously in winter, 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 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 an electromagnetic valve) and the like. The first heat source heat exchanger belongs to a sectional heat exchanger, when the heat exchanger needs to defrost in winter, one section of heat exchanger can be used as a condenser for defrosting, the other section of heat exchanger is used as an evaporator for heating, after the defrosting of the one section of heat exchanger is finished, the two sections of heat exchangers can be switched, and the other section of heat exchanger is defrosted until the defrosting of the two sections of heat exchangers is finished. Thus, 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 of independent operation, simultaneous operation and the like by controlling the four-way valve and the control valve, can realize double-evaporation-temperature refrigeration or single-evaporation-temperature refrigeration in summer, can utilize one heat source to heat or simultaneously utilize two heat sources to heat in winter, improves the operation energy efficiency of the system, and ensures that the system operates optimally.

In some embodiments, the branch where the first usage-side heat exchanger 1 is located is a tenth branch 410, the branch where the second usage-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 is communicated with 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 set up first use side heat exchanger and second use side heat exchanger respectively and carry out the evaporation heat transfer of two evaporating temperature under the refrigeration mode effectively to it is different to form the refrigeration temperature that obtains at first use side and the refrigeration temperature that obtains at the second use side, and the evaporation temperature that obtains from first and second heat source heat exchanger is different under the heating mode, and the heat of acquireing is different, improves energy efficiency utilization ratio.

In some embodiments, the device further comprises a twelfth branch 412 and a thirteenth branch 413, 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 and the other end of the thirteenth branch 413 are communicated 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 converged 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 arrangement of the twelfth branch and the thirteenth branch can respectively arrange the first throttling device and the second throttling device on the first throttling device in a one-to-one correspondence manner, so that the refrigerant in the pipeline of the first using side heat exchanger is effectively throttled, the refrigerant in the pipeline of the second using side heat exchanger is effectively throttled, the twelfth branch is communicated with the thirteenth branch, and the thirteenth branch is communicated with the junction of the two parallel branches of the first heat source heat exchanger, so that the first and the second using side heat exchangers are effectively connected with the first heat source heat exchanger to form a loop, and heat absorption heating or heat release cooling is carried out from 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 second use side heat exchanger 10 can be short-circuited under control by the sixteenth branch, so as to meet the use requirements of more working conditions.

In some embodiments, a seventeenth branch 417 is further disposed in a connection position between 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 is led out 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 with the second heat source heat exchanger through the seventeenth branch and discharged to the compressor through the eighteenth branch, so that the first and second using side heat exchangers are effectively connected with the second heat source heat exchanger to form a loop so as to absorb heat from the second heat source heat exchanger or release heat for refrigeration.

In some embodiments, the nineteenth branch 419 is further provided with one end connected to the eleventh branch 411 and the other end connected to the second suction line 200, so that the second use side heat exchanger 10 can be connected to the second suction line 200, one end of the second suction line 200 is connected to the second cylinder, the other end is connected to the eighteenth branch 418, a second control valve 22 is provided on the second suction line 200, a thirteenth control valve 94 is provided 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 a compressor on the second suction line 200. Through setting up nineteenth branch road can be effectively with the eleventh branch road intercommunication that the second use side heat exchanger was located back to the second in the pipeline of breathing in, this kind of condition is applicable to the second and uses side heat exchanger and be in under the refrigeration mode, can be with first use side heat exchanger and second use side heat exchanger respectively through first breathing in pipeline and second breathing in pipeline intercommunication to two different cylinders of compressor, effectively realize the refrigeration effect of different evaporating temperatures, 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 joined 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 disposed on the twentieth branch 420, and a ninth control valve 76 is disposed 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 twentieth branch, the situation is suitable for the situation that a certain subsection part in the first heat source heat exchanger frosts or needs to be frosted, the subsection part is frosted by utilizing the heat absorption from the second heat source heat exchanger, and the other subsection part can continue to absorb the heat effectively so as to meet the heating requirement of 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 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.

In some embodiments, when heating does not defrost, 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;

when heating and defrosting, 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, 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.

This is a form of control of several preferred modes of operation of the heat pump system of the present disclosure, namely heating without defrosting, heating with defrosting, and preferred control actions in the cooling mode.

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

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

the defrost mode system control strategy is:

mode one: in some embodiments, in the heating and defrosting mode, and when both the first heat source heat exchanger 6 and the second heat source heat exchanger 8 are operated for indoor heating 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, the first throttle device 41, the second throttle device 42, and the third throttle device 43 are included:

the system starts the defrosting mode one, 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, control 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, open the first throttle device 41, open the second throttle device 42 and open the third throttle device 43.

Mode one: when both the first heat source heat exchanger 6 and the second heat source heat exchanger 8 are heating and the first heat source heat exchanger 6 needs defrosting, the system starts the defrosting mode I, and the system under the working condition circulates as follows: the refrigerant discharged from the discharge port of the compressor 3 passes through the four-way valve 5, and a part of the refrigerant passes through the eleventh control valve 92 and the twelfth control valve 93, respectively enters the first use side heat exchanger 1 and the second use side heat exchanger 10, releases heat, and then the refrigerant flowing through the first use side heat exchanger 1 is throttled by the first throttle device 41, passes through the fifth control valve 72, enters a first heat source heat exchanger 6, 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 throttle device 42, enters the second heat source heat exchanger 8 through the fifteenth control valve 96 to absorb heat, and then enters the individual cylinder of the compressor 3 through the second control valve 22 to be compressed. The other part of the refrigerant which comes out from 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 is discharged in the first heat source heat exchanger 6 for defrosting, is throttled by the third throttling device 43 after heat release, enters the second heat source heat exchanger 8 for absorbing heat, passes through the ninth control valve 76 after absorbing heat, is mixed with the refrigerant which passes through the seventeenth control valve 98, enters the other independent cylinder of the compressor 3 through the four-way valve 5 and the third control valve 23 for compression, and all the refrigerant after compression is discharged through the same exhaust port for the next cycle. After defrosting of one stage of the first heat source heat exchanger 6 is completed, the other stage 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.

Mode two: in some embodiments, in the heating and defrosting mode, and only when the first heat source heat exchanger 6 is operated for heating the room and the first heat source heat exchanger 6 needs defrosting,

the system starts the defrosting mode two, 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, control 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 throttle device 41, open the second throttle device 42 and open the third throttle device 43.

Defrosting mode two: when the first heat source heat exchanger 6 is used for heating independently and defrosting is needed, the system starts the defrosting mode II, and the system under the working condition circulates as follows: part of the refrigerant discharged from the discharge port of the compressor 3 passes through the four-way valve 5, passes through the eleventh control valve 92 and the twelfth control valve 93, respectively enters the first use side heat exchanger 1 and the second use side heat exchanger 10, releases 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, passes through the fourteenth control valve 95, is mixed with the refrigerant throttled by the first throttling device 41, passes through the fifth control valve 72, enters the first heat source heat exchanger 6, absorbs heat in the first heat source heat exchanger 6, and passes through the seventeenth control valve 98. The other part of the refrigerant which comes out from 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 is discharged in the first heat source heat exchanger 6 for defrosting, is throttled by the third throttling device 43 after heat release, enters the second heat source heat exchanger 8 for absorbing heat, passes through the ninth control valve 76 after absorbing heat, is mixed with the refrigerant which passes through the seventeenth control valve 98, and enters the two independent parallel cylinders of the compressor 3 for compression through the four-way valve 5, the third control valve 23 and the first control valve 21, and the compressed refrigerant is discharged through the same exhaust port for the next cycle. After defrosting of one stage of the first heat source heat exchanger 6 is completed, the other stage 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 heats, the first heat source heat exchanger 6 does not operate, and defrosting is not required.

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

mode one:

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

the system is started and only needs heating mode one without defrosting, and controls to open the first control valve 21, open the second control valve 22, open the eleventh control valve 92, open the twelfth control valve 93, open the fourteenth control valve 95, open the fifteenth control valve 96, control to close the third control valve 23, close the tenth control valve 91, close the thirteenth control valve 94, close the sixteenth control valve 97, 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 and close the ninth control valve 76, open the first throttle device 41 and the second throttle device 42, close the third throttle device 43, and heat the room only through the second heat source heat exchanger 8.

Mode one: 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 refrigerant releases heat in the first use side heat exchanger 1 and the second use side heat exchanger 10 respectively, the refrigerant flowing through the first use side heat exchanger 1 is throttled by the first throttle device 41, enters the second heat source heat exchanger 8 through the fourteenth control valve 95 and the fifteenth control valve 96, the refrigerant flowing through the second use side heat exchanger 10 is throttled by the second throttle 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 after absorbing heat enters two independent parallel cylinders of the compressor 3 through the second control valve 22 and the first control valve 21 for compression, the compressed refrigerant is discharged through the same exhaust port, and enters the first use side heat exchanger 1 and the second use side heat exchanger 10 through the four-way valve 5, the eleventh control valve 92 and the twelfth control valve 93 respectively for next circulation. In this cycle, the indoor side has a single condensing temperature and the outdoor side has a single evaporating temperature.

Defrosting and heating mode two are not needed:

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

the system starts up and only needs heating mode two without defrosting, 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 fourth control valve 71, open the fifth control valve 72, open the seventeenth control valve 98, control 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 sixth control valve 73, close the seventh control valve 74, close the eighth control valve 75 and close the ninth control valve 76, open the first throttle device 41 and the second throttle device 42, close 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.

Mode two: 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: a part of the refrigerant releases heat in the first use side heat exchanger 1, and after releasing heat, the refrigerant is throttled by the first throttle device 41, 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 the independent cylinder of the compressor 3 through the seventeenth control valve 98, the four-way valve 5 and the third control valve 23 to compress. 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 second throttling device 42, then enters the second heat source heat exchanger 8 through the fifteenth control valve 96 to absorb heat, and after absorbing heat, enters the other independent cylinder of the compressor 3 to compress through the second control valve 22. The two compressed refrigerants are discharged from the exhaust port, and enter the first use side heat exchanger 1 and the second use side heat exchanger 10 through the four-way valve 5, the eleventh control valve 92, and the twelfth control valve 93, respectively, and then the next cycle is performed. In this cycle, the indoor side has a single condensing temperature and the outdoor side has a double evaporating temperature.

Mode three without defrost and heating:

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

the system starts up and only needs heating mode three without defrosting, 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 fourth control valve 71, open the fifth control valve 72, open the seventeenth control valve 98, control to close the second control valve 22, close the tenth control valve 91, close the thirteenth control valve 94, open the fifteenth control valve 96, close the sixteenth control valve 97, 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, open the first throttle device 41 and the second throttle device 42, close the third throttle device 43, and heat the room only through the first heat source heat exchanger 6.

Mode three: 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 refrigerant releases heat in the first use side heat exchanger 1 and the second use side heat exchanger 10 respectively, the refrigerant flowing through the first use side heat exchanger 1 is throttled by the first throttle device 41, then enters the first heat source heat exchanger 6 through the fourth control valve 71 and the fifth control valve 72, the refrigerant flowing through the second use side heat exchanger 10 is throttled by the second throttle device 42, then enters the first heat source heat exchanger 6 through the fourteenth control valve 95, the fourth control valve 71 and the fifth control valve 72, all the refrigerant absorbs heat in the first heat source heat exchanger 6, the refrigerant after absorbing heat enters two independent parallel cylinders of the compressor 3 through the seventeenth control valve 98, the four-way valve 5, the third control valve 23 and the first control valve 21 for compression, the compressed refrigerant is discharged through the same exhaust port, and enters the first use side heat exchanger 1 and the second use side heat exchanger 10 through the four-way valve 5, the eleventh control valve 92 and the twelfth control valve 93 respectively for next circulation. 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 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 eleventh or twelfth control valve 92 or 93. 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.

When the system is operated in summer, the first heat source heat exchanger and the second heat source heat exchanger can be used as cold source sides to carry out different operation control:

mode one:

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:

The system starts the first 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 fourteenth control valve 95, open the seventeenth control valve 98, open the fourth control valve 71 and open the fifth control valve 72, 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 fifteenth control valve 96, close the sixteenth control valve 97, 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, open the first throttle device 41 and open the second throttle device 42, close the third throttle device 43, and cool the room only through the first heat source heat exchanger 6.

Mode one: 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 use side heat exchanger 1, and the refrigerant after absorbing heat enters an independent cylinder of the compressor 3 to be compressed through the eleventh control valve 92, the four-way valve 5, and the third control valve 23. The other part of the refrigerant absorbs heat in the second use side heat exchanger 10, and the refrigerant after absorbing heat enters the other 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 refrigerant after heat release passes through the fourth control valve 71 and the fifth control valve 72, and a part of the refrigerant enters the first throttle device 41 to be throttled, and then enters the first use side heat exchanger 1 to be subjected to the next cycle. Another portion of the refrigerant passes through the fourteenth control valve 95, enters the second throttling device 42 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 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:

the system starts the second cooling mode, 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, 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, open the first throttle device 41 and open the second throttle device 42, close the third throttle device 43, and simultaneously cools the room through the first heat source heat exchanger 6 and the second heat source heat exchanger 8.

Mode two: 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: a part of the refrigerant absorbs heat in the first use side heat exchanger 1, and the refrigerant after absorbing heat enters an independent cylinder of the compressor 3 to be compressed through the eleventh control valve 92, the four-way valve 5, and the third control valve 23. The other part of the refrigerant absorbs heat in the second use side heat exchanger 10, and the refrigerant after absorbing heat enters the other 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 released refrigerant 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 be subjected to the next cycle. The other 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 heat, and the released refrigerant 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 be subjected to 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 the cooling mode, and only when the second heat source heat exchanger 8 is exothermic for heat recovery:

the system starts the refrigeration 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 and close the ninth control valve 76, open the first throttle device 41 and open the second throttle device 42, close the third throttle device 43, and cool the room only through the second heat source heat exchanger 8.

Mode three: the heat is released in the second heat source heat exchanger 8, and the second heat source heat exchanger 8 recovers the entire heat. The system cycle for this condition is as follows: a part of the refrigerant absorbs heat in the first use side heat exchanger 1, and the refrigerant after absorbing heat enters an independent cylinder of the compressor 3 to be compressed through the eleventh control valve 92, the four-way valve 5, and the third control valve 23. The other part of the refrigerant absorbs heat in the second use side heat exchanger 10, and the refrigerant after absorbing heat enters the other 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 refrigerant after heat release flows through the fifteenth control valve 96, and a part of the refrigerant passes through the fourteenth control valve 95 to enter the first throttling device 41 to be throttled, and then enters the first use side heat exchanger 1 to be subjected to the next cycle. Another portion of the refrigerant enters the second throttling means 42 to be throttled and then enters the second use 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 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 first and second throttling means 41, 42. 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

1. A dual evaporating 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 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 use side heat exchanger (1) and the second use side heat exchanger (10) can be respectively communicated to a discharge pipeline (300) of the compressor;

The first heat source heat exchanger (6) comprises a first segmented heat exchange part (61) and a second segmented heat exchange part (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 exchange part (61), the third branch (403) penetrates through the second segmented heat exchange part (62), the fourth branch (404) and the fifth branch (405) are arranged in parallel, the fourth branch (404) penetrates through the first segmented heat exchange part (61), and the fifth branch (405) penetrates through the second segmented heat exchange part (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 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 respectively in the first heat source heat exchanger (6).

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

Be provided with third control valve (23) on first suction line (100), be provided with second control valve (22) on second suction line (200), just heat pump system still includes first branch road (401), the one end intercommunication of first branch road (401) first suction line (100), the other end intercommunication of first branch road (401) second suction line (200), be provided with first control valve (21) on first branch road (401).

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

the compressor also 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);

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 converged 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 with 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 communicated to a ninth branch (409) in a combined mode, the ninth branch (409) is communicated with the eighth branch (408), and a seventeenth control valve (98) is arranged on the ninth branch (409).

4. A dual evaporating temperature heat pump system as in claim 3, wherein:

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

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

the device further comprises 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 converged 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).

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

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

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

a seventeenth branch (417) is further arranged at the connection position of the thirteenth branch (413) and the fourteenth branch (414) in a communicating manner, one end of the seventeenth branch (417) is communicated to the second heat source heat exchanger (8) and is led out through an eighteenth branch (418), the other end of the eighteenth branch (418) is communicated 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 arranged on the seventeenth branch (417), and a sixteenth control valve (97) is arranged on the eighteenth branch (418).

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

the utility model also comprises a nineteenth branch (419), one end of the nineteenth branch (419) is communicated with the eleventh branch (411), the other end of the nineteenth branch (419) is communicated with the second air suction pipeline (200), so that the second use side heat exchanger (10) can be communicated with the second air suction pipeline (200), one end of the second air suction pipeline (200) is communicated with the second cylinder, the other end of the second air suction pipeline is communicated with the eighteenth branch (418), a second control valve (22) is arranged on the second air 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 with a position, which is arranged between the second control valve (22) and the compressor, on the second air suction pipeline (200).

9. A dual evaporating temperature heat pump system as in claim 3, wherein:

the other end of the fourth branch (404) and the other end of the fifth branch (405) are converged 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 twentieth first branch (421), the other end of the twentieth first branch (421) is communicated 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 twentieth first branch (421).

10. The dual evaporating temperature heat pump system of any of claims 1-9, wherein:

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

11. A control method of a double evaporation temperature heat pump system as defined in any one of claims 1 to 10, characterized by: and controlling the double-evaporation-temperature heat pump system to switch between operation modes of heating without defrosting, heating and defrosting and refrigerating.

12. The control method according to claim 11, characterized in that:

When heating is not defrosting, 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);

when heating and defrosting, 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, 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).

13. The control method according to claim 12, characterized in that:

in the heating and defrosting mode, when the first heat source heat exchanger (6) and the second heat source heat exchanger (8) are both used for indoor heating and defrosting is needed for the first heat source heat exchanger (6),

and when including 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), and including the first throttle device (41), the second throttle device (42), and the third throttle device (43), the fourth throttle device is provided with the fourth throttle device (96) and the fifth throttle device (43):

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

14. The control method according to claim 12, characterized in that:

in a heating and defrosting mode, and when only the first heat source heat exchanger (6) works to heat the room and defrosting is needed by the first heat source heat exchanger (6),

The system starts a defrosting mode II, and controls to open a first control valve (21), open a third control valve (23), open an eleventh control valve (92), open a twelfth control valve (93), open a fourteenth control valve (95), open a seventeenth control valve (98), open a fifth control valve (72), open a sixth control valve (73), open an eighth control valve (75) and open a 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 a sixteenth control valve (97), close the fourth control valve (71) and close the seventh control valve (74), open a first throttling device (41), open a second throttling device (42) and open a third throttling device (43).

15. The control method according to claim 12, characterized in that:

in a heating and non-defrosting 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 without defrosting, controls to open a first control valve (21), open a second control valve (22), open an eleventh control valve (92), open a twelfth control valve (93), open a fourteenth control valve (95), open a fifteenth control valve (96), control to close a third control valve (23), close a tenth control valve (91), close a thirteenth control valve (94), close a sixteenth control valve (97), close a seventeenth control valve (98), close a fourth control valve (71), close a fifth control valve (72), close a sixth control valve (73), close a seventh control valve (74), close an eighth control valve (75) and close a ninth control valve (76), open a first throttling device (41) and open a second throttling device (42), close a third throttling device (43), and heat the room only through the second heat source heat exchanger (8).

16. The control method according to claim 12, characterized in that:

in a heating and non-defrosting mode, and when the temperature of the second heat source heat exchanger (8) is lower than a preset temperature:

The system starts a heating mode II without defrosting, controls to open a second control valve (22), open a third control valve (23), open an eleventh control valve (92), open a twelfth control valve (93), open a fifteenth control valve (96), open a fourth control valve (71), open a fifth control valve (72), open a seventeenth control valve (98), control to close the first control valve (21), close the tenth control valve (91), close a thirteenth control valve (94), close a fourteenth control valve (95), close a sixteenth control valve (97), close a sixth control valve (73), close a seventh control valve (74), close an eighth control valve (75) and close a ninth control valve (76), open a first throttling device (41) and open a second throttling device (42), close a third throttling device (43), and simultaneously heat indoor through the first heat source heat exchanger (6) and the second heat source heat exchanger (8).

17. The control method according to claim 12, characterized in that:

in a heating and non-defrosting mode, and when the second heat source heat exchanger (8) is not available:

Heating mode three is needed when the system starts without defrosting, 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 controlled to be 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 controlled to be closed, the sixth control valve (73) is controlled to be closed, the seventh control valve (74) is controlled to be closed, the eighth control valve (75) is controlled to be closed, the ninth control valve (76) is controlled to be opened, the first throttling device (41) is controlled to be opened, the second throttling device (42) is controlled to be closed, the third throttling device (43) is controlled to be opened, and indoor heating is only performed through the first heat source heat exchanger (6).

18. The control method according to claim 12, characterized in that:

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 I, controls to open a third control valve (23), open an eleventh control valve (92), open a thirteenth control valve (94), open a fourteenth control valve (95), open a seventeenth control valve (98), open a fourth control valve (71) and open a fifth control valve (72), controls 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 fifteenth control valve (96), close the sixteenth control valve (97), 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), open the first throttling device (41) and open the second throttling device (42), close the third throttling device (43), and refrigerates the indoor space only through the first heat source heat exchanger (6).

19. The control method according to claim 12, characterized in that:

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:

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

20. The control method according to claim 12, characterized in that:

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