CN213334691U - Double-condensation temperature heat pump system - Google Patents
Double-condensation temperature heat pump system Download PDFInfo
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- CN213334691U CN213334691U CN202022008589.3U CN202022008589U CN213334691U CN 213334691 U CN213334691 U CN 213334691U CN 202022008589 U CN202022008589 U CN 202022008589U CN 213334691 U CN213334691 U CN 213334691U
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Abstract
The utility model provides a double-condensing temperature heat pump system, including compressor, first heat source heat exchanger, second heat source heat exchanger, first use side heat exchanger and second use side heat exchanger, first use side heat exchanger can communicate to first exhaust pipe and second use side heat exchanger can communicate to second exhaust pipe; or the first use-side heat exchanger and the second use-side heat exchanger can be respectively communicated to a suction pipeline of the compressor. According to the present disclosure, double condensing temperatures can be provided, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, according to the provided double-condensation temperature, the heat source heat exchanger can supply heat and hot water to meet different requirements, and the heat source heat exchangers of two different heat sources can fully utilize energy sources according to the characteristics of different heat sources, so that the system can stably, energy-saving and efficiently run; the indoor heating performance or the hot water heating performance is improved, the normal heat supply or hot water requirement is met, and the energy efficiency is greatly improved.
Description
Technical Field
The disclosure relates to the technical field of air conditioners, in particular to a double-condensation-temperature heat pump system.
Background
Prior art patents provide a cycle system with dual condensing temperatures, including an evaporator, two condensers, and a compressor with dual discharge ports. The system reduces the condensing temperature of part of refrigerants, reduces the power consumption of the vapor compression refrigeration/heat pump compressor and improves the efficiency of the vapor compression refrigeration/heat pump system by increasing the number of the exhaust pressure of the compressor in a single refrigerant loop. However, the system is used for heating in winter or refrigerating in summer, switching in winter and summer cannot be performed, the system is simple to control, and flexible adjustment cannot be performed when actual loads are variable.
Because the heat pump system in the prior art has the problems that the indoor heating performance or the hot water heating performance is lower due to the fact that a heat source is unstable in winter, the normal heat supply or hot water demand cannot be met, the energy efficiency is lower and the like, the double-condensation-temperature heat pump system is researched and designed according to the disclosure.
SUMMERY OF THE UTILITY MODEL
Therefore, the technical problem to be solved by the present disclosure is mainly to overcome the defects that the heat pump system in the prior art has low indoor heating performance or low hot water heating performance due to unstable heat source in winter, cannot meet the requirement of normal heat supply or hot water, and has low energy efficiency, thereby providing a dual-condensing temperature heat pump system.
In order to solve the above problem, the present disclosure provides a dual condensing temperature heat pump system, wherein:
the heat exchanger comprises a compressor, a first heat source heat exchanger, a second heat source heat exchanger, a first use side heat exchanger and a second use side heat exchanger, wherein refrigerant exchanges heat with a first heat source in the first heat source heat exchanger, and the refrigerant exchanges heat with a second heat source in the second heat source heat exchanger, the compressor comprises a first exhaust port, a second exhaust port and an air suction port, the first exhaust port is communicated with a first exhaust pipeline, the second exhaust port is communicated with a second exhaust pipeline, the air suction port is communicated with an air suction pipeline, the first use side heat exchanger can be communicated to the first exhaust pipeline, and the second use side heat exchanger can be communicated to the second exhaust pipeline; or the first usage-side heat exchanger and the second usage-side heat exchanger can be respectively communicated to a suction pipeline of the compressor.
In some embodiments, further comprising a first four-way valve, a first end of the first four-way valve in communication with a first discharge line of the compressor;
the second end of the first four-way valve is communicated with a first branch, the first using side heat exchanger is arranged on the first branch, and a ninth control valve is arranged on the first branch;
the third end of the first four-way valve is communicated to the air suction pipeline through a second branch, and a second control valve is arranged on the second branch;
the fourth end of the first four-way valve is communicated with a third branch, one end of the first heat source heat exchanger is communicated to the third branch through a fourth branch, an eleventh control valve is arranged on the fourth branch, one end of the second heat source heat exchanger is communicated to the third branch through a fifth branch, and a fourth control valve is arranged on the fifth branch.
In some embodiments, further comprising a second four-way valve, a fifth end of the second four-way valve in communication with a second discharge line of the compressor;
a sixth end of the second four-way valve is communicated with a sixth branch, the sixth branch is provided with the second use-side heat exchanger, and the sixth branch is provided with a fourth control valve;
the seventh end of the second four-way valve is communicated with the air suction pipeline, and a third control valve is also arranged between the joint of the air suction pipeline and the second branch and the second four-way valve;
the eighth end of the second four-way valve is communicated with a seventh branch, the seventh branch is communicated to the fifth branch and is positioned between the fourth control valve and the second heat source heat exchanger, and a sixth control valve is further arranged on the fifth branch and between the joint of the fifth branch and the seventh branch and the second heat source heat exchanger.
In some embodiments, the other end of the first using-side heat exchanger is communicated with one end of an eighth branch, the other end of the second using-side heat exchanger is communicated with one end of a ninth branch, a first throttling device is arranged on the eighth branch, and a third throttling device is arranged on the ninth branch;
the other end of the first heat source heat exchanger is communicated with one end of a tenth branch, the other end of the eighth branch is communicated to the tenth branch, the other end of the ninth branch is communicated to the tenth branch, a thirteenth control valve is arranged on the tenth branch between the joint of the tenth branch and the eighth branch and the first heat source heat exchanger, and a twelfth control valve is arranged on the tenth branch between the joint of the tenth branch and the ninth branch.
In some embodiments, the eighth branch and the ninth branch are further communicated through an eleventh branch, and an eighth control valve is disposed on the eleventh branch.
In some embodiments, a twelfth branch is further arranged at the position where the ninth branch meets the tenth branch, one end of the twelfth branch is communicated to the other end of the second heat source heat exchanger, and a fifth control valve is arranged on the twelfth branch.
In some embodiments, the compressor further comprises a flash evaporator, the flash evaporator is connected and arranged on the eighth branch and located at a position between the position where the eighth branch is connected and the first throttling device, a second throttling device is further arranged on the eighth branch and between the position where the tenth branch is connected and the flash evaporator, an air supplementing pipeline of the flash evaporator is communicated to an air supplementing port of the compressor, and a first control valve is arranged on the air supplementing pipeline.
In some embodiments, a thirteenth branch is further disposed between the first branch and the sixth branch in a communicating manner, and a tenth control valve is further disposed on the thirteenth branch.
In some embodiments, the first heat source is an air source and the second heat source is a water source.
The double-condensation-temperature heat pump system provided by the disclosure has the following beneficial effects:
1. according to the heat pump system, the two exhaust ports and the two pipelines are adopted, and the two using side heat exchangers can be communicated with the first exhaust pipeline and the second exhaust pipeline one to one respectively, so that double condensation temperatures can be effectively formed for condensation and heat release, the heating effects under different temperature working conditions are met when the using side (indoor) is used for heating, the energy is saved, the energy efficiency is improved, and the heat release at different condensation temperatures is carried out through the two different heat sources when the using side (indoor) is used for refrigerating, so that the capability of condensation and heat release at the heat sources with different temperatures can be effectively improved, the heat recovery is carried out, and the system energy efficiency is effectively improved; the single-suction double-row compressor is adopted, so that double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, the double-condensation temperature can be provided, so that heat can be supplied, hot water can be supplied, and different requirements can be met. The two heat source heat exchangers with different heat sources can be switched according to different heat source conditions, so that the heat source heat exchanger is suitable for the condition that the heat source conditions are unstable in winter, and the energy is fully utilized according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate; the second heat source heat exchanger can realize heat recovery in summer, and recover partial energy, thereby achieving the effect of fully utilizing energy; the indoor heating performance or the hot water making performance is effectively improved, the requirements of normal heat supply or hot water are met, and the energy efficiency is greatly improved;
2. according to the control method, through the control of the four-way valve and the electromagnetic valve, different circulation modes of the system can be realized under different operation working conditions, double-condensation-temperature heating can be realized in winter, one heat source can be used for refrigeration or two heat sources can be used for refrigeration simultaneously in summer, 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; different combination modes such as independent operation, simultaneous operation and the like can be realized by controlling the four-way reversing valve and the electromagnetic valve, the two evaporators and the two condensers, and the circulation mode can be flexibly selected according to actual requirements.
Drawings
FIG. 1 is a system diagram of a dual condensing temperature heat pump system of the present disclosure;
fig. 2 is a system diagram of a dual condensing temperature heat pump system according to an alternate embodiment 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; 31. a first exhaust port; 32. a second exhaust port; 33. an air suction port; 34. an air supplement port; 41. a first throttling device; 42. a second throttling device; 43. a third throttling means; 5. a flash evaporator; 6. a first heat source heat exchanger; 71. a fourth control valve; 72. a fifth control valve; 73. a sixth control valve; 74. a seventh control valve; 8. a second heat source heat exchanger; 91. an eighth control valve; 92. a ninth control valve; 93. a tenth control valve; 94. an eleventh control valve; 95. a twelfth control valve; 951. a thirteenth control valve; 10. a second use-side heat exchanger; 11. a first four-way valve; 111. a first end; 112. a second end; 113. a third end; 114. a fourth end; 12. a second four-way valve; 121. a fifth end; 122. a sixth terminal; 123. a seventh terminal; 124. an eighth end;
100. an air intake pipeline; 200. an air supply pipeline; 301. a first exhaust line; 302. a second 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. and a thirteenth branch.
Detailed Description
As shown in fig. 1-2, the present disclosure provides a dual condensing temperature heat pump system, wherein:
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, refrigerant exchanges heat with a second heat source in the second heat source heat exchanger 8, the compressor 3 includes a first discharge port 31 and a second discharge port 32, and a suction port 33, the first discharge port 31 communicating with a first discharge line 301, the second discharge port 32 communicating with a second discharge line 302, the suction port 33 communicates with a suction line 100, the first use-side heat exchanger 1 is communicable to the first exhaust line 301, and the second use-side heat exchanger 10 is communicable to the second exhaust line 302; alternatively, the first and second use- side heat exchangers 1 and 10 can be connected to the suction line 100 of the compressor.
According to the heat pump system, the two exhaust ports and the two pipelines are adopted, and the two using side heat exchangers can be communicated with the first exhaust pipeline and the second exhaust pipeline one to one respectively, so that double condensation temperatures can be effectively formed for condensation and heat release, the heating effects under different temperature working conditions are met when the using side (indoor) is used for heating, the energy is saved, the energy efficiency is improved, and the heat release at different condensation temperatures is carried out through the two different heat sources when the using side (indoor) is used for refrigerating, so that the capability of condensation and heat release at the heat sources with different temperatures can be effectively improved, the heat recovery is carried out, and the system energy efficiency is effectively improved; the single-suction double-row compressor is adopted, so that double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, the double-condensation temperature can be provided, so that heat can be supplied, hot water can be supplied, and different requirements can be met. The two heat source heat exchangers with different heat sources can be switched according to different heat source conditions, so that the heat source heat exchanger is suitable for the condition that the heat source conditions are unstable in winter, and the energy is fully utilized according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate; the second heat source heat exchanger can realize heat recovery in summer, and recover partial energy, thereby achieving the effect of fully utilizing energy; the indoor heating performance or the hot water heating performance is effectively improved, the requirement of normal heat supply or hot water is met, and the energy efficiency is greatly improved.
In some embodiments, further comprising a first four-way valve 11, a first end 111 of the first four-way valve 11 being in communication with a first discharge line 301 of the compressor 3;
a second end 112 of the first four-way valve 11 is communicated with a first branch 401, the first usage-side heat exchanger 1 is arranged on the first branch 401, and a ninth control valve 92 is arranged on the first branch 401;
the third end 113 of the first four-way valve 11 is communicated to the suction pipeline 100 through a second branch 402, and a second control valve 22 is arranged on the second branch 402;
the fourth end 114 of the first four-way valve 11 is communicated with a third branch 403, one end of the first heat source heat exchanger 6 is communicated to the third branch 403 through a fourth branch 404, an eleventh control valve 94 is arranged on the fourth branch 404, one end of the second heat source heat exchanger 8 is communicated to the third branch 403 through a fifth branch 405, and a seventh control valve 74 is arranged on the fifth branch 405.
According to the system, through the control of the first four-way valve and the control valve (preferably, the electromagnetic valve), different circulation modes of the system can be realized under different operation working conditions, double-condensation-temperature heating can be realized in winter, one heat source can be used for refrigeration or two heat sources can be used for refrigeration simultaneously in summer, 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; different combination modes such as independent operation, simultaneous operation and the like can be realized by controlling the four-way reversing valve and the electromagnetic valve, the two evaporators and the two condensers, and the circulation mode can be flexibly selected according to actual requirements.
In some embodiments, further comprising a second four-way valve 12, a fifth end 121 of said second four-way valve 12 being in communication with a second discharge line 302 of said compressor 3;
a sixth end 122 of the second four-way valve 12 is communicated with a sixth branch 406, the second usage-side heat exchanger 10 is disposed on the sixth branch 406, and a fourth control valve 71 is disposed on the sixth branch 406;
the seventh end 123 of the second four-way valve 12 is communicated with the suction pipeline 100, and a third control valve 23 is further arranged on the suction pipeline 100 between the joint of the suction pipeline 100 and the second branch 402 and the second four-way valve 12;
the eighth end 124 of the second four-way valve 12 is communicated with a seventh branch 407, the seventh branch 407 is communicated to the fifth branch 405 and is located between the seventh control valve 74 and the second heat source heat exchanger 8, and a sixth control valve 73 is further arranged on the fifth branch 405 and is located between the junction of the seventh branch 407 and the second heat source heat exchanger 8.
According to the control of the second four-way valve and the control valve (preferably, the solenoid valve), the first using side heat exchanger, the first exhaust port and the first heat source heat exchanger can be communicated through the first four-way valve, the second using side heat exchanger, the second exhaust port and the second heat source heat exchanger can be communicated through the second four-way valve, the two four-way valves can be connected with each other, different circulation modes of the system are further realized, double condensation temperature heating can be realized in winter, one heat source can be used for refrigeration or two heat sources can be used for refrigeration simultaneously in summer, the system operation energy efficiency is improved, the system operation is optimal, and the problem that the system cannot achieve optimal operation under different working conditions is solved; different combination modes such as independent operation, simultaneous operation and the like can be realized by controlling the four-way reversing valve and the electromagnetic valve, the two evaporators and the two condensers, and the circulation mode can be flexibly selected according to actual requirements.
In some embodiments, the other end of the first usage-side heat exchanger 1 is communicated with one end of an eighth branch 408, the other end of the second usage-side heat exchanger 10 is communicated with one end of a ninth branch 409, the eighth branch 408 is provided with a first throttling device 41, and the ninth branch 409 is provided with a third throttling device 43;
the other end of the first heat source heat exchanger 6 is communicated with one end of a tenth branch 410, the other end of the eighth branch 408 is communicated with the tenth branch 410, the other end of the ninth branch 409 is communicated with the tenth branch 410, a thirteenth control valve 951 is arranged on the tenth branch 410 and between the joint of the tenth branch and the eighth branch 408 and the first heat source heat exchanger 6, and a twelfth control valve 95 is arranged on the tenth branch 410 and between the joint of the tenth branch and the ninth branch 409 and the joint of the ninth branch 409.
Through the setting of eighth branch road and ninth branch road, can effectively set up first use side heat exchanger and second use side heat exchanger respectively and carry out the condensation heat transfer of two condensing temperatures under the mode of heating to the formation is different at the heating temperature that first use side acquireed and the heating temperature that acquires at the second use side, and the condensing temperature who acquires from first and second heat source heat exchanger under the cooling mode is different, and the heat of release is different, improves the efficiency utilization ratio. The first throttling device and the third throttling device can effectively throttle the refrigerant in the pipeline of the first using side heat exchanger and effectively throttle the refrigerant in the pipeline of the second using side heat exchanger.
In some embodiments, the eighth branch 408 and the ninth branch 409 are further communicated through an eleventh branch 411, and an eighth control valve 91 is disposed on the eleventh branch 411. The short circuit of the second user-side heat exchanger 10 can be controlled by the eleventh branch circuit, so that the use requirements of more working conditions can be met.
In some embodiments, a twelfth branch 412 is further disposed in the position where the ninth branch 409 meets the tenth branch 410, one end of the twelfth branch 412 is communicated to the other end of the second heat source heat exchanger 8, and a fifth control valve 72 is disposed on the twelfth branch 412. The ninth branch can be effectively communicated to the second heat source heat exchanger through the twelfth 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 refrigeration are carried out on the second heat source heat exchanger.
In some embodiments, the flash evaporator 5 is further included, the flash evaporator 5 is connected to the eighth branch 408 at a position between the junction with the tenth branch 410 and the first throttling device 41, a second throttling device 42 is further provided on the eighth branch 408 between the junction with the tenth branch 410 and the flash evaporator 5, the air supplement pipeline 200 of the flash evaporator 5 is communicated to the air supplement port 34 of the compressor 3, and the first control valve 21 is provided on the air supplement pipeline 200. The flash evaporator can be used for supplying air and increasing enthalpy when the first using side heat exchanger is heated, so that the enthalpy value is increased, and the heating efficiency is improved.
In some embodiments, a thirteenth branch 413 is further communicatively disposed between the first branch 401 and the sixth branch 406, and a tenth control valve 93 is further disposed on the thirteenth branch 413. The first branch and the sixth branch can be effectively communicated through the thirteenth branch, and the situation that the first branch and the sixth branch are communicated to the air suction pipeline through one pipeline is suitable for the situation, so that the diversity of different controls under different working conditions is met.
In some embodiments, the first heat source is an air source and the second heat source is a water source. The double heat sources 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 the dual condensing temperature heat pump system according to any one of the preceding claims, wherein: and controlling the double-condensation-temperature heat pump system to operate in at least one mode of a heating mode, a hot water heating mode, a heat recovery mode and a cooling mode.
The system comprises two evaporators, two condensers, a compressor, two four-way valves, an electromagnetic valve, a throttling device and the like. In summer, double condensing temperatures can be provided, the power consumption of the compressor is reduced, the system efficiency is improved, and the heat recovery function can be realized; in winter, according to the provided double condensation temperature, the system can supply heat and hot water, meets different requirements, can realize refrigeration, heating, hot water supply and heat recovery, and improves the utilization rate of equipment. The single-suction double-row compressor is adopted, so that double condensing temperatures can be provided in summer, the power consumption of the compressor is reduced, and the system efficiency is improved; in winter, according to the provided double condensation temperature, the solar energy water heater can supply heat and hot water, and different requirements are met. The double heat sources are adopted in winter, switching can be performed according to different heat source conditions, and the double heat sources are suitable for the condition that the heat source conditions in winter are unstable.
In winter, one heat source can be used for heating or two heat sources can be used for heating simultaneously. The energy is fully utilized according to the characteristics of different heat sources, so that the system is stable, energy-saving and efficient to operate.
Under different operating conditions, the system can realize different combination modes such as independent operation, simultaneous operation and the like by controlling the four-way reversing valve and the electromagnetic valve, the two evaporators and the two condensers, and the circulation mode can be flexibly selected according to actual requirements.
In some embodiments, while in the heating mode, the refrigerant is controlled to exchange heat with a first heat source in the first heat source heat exchanger 6 (to absorb heat from the first heat source for heating the room), and/or the refrigerant is controlled to exchange heat with a second heat source in the second heat source heat exchanger 8 (to absorb heat from the second heat source for heating the room);
in the cooling mode, the refrigerant is controlled to exchange heat with a first heat source in the first heat source heat exchanger 6 (to release heat from the first heat source for cooling the room), and/or the refrigerant is controlled to exchange heat with a second heat source in the second heat source heat exchanger 8 (to release heat from the second heat source for cooling the room).
This is a control form of several preferred operation modes of the heat pump system of the present disclosure, i.e., preferred control actions in the heating mode and the cooling mode.
When the system operates in winter, different operation controls can be carried out according to different heat source temperatures:
a first heating mode:
in some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger 8 is higher than a preset temperature:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
in the first heating mode, the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the ninth control valve 92 is controlled to be opened, the twelfth 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 sixth control valve 73 is controlled to be opened, the seventh control valve 74 is controlled to be opened, the eighth control valve 91 is controlled to be closed, the tenth control valve 93 is controlled to be closed, the eleventh control valve 94 is controlled to be closed, the thirteenth control valve 951 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 opened, and indoor heating is performed only through the second heat source heat.
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 first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the twelfth control valve 95, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, and the seventh control valve 74 are opened, the eighth control valve 91, the tenth control valve 93, the eleventh control valve 94, and the thirteenth control valve 951 are closed, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are opened. 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 and throttled by the second throttling device 42, and then enters the second heat source heat exchanger 8 through the twelfth and fifth control valves 95 and 72, the refrigerant flowing through the second usage-side heat exchanger 10 is throttled by the third throttling device 43 and enters the second heat source heat exchanger 8 through the fifth control valve 72, all the refrigerant absorbs heat in the second heat source heat exchanger 8, the refrigerant absorbing heat passes through the sixth control valve 73, a part of the refrigerant enters the compressor 3 through the second four-way valve 12 to be compressed, a part of the refrigerant enters the compressor 3 through the seventh and the first four-way valve 11 to be compressed, and the compressor has two exhaust ports adapted to different exhaust pressures. A part of the refrigerant is discharged from one of the discharge ports, passes through the first four-way valve 11 and the ninth control valve 92, enters the first usage-side heat exchanger 1, and is subjected to the next cycle, and another part of the refrigerant is discharged from the other discharge port, passes through the second four-way valve 12 and the fourth control valve 71, and is introduced into the second usage-side heat exchanger 10, and is subjected to the next cycle. The refrigerant has different condensation temperatures and different heating temperatures in the first and second usage- side heat exchangers 1 and 10. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.
And a second heating mode:
in some embodiments, in the heating mode, and when the temperature of the second heat source heat exchanger 8 is lower than a preset temperature:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
and in the second heating mode of system starting, the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the ninth control valve 92 is controlled to be opened, the eleventh control valve 94 is controlled to be opened, the thirteenth control valve 951 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 sixth control valve 73 is controlled to be opened, the eighth control valve 91 is controlled to be closed, the tenth control valve 93 is controlled to be closed, the twelfth control valve 95 is controlled to be closed, the seventh control valve 74 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 opened, and indoor heating is carried out through the first heat source heat exchanger 6 and.
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: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the thirteenth control valve 951, the fourth control valve 71, the fifth control valve 72, and the sixth control valve 73 are opened, the eighth control valve 91, the tenth control valve 93, the twelfth control valve 95, and the seventh control valve 74 are closed, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are opened. 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 throttle device 41 and the second throttle device 42, and then enters the first heat source heat exchanger 6 through the thirteenth control valve 951 to absorb heat, and after absorbing heat, the refrigerant enters the compressor 3 through the eleventh control valve 94 and the first four-way valve 11 to be compressed. Another part of the refrigerant releases heat in the second usage-side heat exchanger 10, and after releasing heat, the refrigerant is throttled by the third throttling device 43, then enters the second heat source heat exchanger 8 through the fifth control valve 72 to absorb heat, and after absorbing heat, enters the compressor 3 through the sixth control valve 73 and the second four-way valve 12 to be compressed. After compression, a part of the refrigerant is discharged from one of the discharge ports, passes through the first four-way valve 11 and the ninth control valve 92, enters the first use-side heat exchanger 1 for the next cycle, and another part of the refrigerant is discharged from the other discharge port, passes through the second four-way valve 12 and the fourth control valve 71, and enters the second use-side heat exchanger 10 for the next cycle. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.
A heating mode III:
in some embodiments, in the heating mode, and when the second heat source heat exchanger 8 is not available:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
and a third heating mode of the system is started, wherein the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the ninth control valve 92 is controlled to be opened, the eleventh control valve 94 is controlled to be opened, the twelfth control valve 95 is controlled to be opened, the thirteenth control valve 951 is controlled to be opened, the fourth control valve 71 is controlled to be opened, the seventh control valve 74 is controlled to be opened, the eighth control valve 91 is controlled to be closed, the tenth control valve 93 is controlled to be closed, the fifth control valve 72 is controlled to be closed, the sixth control valve 73 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 opened, and indoor heating is performed.
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 first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951, the fourth control valve 71, and the seventh control valve 74 are opened, the eighth control valve 91, the tenth control valve 93, the fifth control valve 72, and the sixth control valve 73 are closed, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are opened. 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 and second throttling devices 41 and 42, and then enters the first heat source heat exchanger 6 through the thirteenth control valve 951, the refrigerant flowing through the second usage-side heat exchanger 10 is throttled by the third throttling device 43, and then enters the first heat source heat exchanger 6 through the twelfth and thirteenth control valves 95 and 951, all the refrigerant absorbs heat in the first heat source heat exchanger 6, the refrigerant absorbing heat passes through the eleventh control valve 94, a part of the refrigerant passes through the first four-way valve 11 and enters the compressor 3 for compression, and the other part of the refrigerant passes through the seventh control valve 74 and the second four-way valve 12 and enters the compressor 3 for compression. After compression, a part of the refrigerant is discharged from one of the discharge ports, passes through the first four-way valve 11 and the ninth control valve 92, enters the first use-side heat exchanger 1 for the next cycle, and another part of the refrigerant is discharged from the other discharge port, passes through the second four-way valve 12 and the fourth control valve 71, and enters the second use-side heat exchanger 10 for the next cycle. In this cycle, the indoor side has a double condensing temperature and the outdoor side has a single evaporating temperature.
When the first and second usage- side heat exchangers 1 and 10 do not need to be operated simultaneously, the refrigerant can be caused to flow through only one of the usage-side heat exchangers by closing the ninth control valve 92 or the fourth control valve 71. In this case, the first heat source heat exchanger 6 and the second heat source heat exchanger 8 may be operated independently or simultaneously.
A first summer refrigeration mode:
in some embodiments, in the cooling mode, and while the first heat source heat exchanger 6 is releasing heat, the second heat source heat exchanger 8 is also releasing heat for heat recovery:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
and the system starts the first cooling mode, controls to open the first control valve 21, open the second control valve 22, open the third control valve 23, open the ninth control valve 92, open the eleventh control valve 94, open the thirteenth control valve 951, open the fourth control valve 71, open the fifth control valve 72, open the sixth control valve 73, control to close the eighth control valve 91, close the tenth control valve 93, close the twelfth control valve 95 and close the seventh control valve 74, opens the first throttling device 41 and opens the second throttling device 42, opens the third throttling device 43, and cools the room through the first heat source heat exchanger 6 and the second heat source heat exchanger 8.
When the system runs in summer, the operation control is as follows:
heat is released in the first heat source heat exchanger 6 and the second heat source heat exchanger 8, and part of the heat is recovered by the second heat source heat exchanger 8. The system cycle for this condition is as follows: the first control valve 21, the second control valve 22, the third control valve 23, the ninth control valve 92, the eleventh control valve 94, the thirteenth control valve 951, the fourth control valve 71, the fifth control valve 72, and the sixth control valve 73 are opened, the eighth control valve 91, the tenth control valve 93, the twelfth control valve 95, and the seventh control valve 74 are closed, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are opened. A part of the refrigerant absorbs heat in the first usage-side heat exchanger 1, and the refrigerant having absorbed heat enters the compressor 3 through the ninth control valve 92 and the first four-way valve 11 and is compressed. The other part of the refrigerant absorbs heat in the second usage-side heat exchanger 10, and the refrigerant having absorbed heat enters the compressor 3 through the fourth control valve 71 and the second four-way valve 12 and is compressed. A part of the compressed refrigerant is discharged from one exhaust port, enters the first heat source heat exchanger 6 through the first four-way valve 11 and the eleventh control valve 94 to release heat, and enters the second throttling device 42 and the first throttling device 41 through the thirteenth control valve 951 to be throttled, and then enters the first use-side heat exchanger 1 to perform the next cycle. And the other part of the refrigerant is discharged from the other exhaust port, enters the second heat source heat exchanger 8 through the second four-way valve 12 and the sixth control valve 73 to release heat, the second heat source heat exchanger 8 recovers the part of the heat, and the refrigerant after heat release enters the third throttling device 43 through the fifth control valve 72 to be throttled and then enters the second use side heat exchanger 10 to perform the next cycle. In this cycle, the indoor side has a single evaporation temperature and the outdoor side has a dual condensation temperature.
And a second refrigeration mode:
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:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
and the system starts a second cooling mode, the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the ninth control valve 92 is controlled to be opened, the eleventh control valve 94 is controlled to be opened, the thirteenth control valve 951 is controlled to be opened, the twelfth control valve 95 is controlled to be opened, the fourth control valve 71 is controlled to be opened, the seventh control valve 74 is controlled to be opened, the eighth control valve 91 is controlled to be closed, the tenth control valve 93 is controlled to be closed, the fifth control valve 72 is controlled to be closed, the sixth control valve 73 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 opened, and the indoor space is cooled only through.
When heat is released only in the first heat source heat exchanger 6 and heat recovery is not performed, the two paths of refrigerants coming out of the two exhaust ports of the compressor 3 flow into the first heat source heat exchanger 6 to release heat and do not flow into the second heat source heat exchanger 8. The detailed process is not repeated herein.
And a third refrigeration mode:
in some embodiments, in cooling mode, and only when the second heat source heat exchanger 8 is releasing heat for heat recovery:
and when the first control valve 21, the second control valve 22, the third control valve 23, the fourth control valve 71, the fifth control valve 72, the sixth control valve 73, the seventh control valve 74, the eighth control valve 91, the ninth control valve 92, the tenth control valve 93, the eleventh control valve 94, the twelfth control valve 95, the thirteenth control valve 951 are included together, and the first throttling device 41, the second throttling device 42, and the third throttling device 43 are included:
and a third cooling mode of the system is started, wherein the first control valve 21 is controlled to be opened, the second control valve 22 is controlled to be opened, the third control valve 23 is controlled to be opened, the ninth control valve 92 is controlled to be opened, the twelfth 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 sixth control valve 73 is controlled to be opened, the seventh control valve 74 is controlled to be opened, the eighth control valve 91 is controlled to be closed, the tenth control valve 93 is controlled to be closed, the thirteenth control valve 951 is controlled to be closed, the eleventh control valve 94 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 opened, and the indoor space is.
When heat is released in the second heat source heat exchanger 8 and the second heat source heat exchanger 8 recovers all heat, two paths of refrigerants coming out of two exhaust ports of the compressor 3 flow into the second heat source heat exchanger 8 to release heat and do not flow into the first heat source heat exchanger 6. The detailed process is not repeated herein.
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 second and third throttling devices 42 and 43. 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 (9)
1. A dual condensing temperature heat pump system characterized in that:
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), refrigerant exchanges heat with a second heat source in the second heat source heat exchanger (8), the compressor (3) comprises a first exhaust port (31), a second exhaust port (32) and a suction port (33), the first exhaust port (31) is communicated with a first exhaust pipeline (301), the second exhaust port (32) is communicated with a second exhaust pipeline (302), the suction opening (33) communicates with a suction line (100), the first use-side heat exchanger (1) is communicable to the first exhaust line (301), and the second use-side heat exchanger (10) is communicable to the second exhaust line (302); or the first and second use-side heat exchangers (1, 10) can be respectively connected to the suction line (100) of the compressor.
2. The dual condensing temperature heat pump system of claim 1, wherein:
the compressor further comprises a first four-way valve (11), wherein a first end (111) of the first four-way valve (11) is communicated with a first exhaust pipeline (301) of the compressor (3);
a second end (112) of the first four-way valve (11) is communicated with a first branch (401), the first using side heat exchanger (1) is arranged on the first branch (401), and a ninth control valve (92) is arranged on the first branch (401);
a third end (113) of the first four-way valve (11) is communicated to the suction pipeline (100) through a second branch (402), and a second control valve (22) is arranged on the second branch (402);
the fourth end (114) of the first four-way valve (11) is communicated with a third branch (403), one end of the first heat source heat exchanger (6) is communicated to the third branch (403) through a fourth branch (404), an eleventh control valve (94) is arranged on the fourth branch (404), one end of the second heat source heat exchanger (8) is communicated to the third branch (403) through a fifth branch (405), and a seventh control valve (74) is arranged on the fifth branch (405).
3. The dual condensing temperature heat pump system of claim 2, wherein:
the compressor further comprises a second four-way valve (12), and a fifth end (121) of the second four-way valve (12) is communicated with a second exhaust pipeline (302) of the compressor (3);
a sixth end (122) of the second four-way valve (12) is communicated with a sixth branch (406), the second use-side heat exchanger (10) is arranged on the sixth branch (406), and a fourth control valve (71) is arranged on the sixth branch (406);
a seventh end (123) of the second four-way valve (12) is communicated with the air suction pipeline (100), and a third control valve (23) is further arranged between the position, connected with the second branch (402), of the air suction pipeline (100) and the second four-way valve (12);
an eighth end (124) of the second four-way valve (12) is communicated with a seventh branch (407), the seventh branch (407) is communicated to the fifth branch (405) and is positioned between the seventh control valve (74) and the second heat source heat exchanger (8), and a sixth control valve (73) is further arranged on the fifth branch (405) and is positioned between the joint of the seventh branch (407) and the second heat source heat exchanger (8).
4. The dual condensing temperature heat pump system of claim 3, wherein:
the other end of the first using side heat exchanger (1) is communicated with one end of an eighth branch (408), the other end of the second using side heat exchanger (10) is communicated with one end of a ninth branch (409), a first throttling device (41) is arranged on the eighth branch (408), and a third throttling device (43) is arranged on the ninth branch (409);
the other end of the first heat source heat exchanger (6) is communicated with one end of a tenth branch (410), the other end of the eighth branch (408) is communicated to the tenth branch (410), the other end of the ninth branch (409) is communicated to the tenth branch (410), a thirteenth control valve (951) is arranged on the tenth branch (410) and between the joint of the tenth branch and the eighth branch (408) and the first heat source heat exchanger (6), and a twelfth control valve (95) is arranged on the tenth branch (410) and between the joint of the tenth branch and the ninth branch (409) and the joint of the ninth branch (409).
5. The dual condensing temperature heat pump system of claim 4, wherein:
the eighth branch (408) and the ninth branch (409) are communicated through an eleventh branch (411), and an eighth control valve (91) is arranged on the eleventh branch (411).
6. The dual condensing temperature heat pump system of claim 4, wherein:
a twelfth branch (412) is further arranged at the position where the ninth branch (409) and the tenth branch (410) are connected, one end of the twelfth branch (412) is communicated to the other end of the second heat source heat exchanger (8), and a fifth control valve (72) is arranged on the twelfth branch (412).
7. The dual condensing temperature heat pump system of claim 4, wherein:
the compressor further comprises a flash evaporator (5), the flash evaporator (5) is connected to the eighth branch (408) and located between the joint of the eighth branch (408) and the tenth branch (410) and the first throttling device (41), a second throttling device (42) is further arranged between the joint of the eighth branch (408) and the tenth branch (410) and the flash evaporator (5), an air supplementing pipeline (200) of the flash evaporator (5) is communicated to an air supplementing port (34) of the compressor (3), and a first control valve (21) is arranged on the air supplementing pipeline (200).
8. The dual condensing temperature heat pump system according to any one of claims 3-7, wherein:
a thirteenth branch (413) is further arranged between the first branch (401) and the sixth branch (406) in a communicated manner, and a tenth control valve (93) is further arranged on the thirteenth branch (413).
9. The dual condensing 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.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112128852A (en) * | 2020-09-14 | 2020-12-25 | 珠海格力电器股份有限公司 | Double-condensation temperature heat pump system and control method |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112128852A (en) * | 2020-09-14 | 2020-12-25 | 珠海格力电器股份有限公司 | Double-condensation temperature heat pump system and control method |
| CN112128852B (en) * | 2020-09-14 | 2024-04-12 | 珠海格力电器股份有限公司 | Double-condensation-temperature heat pump system and control method |
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