CN110749114A - Novel high-efficient multi-mode overlapping high temperature heat pump set - Google Patents
Novel high-efficient multi-mode overlapping high temperature heat pump set Download PDFInfo
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- CN110749114A CN110749114A CN201911206056.1A CN201911206056A CN110749114A CN 110749114 A CN110749114 A CN 110749114A CN 201911206056 A CN201911206056 A CN 201911206056A CN 110749114 A CN110749114 A CN 110749114A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2347/00—Details for preventing or removing deposits or corrosion
- F25B2347/02—Details of defrosting cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
Abstract
The invention discloses a novel high-efficiency multi-mode cascade high-temperature heat pump unit, which has three heating operation modes according to the environment temperature and the return water temperature, and only operates a low-temperature system when the return water temperature is lower than 45 ℃. And secondly, when the return water temperature is greater than 45 ℃ and the ambient temperature is less than T1, the low-temperature stage and the high-temperature stage operate together. And thirdly, when the return water temperature is higher than 45 ℃ and the environment temperature is more than or equal to T1, only operating the high-temperature system. Except the heating function, when a customer needs cold water, the low-temperature system can be switched to a refrigeration mode, a single machine can prepare the cold water, and at the moment, the high-temperature system can recover the condensation heat of the low-temperature system to prepare the hot water. In addition, the low-temperature-level system and the high-temperature-level system can be switched to defrost simultaneously, so that the unit can defrost quickly and stably, and the unit can be guaranteed to operate stably under severe working conditions in winter.
Description
Technical Field
The invention relates to a heat pump unit, in particular to a novel high-efficiency multi-mode overlapping high-temperature heat pump unit.
Background
At present, with the development of the overlapping heat pump technology, the overlapping high-temperature heat pump unit is more and more widely applied, for example, in the fields of electroplating, slaughtering, oil field crude oil heating and the like. However, the existing overlapping unit has the problems of single function, high defrosting difficulty, low heating efficiency and the like.
Under the working conditions of low return water temperature and low environment temperature, the cascade heating is adopted, the heating capacity of the high-temperature system is far larger than the design value, the low-temperature system is insufficient in heat supply, and the energy efficiency of the whole machine is low. In summer, the system adopts cascade heating, so that when hot water is prepared, the low-temperature-level operation frequency is low, the energy efficiency of the whole machine is low, oil return of the compressor is not facilitated, and the operation life of the compressor is shortened.
Disclosure of Invention
According to the technical problems provided by the above, a novel high-efficiency multi-mode overlapping high-temperature heat pump unit is provided.
The technical means adopted by the invention are as follows:
a novel high-efficiency multi-mode cascade high-temperature heat pump unit comprises a low-temperature system and a high-temperature system;
the high-temperature stage system comprises a high-temperature compressor, an air suction port of the high-temperature compressor is connected with an air outlet of a first gas-liquid separator, the air outlet of the high-temperature compressor is respectively connected with an electromagnetic valve A, an electromagnetic valve B, the first gas-liquid separator and a finned tube heat exchanger through a first four-way reversing valve, the electromagnetic valve A is connected with a second economizer, and the electromagnetic valve B is connected with a first water-cooling heat exchanger; the first water-cooling heat exchanger is connected with the first liquid storage device, and the first liquid storage device is connected with the finned tube type heat exchanger;
the low-temperature stage system comprises a variable-frequency compressor, an air suction port of the variable-frequency compressor is connected with an air outlet of the second gas-liquid separator, the air outlet of the variable-frequency compressor is respectively connected with an electromagnetic valve C, an electromagnetic valve D, the second gas-liquid separator and the finned tube heat exchanger through a second four-way reversing valve, the electromagnetic valve C is connected with a second economizer, and the electromagnetic valve D is connected with a second water-cooling heat exchanger; the air supplement port of the variable frequency compressor is connected with the first economizer; the second water-cooled heat exchanger is connected with the second liquid storage device, the second liquid storage device is connected with the first economizer, and the finned tube heat exchanger is connected with the first economizer;
the low-temperature system and the high-temperature system share the finned tube heat exchanger, pipelines connected with the finned tube heat exchanger and the low-temperature system and the high-temperature system are arranged in a crossed mode, and a fan is arranged at the position of the finned tube heat exchanger.
Further, the first reservoir is connected with the finned tube heat exchanger through a first throttling valve;
the finned tube heat exchanger is connected with the first economizer through a second throttling valve group;
the second reservoir is connected with the first economizer through an enthalpy-increasing solenoid valve and a third throttle valve group.
Furthermore, the air suction port of the high-temperature compressor is connected with the first gas-liquid separator through a liquid spraying capillary tube and a liquid spraying electromagnetic valve.
Further, the water-cooled heat exchanger is a double-pipe heat exchanger or a plate heat exchanger or a high-efficiency tank heat exchanger.
Further, the first economizer and the second economizer are plate heat exchangers.
Furthermore, the first throttle valve group, the second throttle valve group and the third throttle valve group are all composed of an electronic expansion valve, a capillary tube and a filter.
The invention discloses a heating mode of a novel high-efficiency multi-mode cascade high-temperature heat pump unit, which has three modes, namely:
firstly, when the return water temperature is less than 45 ℃, only the low-temperature system is operated.
At this time, the solenoid valve D is closed, the solenoid valve C is opened, the enthalpy increasing solenoid valve is closed, the solenoid valve a is closed, and the solenoid valve B is closed. And the low-temperature-level refrigerant is discharged to the second four-way reversing valve through an exhaust port of the variable-frequency compressor, then sequentially passes through the electromagnetic valve C and the second water-cooling heat exchanger, after being heated by cold water, the low-temperature-level refrigerant sequentially passes through the second liquid storage device and the first economizer, is throttled and cooled by the second throttle valve group, then enters the finned tube heat exchanger to exchange heat with air, and after absorbing heat, the low-temperature-level refrigerant sequentially passes through the second four-way reversing valve and the second gas-liquid separator and then returns to the variable-frequency compressor, so that the single-.
When the system needs air supplement, the low-temperature system starts the air supplement and enthalpy increase function. The refrigerant cycle is different from the refrigerant cycle, except for the refrigerant cycle, a part of low-temperature-stage refrigerant from the second liquid storage device is bypassed, is throttled by the enthalpy-increasing solenoid valve and the third throttle valve group in sequence, enters the first economizer to exchange heat with main path refrigerant from the second liquid storage device, absorbs heat and returns to an air supplement port of the variable frequency compressor, and the main path refrigerant cycle is the same as the cycle.
And secondly, when the return water temperature is greater than 45 ℃ and the ambient temperature is less than T1(T1 is a preset value), the low-temperature-level system and the high-temperature-level system operate together.
At this time, the solenoid valve D is opened, the solenoid valve C is closed, the enthalpy increasing solenoid valve is closed, the solenoid valve a is opened, and the solenoid valve B is closed. And after the low-temperature-level refrigerant absorbs heat, the low-temperature-level refrigerant returns to the variable-frequency compressor after passing through the second four-way reversing valve and the second gas-liquid separator, and the cascade heating cycle is completed.
When the system needs air supplement, the low-temperature system starts the air supplement and enthalpy increase function. When the low-temperature refrigerant circulation is different from the low-temperature refrigerant circulation, besides the low-temperature refrigerant circulation, a part of low-temperature-stage refrigerant from the second liquid storage device bypasses, enters the first economizer after being throttled by the enthalpy-increasing electromagnetic valve and the third throttle group in sequence, exchanges heat with main path refrigerant from the second liquid storage device, absorbs heat and returns to an air supplement port of the variable frequency compressor, and the main path refrigerant circulation is the same as the circulation.
The high-temperature refrigerant circulates as follows: the high-temperature-stage refrigerant is discharged to the first four-way reversing valve through a high-temperature compressor exhaust port, then is heated by the first water-cooling heat exchanger, then sequentially passes through the first liquid storage device and the first throttle valve group for throttling and cooling, then is subjected to heat exchange with the low-temperature-stage refrigerant through the second economizer, absorbs heat, sequentially passes through the electromagnetic valve A, the first four-way reversing valve and the first gas-liquid separator, and then returns to the high-temperature compressor, so that the circulation of the high-temperature-stage refrigerant is completed.
When the exhaust temperature of the high-temperature compressor is too high, in addition to the circulation, the liquid spraying electromagnetic valve is opened, and a part of high-temperature refrigerant from the first liquid storage device bypasses and sequentially passes through the liquid spraying electromagnetic valve and the liquid spraying capillary tube for throttling and cooling, enters the air suction pipe of the high-temperature compressor to be mixed with main path refrigerant, and then returns to the compressor. The main path refrigerant cycle is the same as the above cycle.
And thirdly, when the return water temperature is higher than 45 ℃ and the environment temperature is more than or equal to T1, only operating the high-temperature system.
At this time, the solenoid valve D is closed, the solenoid valve C is closed, the enthalpy-increasing solenoid valve is closed, the solenoid valve a is closed, and the solenoid valve B is opened. The high-temperature-stage refrigerant is discharged to the first four-way reversing valve through a high-temperature compressor exhaust port, then is heated by the first water-cooling heat exchanger, then sequentially passes through the first liquid storage device and the first throttle valve group for throttling and cooling, then is subjected to heat exchange with air by the fin tube type heat exchanger, absorbs heat, sequentially passes through the electromagnetic valve A, the first four-way reversing valve and the first gas-liquid separator, and then returns to the high-temperature compressor, so that the circulation of the high-temperature-stage refrigerant is completed.
When the exhaust temperature of the high-temperature compressor is too high, in addition to the circulation, the liquid spraying electromagnetic valve is opened, and a part of high-temperature refrigerant from the first liquid storage device bypasses and sequentially passes through the liquid spraying electromagnetic valve and the liquid spraying capillary tube for throttling and cooling, enters the air suction pipe of the high-temperature compressor to be mixed with main path refrigerant, and then returns to the compressor. The main path refrigerant cycle is the same as the above cycle.
Through switching between single-stage operation and double-stage operation under different working conditions, the unit can continuously, efficiently and stably prepare high-temperature hot water at 85 ℃ in an ultra-wide ring temperature range of-30 ℃ to 40 ℃.
Except the heating function, when a customer needs cold water, the low-temperature system can be switched to a refrigeration mode, a single machine can prepare the cold water, and at the moment, the high-temperature system can recover the condensation heat of the low-temperature system to prepare the hot water.
At this time, the solenoid valve D is closed, the solenoid valve C is opened, the enthalpy increasing solenoid valve is closed, the solenoid valve a is closed, and the solenoid valve B is opened. And the low-temperature-level refrigerant is discharged to the second four-way reversing valve through an exhaust port of the variable-frequency compressor, then sequentially passes through the finned tube heat exchanger, after being throttled and cooled by the second throttling valve group, sequentially passes through the first economizer, the second liquid reservoir and the electromagnetic valve C, enters the second water-cooling heat exchanger to exchange heat with water, absorbs heat in the water, sequentially passes through the second four-way reversing valve, and the second gas-liquid separator returns to the variable-frequency compressor to complete the refrigeration cycle.
The high-temperature-level system is operated to heat, high-temperature-level refrigerant is discharged to the first four-way reversing valve through the exhaust port of the high-temperature compressor, hot water is heated through the first water-cooling heat exchanger, and then the hot water sequentially passes through the first liquid storage device and the first throttle valve group for throttling and cooling, then the hot water passes through the finned tube heat exchanger to absorb heat in hot air after exchanging heat with the low-temperature-level refrigerant, and after absorbing heat, the hot water sequentially passes through the electromagnetic valve B, the first four-way reversing valve and the first gas-liquid separator and then returns to the high-temperature compressor.
In addition, the low-temperature-level system and the high-temperature-level system can be switched to defrost simultaneously, so that the unit can defrost quickly and stably, and the unit can be guaranteed to operate stably under severe working conditions in winter.
Defrosting mode: when the unit needs defrosting, at the moment, the electromagnetic valve D is closed, the electromagnetic valve C is opened, the enthalpy-increasing electromagnetic valve is closed, the electromagnetic valve A is closed, and the electromagnetic valve B is opened. And the low-temperature refrigerant is discharged to the second four-way reversing valve through an exhaust port of the variable frequency compressor, and then passes through the fin tube type heat exchanger to heat a frost layer for defrosting. And then, after throttling and cooling through a second throttling valve group, the mixed gas enters a second water-cooling heat exchanger to exchange heat with water after passing through a first economizer, a second liquid storage device and an electromagnetic valve C in sequence, and then passes through a second four-way reversing valve in sequence, and a second gas-liquid separator returns to the variable frequency compressor to complete the low-temperature defrosting cycle.
And (3) high-temperature defrosting, wherein the refrigerant is discharged to the first four-way reversing valve through an exhaust port of the high-temperature compressor, then reaches the fin tube type heat exchanger through the electromagnetic valve B, heats a frost layer and defrosts. And then the high-temperature defrosting cycle is finished by throttling and cooling through the first throttling valve group, entering the first water-cooling heat exchanger through the first liquid storage device to exchange heat with water, returning the high-temperature compressor through the first four-way reversing valve and the first gas-liquid separator, and finally finishing the high-temperature defrosting cycle.
The invention has the following advantages:
1. has three heating operation modes. Firstly, when the return water temperature is less than 45 ℃, only the low-temperature system is operated for heating. And secondly, when the return water temperature is greater than 45 ℃ and the environment temperature is less than T1, the low-temperature stage and the high-temperature stage operate together to produce heat. And thirdly, when the return water temperature is higher than 45 ℃ and the environment temperature is more than or equal to T1, only operating the high-temperature system for heating. Through switching between single-stage operation and double-stage operation under different working conditions, the unit can continuously, efficiently and stably prepare high-temperature hot water at 85 ℃ in an ultra-wide ring temperature range of-30 ℃ to 40 ℃.
2. Besides the conventional heating function, the system has the functions of refrigeration and heat recovery, and when a customer needs to prepare cold water, the low-temperature system operates independently and is switched into a refrigeration mode to prepare the cold water. At the moment, the high-temperature system can recover the condensation heat of the low-temperature system to prepare hot water, and the energy efficiency of the whole machine is improved.
3. The defrosting is rapid, and the low-temperature-level system and the high-temperature-level system are switched to defrost at the same time, so that the unit can utilize the double-level heating quantity to defrost quickly and stably, and the stable operation of the unit under the severe working condition in winter is ensured.
Based on the reasons, the invention can be widely popularized in the fields of heat pump units and the like.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a novel high-efficiency multi-mode cascade high-temperature heat pump unit according to an embodiment of the present invention.
FIG. 2 is a flow chart of the media when the heating mode is only low temperature stage system on in accordance with an embodiment of the present invention.
Fig. 3 is a medium flow diagram illustrating the simultaneous operation of a heating mode low temperature stage system and a heating mode high temperature stage system in accordance with an embodiment of the present invention.
FIG. 4 is a medium flow diagram illustrating a heating mode with only the high temperature stage system on in accordance with an embodiment of the present invention.
FIG. 5 is a flow diagram of the refrigerant and heat recovery mode media in an embodiment of the present invention.
FIG. 6 is a flow chart of the defrosting mode medium in the embodiment of the invention.
In the figure: 1. a first water-cooled heat exchanger; 2. a first four-way reversing valve; 3. a high temperature compressor; 4. a first gas-liquid separator; 5. spraying a liquid capillary; 6. a liquid spraying electromagnetic valve; 7. a first reservoir; 8. a first throttle valve set; 9. an electromagnetic valve A; 10, an electromagnetic valve B; 11. a finned tube heat exchanger; 12. a fan; 13. a second throttle valve group; 14. a first economic device; 15. an enthalpy-increasing electromagnetic valve; 16. a third throttle valve group; 17. a second reservoir; 18. a second gas-liquid separator; 19. a variable frequency compressor; 20. a second four-way reversing valve; 21. a solenoid valve C; 22. a solenoid valve D; 23. a second water-cooled heat exchanger; 24. and a second economizer.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1, a novel high-efficiency multi-mode cascade high-temperature heat pump unit comprises a low-temperature-stage system and a high-temperature-stage system;
the high-temperature stage system comprises a high-temperature compressor 3, an air suction port of the high-temperature compressor 3 is connected with an air outlet of a first gas-liquid separator 4, the air outlet of the high-temperature compressor 3 is respectively connected with an electromagnetic valve A9, an electromagnetic valve B10, the first gas-liquid separator 4 and a finned tube heat exchanger 11 through a first four-way reversing valve 2, the electromagnetic valve A9 is connected with a second economizer 24, and the electromagnetic valve B10 is connected with a first water-cooling heat exchanger 1; the first water-cooled heat exchanger 1 is connected with the first liquid storage device 7, and the first liquid storage device 7 is connected with the finned tube heat exchanger 11;
the low-temperature stage system comprises a variable-frequency compressor 19, an air suction port of the variable-frequency compressor 19 is connected with an air outlet of a second gas-liquid separator 18, the air outlet of the variable-frequency compressor 19 is respectively connected with an electromagnetic valve C21, an electromagnetic valve D22, the second gas-liquid separator 18 and the finned tube heat exchanger 11 through a second four-way reversing valve 20, the electromagnetic valve C21 is connected with a second economizer 24, and the electromagnetic valve D22 is connected with a second water-cooling heat exchanger 23; the air supplement port of the variable frequency compressor 19 is connected with the first economizer 14; the second water-cooled heat exchanger 23 is connected with the second reservoir 17, the second reservoir 17 is connected with the first economizer 14, and the finned tube heat exchanger 11 is connected with the first economizer 14;
the low-temperature system and the high-temperature system share the finned tube heat exchanger 11, pipelines connected with the finned tube heat exchanger 11 are arranged in a crossed manner, and a fan 12 is arranged at the position of the finned tube heat exchanger 11.
Further, the first reservoir 7 is connected with the finned tube heat exchanger 11 through a first throttle valve;
the finned tube heat exchanger 11 is connected with the first economizer 14 through a second throttle valve group 13;
the second accumulator 17 is connected to the first economizer 14 through an enthalpy-increasing solenoid valve 15 and a third throttle valve group 16.
Furthermore, the air suction port of the high-temperature compressor 3 is connected with the first gas-liquid separator 4 through a liquid spraying capillary tube 5 and a liquid spraying electromagnetic valve 6.
Further, the water-cooled heat exchanger is a double-pipe heat exchanger or a plate heat exchanger or a high-efficiency tank heat exchanger.
Further, the first economizer 14 and the second economizer 24 are plate heat exchangers.
Further, the first throttle valve set 8, the second throttle valve set 13, and the third throttle valve set 16 are all composed of an electronic expansion valve, a capillary tube, and a filter.
The invention discloses a heating mode of a novel high-efficiency multi-mode cascade high-temperature heat pump unit, which has three modes, namely:
first, when the return water temperature is <45 ℃, only the low-temperature stage system is operated (as shown in fig. 2).
At this time, solenoid D22 is closed, solenoid C21 is open, enthalpy-increasing solenoid 15 is closed, solenoid A9 is closed, and solenoid B10 is closed. The low-temperature-level refrigerant is discharged to the second four-way reversing valve 20 through an exhaust port of the variable-frequency compressor 19, then sequentially passes through the electromagnetic valve C21 and the second water-cooling heat exchanger 23, after the cold water is heated, the low-temperature-level refrigerant sequentially passes through the second liquid storage device 17 and the first economizer 14, is throttled and cooled through the second throttling valve group 13, enters the finned tube heat exchanger 11 to exchange heat with air, and after absorbing heat, the low-temperature-level refrigerant sequentially passes through the second four-way reversing valve 20 and the second gas-liquid separator 18 and then returns to the variable-frequency compressor 19, so that the single-stage heating cycle.
When the system needs air supplement, the low-temperature system starts the air supplement and enthalpy increase function. Different from the refrigerant cycle, in addition to the refrigerant cycle, a part of the low-temperature-stage refrigerant from the second liquid reservoir 17 is bypassed, is throttled by the enthalpy-increasing solenoid valve 15 and the third throttle valve group 16 in sequence, enters the first economizer 14 to exchange heat with the main path refrigerant from the second liquid reservoir 17, absorbs heat, and returns to the air supplement port of the inverter compressor 19, and the main path refrigerant cycle is the same as the cycle.
And secondly, when the return water temperature is greater than 45 ℃ and the ambient temperature is less than T1(T1 is a preset value), the low-temperature-level system and the high-temperature-level system operate together (as shown in figure 3).
At this time, solenoid D22 is open, solenoid C21 is closed, enthalpy-increasing solenoid 15 is closed, solenoid A9 is open, and solenoid B10 is closed. The low-temperature-stage refrigerant is discharged to the second four-way reversing valve 20 through an exhaust port of the variable-frequency compressor 19, then sequentially passes through the electromagnetic valve D22 and the second economizer 24, after the high-temperature-stage refrigerant is heated, the low-temperature-stage refrigerant sequentially passes through the second liquid reservoir 17 and the first economizer 14, is throttled and cooled through the second throttling valve group 13, enters the finned tube heat exchanger 11 to exchange heat with air, and after the low-temperature-stage refrigerant absorbs heat, sequentially passes through the second four-way reversing valve 20 and the second gas-liquid separator 18 and then returns to the variable-frequency compressor 19, so that the cascade heating cycle is completed.
When the system needs air supplement, the low-temperature system starts the air supplement and enthalpy increase function. When the low-temperature refrigerant cycle is different from the low-temperature refrigerant cycle, in addition to the low-temperature refrigerant cycle, a part of the low-temperature-stage refrigerant from the second liquid storage device 17 bypasses, sequentially passes through the enthalpy-increasing solenoid valve 15 and the third throttling valve group 16, is throttled, enters the first economizer 14 to exchange heat with the main path refrigerant from the second liquid storage device 17, absorbs heat, and returns to the air supplement port of the inverter compressor 19, and the main path refrigerant cycle is the same as the cycle.
The high-temperature refrigerant circulates as follows: the high-temperature-stage refrigerant is discharged to the first four-way reversing valve 2 through an exhaust port of the high-temperature compressor 33, then the hot water is heated through the first water-cooling heat exchanger 1, then the hot water is throttled and cooled through the first liquid storage device 7 and the first throttling valve group 8 in sequence, then the hot water exchanges heat with the low-temperature-stage refrigerant through the second economizer 24, the hot water absorbs heat and returns to the high-temperature compressor 33 after passing through the electromagnetic valve A9, the first four-way reversing valve 2 and the first gas-liquid separator 4 in sequence, and circulation of the high-temperature.
When the exhaust temperature of the high-temperature compressor 33 is too high, in addition to the circulation, the liquid injection solenoid valve 6 is opened, and a part of the high-temperature refrigerant from the first liquid reservoir 7 bypasses and sequentially passes through the liquid injection solenoid valve 6 and the liquid injection capillary tube 5 for throttling and cooling, enters the air suction pipe of the high-temperature compressor 33, is mixed with the main path refrigerant, and then returns to the compressor. The main path refrigerant cycle is the same as the above cycle.
And thirdly, when the return water temperature is higher than 45 ℃ and the environment temperature is higher than or equal to T1, only operating the high-temperature-level system (as shown in figure 4).
At this time, solenoid D22 is closed, solenoid C21 is closed, enthalpy-increasing solenoid 15 is closed, solenoid A9 is closed, and solenoid B10 is open. The high-temperature-stage refrigerant is discharged to the first four-way reversing valve 2 through an exhaust port of the high-temperature compressor 33, then is heated by the first water-cooling heat exchanger 1, then sequentially passes through the first liquid reservoir 7 and the first throttling valve group 8 for throttling and cooling, then is subjected to heat exchange with air through the fin tube type heat exchanger 11, absorbs heat, sequentially passes through the electromagnetic valve A9, the first four-way reversing valve 2 and the first gas-liquid separator 4, and then returns to the high-temperature compressor 33, so that the circulation of the high-temperature-stage refrigerant is completed.
When the exhaust temperature of the high-temperature compressor 33 is too high, in addition to the circulation, the liquid injection solenoid valve 6 is opened, and a part of the high-temperature refrigerant from the first liquid reservoir 7 bypasses and sequentially passes through the liquid injection solenoid valve 6 and the liquid injection capillary tube 5 for throttling and cooling, enters the air suction pipe of the high-temperature compressor 33, is mixed with the main path refrigerant, and then returns to the compressor. The main path refrigerant cycle is the same as the above cycle.
Through switching between single-stage operation and double-stage operation under different working conditions, the unit can continuously, efficiently and stably prepare high-temperature hot water at 85 ℃ in an ultra-wide ring temperature range of-30 ℃ to 40 ℃.
Besides the heating function, when the customer needs cold water, the low-temperature system can be switched to the cooling mode, and the single machine can produce cold water, and at the moment, the high-temperature system can recover the condensation heat of the low-temperature system to produce hot water (as shown in fig. 5).
At this time, solenoid D22 is closed, solenoid C21 is open, enthalpy-increasing solenoid 15 is closed, solenoid A9 is closed, and solenoid B10 is open. The low-temperature-stage refrigerant is discharged to the second four-way reversing valve 20 through an exhaust port of the variable frequency compressor 19, then sequentially passes through the finned tube heat exchanger, after being throttled and cooled by the second throttle valve group 13, sequentially passes through the first economizer 14, the second liquid reservoir 17 and the electromagnetic valve C21, enters the second water-cooling heat exchanger 23 to exchange heat with water, absorbs heat in the water, sequentially passes through the second four-way reversing valve 20, and the second gas-liquid separator 18 returns to the variable frequency compressor 19, so that the refrigeration cycle is completed.
The high-temperature-level system operates to heat, high-temperature-level refrigerant is discharged to the first four-way reversing valve 2 through the exhaust port of the high-temperature compressor 33, hot water is heated through the first water-cooling heat exchanger 1, the hot water sequentially passes through the first liquid storage device 7 and the first throttling valve group 8, is throttled and cooled, then passes through the finned tube heat exchanger 11, absorbs heat in hot air after exchanging heat with the low-temperature-level refrigerant, and returns to the high-temperature compressor 33 after absorbing heat sequentially passes through the electromagnetic valve B10, the first four-way reversing valve 2 and the first gas-liquid separator 4, so that circulation of the high-temperature-level.
In addition, the low-temperature-level system and the high-temperature-level system can be switched to defrost simultaneously, so that the unit can defrost quickly and stably, and the unit can be guaranteed to operate stably under severe working conditions in winter (as shown in fig. 6).
Defrosting mode: when the unit needs defrosting, at this time, the solenoid valve D22 is closed, the solenoid valve C21 is opened, the enthalpy-increasing solenoid valve 15 is closed, the solenoid valve A9 is closed, and the solenoid valve B10 is opened. And the low-temperature-stage refrigerant is discharged to the second four-way reversing valve 20 through an exhaust port of the variable frequency compressor 19, and then passes through the fin tube type heat exchanger to heat a frost layer for defrosting. And then the temperature is reduced by throttling through a second throttling valve group 13, the obtained product sequentially passes through the first economizer 14, the second liquid storage 17 and the electromagnetic valve C21, enters a second water-cooling heat exchanger 23 to exchange heat with water, sequentially passes through a second four-way reversing valve 20, and a second gas-liquid separator 18 returns to the variable frequency compressor 19, so that the low-temperature defrosting cycle is completed.
And (3) high-temperature defrosting, namely, the refrigerant is discharged to the first four-way reversing valve 2 through an exhaust port of the high-temperature compressor 33, then reaches the fin tube type heat exchanger through an electromagnetic valve B10, and is heated to defrost the frost layer. And then the water enters the first water-cooling heat exchanger 1 through the first liquid storage device 7 after throttling and cooling through the first throttling valve group 8 to exchange heat with water, and then returns to the high-temperature compressor 33 after passing through the first four-way reversing valve 2 and the first gas-liquid separator 4, so that the high-temperature stage defrosting cycle is completed.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.
Claims (6)
1. A novel high-efficiency multi-mode cascade high-temperature heat pump unit is characterized by comprising a low-temperature system and a high-temperature system;
the high-temperature stage system comprises a high-temperature compressor, an air suction port of the high-temperature compressor is connected with an air outlet of a first gas-liquid separator, the air outlet of the high-temperature compressor is respectively connected with an electromagnetic valve A, an electromagnetic valve B, the first gas-liquid separator and a finned tube heat exchanger through a first four-way reversing valve, the electromagnetic valve A is connected with a second economizer, and the electromagnetic valve B is connected with a first water-cooling heat exchanger; the first water-cooling heat exchanger is connected with the first liquid storage device, and the first liquid storage device is connected with the finned tube type heat exchanger;
the low-temperature stage system comprises a variable-frequency compressor, an air suction port of the variable-frequency compressor is connected with an air outlet of the second gas-liquid separator, the air outlet of the variable-frequency compressor is respectively connected with an electromagnetic valve C, an electromagnetic valve D, the second gas-liquid separator and the finned tube heat exchanger through a second four-way reversing valve, the electromagnetic valve C is connected with a second economizer, and the electromagnetic valve D is connected with a second water-cooling heat exchanger; the air supplement port of the variable frequency compressor is connected with the first economizer; the second water-cooled heat exchanger is connected with the second liquid storage device, the second liquid storage device is connected with the first economizer, and the finned tube heat exchanger is connected with the first economizer;
the low-temperature system and the high-temperature system share the finned tube heat exchanger, pipelines connected with the finned tube heat exchanger and the low-temperature system and the high-temperature system are arranged in a crossed mode, and a fan is arranged at the position of the finned tube heat exchanger.
2. The novel high-efficiency multi-mode cascade high-temperature heat pump unit according to claim 1, characterized in that:
the first reservoir is connected with the finned tube heat exchanger through a first throttling valve;
the finned tube heat exchanger is connected with the first economizer through a second throttling valve group;
the second reservoir is connected with the first economizer through an enthalpy-increasing solenoid valve and a third throttle valve group.
3. The novel high-efficiency multi-mode cascade high-temperature heat pump unit according to claim 1, characterized in that: the air suction port of the high-temperature compressor is connected with the first gas-liquid separator through a liquid spraying capillary tube and a liquid spraying electromagnetic valve.
4. The novel high-efficiency multi-mode cascade high-temperature heat pump unit according to claim 1, characterized in that: the water-cooled heat exchanger is a double-pipe heat exchanger or a plate heat exchanger or a high-efficiency tank heat exchanger.
5. The novel high-efficiency multi-mode cascade high-temperature heat pump unit according to claim 1, characterized in that: the first economizer and the second economizer are plate heat exchangers.
6. The novel high-efficiency multi-mode cascade high-temperature heat pump unit according to claim 1, characterized in that: the first throttle valve group, the second throttle valve group and the third throttle valve group are all composed of an electronic expansion valve, a capillary tube and a filter.
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112594957A (en) * | 2020-12-18 | 2021-04-02 | 浙江艾奇尼环境科技有限公司 | Air source heat pump system applied to field of liquor distillation |
| CN113251683A (en) * | 2021-06-17 | 2021-08-13 | 广州能茵热泵科技有限公司 | Cascade type air source heat pump system capable of automatically switching high-low evaporation and operation method |
| CN113310234A (en) * | 2021-06-17 | 2021-08-27 | 青岛理工大学 | Comprehensive frequency conversion cascade type air source heat pump system and operation method |
| CN113310235A (en) * | 2021-06-17 | 2021-08-27 | 青岛理工大学 | Cascade type variable frequency heat pump system capable of automatically switching high and low condensation and operation method |
| CN115420029A (en) * | 2022-07-21 | 2022-12-02 | 日出东方控股股份有限公司 | Novel efficient multi-mode cascade heat pump system and operation method thereof |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN112594957A (en) * | 2020-12-18 | 2021-04-02 | 浙江艾奇尼环境科技有限公司 | Air source heat pump system applied to field of liquor distillation |
| CN113251683A (en) * | 2021-06-17 | 2021-08-13 | 广州能茵热泵科技有限公司 | Cascade type air source heat pump system capable of automatically switching high-low evaporation and operation method |
| CN113310234A (en) * | 2021-06-17 | 2021-08-27 | 青岛理工大学 | Comprehensive frequency conversion cascade type air source heat pump system and operation method |
| CN113310235A (en) * | 2021-06-17 | 2021-08-27 | 青岛理工大学 | Cascade type variable frequency heat pump system capable of automatically switching high and low condensation and operation method |
| CN113310235B (en) * | 2021-06-17 | 2021-12-31 | 青岛理工大学 | Cascade type variable frequency heat pump system capable of automatically switching high and low condensation and operation method |
| CN113310234B (en) * | 2021-06-17 | 2022-02-18 | 青岛理工大学 | Comprehensive frequency conversion cascade type air source heat pump system and operation method |
| CN115420029A (en) * | 2022-07-21 | 2022-12-02 | 日出东方控股股份有限公司 | Novel efficient multi-mode cascade heat pump system and operation method thereof |
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