CN116123744A - Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit - Google Patents
Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit Download PDFInfo
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- CN116123744A CN116123744A CN202310298784.XA CN202310298784A CN116123744A CN 116123744 A CN116123744 A CN 116123744A CN 202310298784 A CN202310298784 A CN 202310298784A CN 116123744 A CN116123744 A CN 116123744A
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- 238000001704 evaporation Methods 0.000 claims abstract description 24
- 230000008020 evaporation Effects 0.000 claims abstract description 20
- 239000007788 liquid Substances 0.000 claims description 21
- 230000001502 supplementing effect Effects 0.000 claims description 12
- 230000005494 condensation Effects 0.000 claims description 3
- 238000009833 condensation Methods 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 description 37
- 238000010438 heat treatment Methods 0.000 description 19
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000005057 refrigeration Methods 0.000 description 6
- 230000009977 dual effect Effects 0.000 description 3
- 239000013589 supplement Substances 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000001932 seasonal effect Effects 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
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Classifications
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
An ultralow-temperature single-stage and double-stage hybrid air source heat pump unit relates to an air source heat pump. The evaporator and condenser heat exchange device comprises a first heat pump loop, a second heat pump loop, an evaporator parallel pipeline, a condenser parallel pipeline and an evaporation condenser, different operation conditions can be switched through the arranged evaporator parallel pipeline and the condenser parallel pipeline, two parallel evaporators can be simultaneously used at a low temperature level in ultralow temperature conditions, two parallel condensers are simultaneously used at a high temperature level, the heat exchange area of the evaporators and the condensers is utilized to the maximum extent, the performance coefficient is improved, and the device can be operated in an energy-saving and efficient mode all seasons.
Description
Technical Field
The invention relates to an air source heat pump, in particular to an ultralow-temperature single-stage and double-stage hybrid air source heat pump unit, and belongs to the technical field of heat pump system performance development.
Background
The air source heat pump is widely applied to the field of heat pump air conditioners due to the advantages of small investment, convenient installation and maintenance and the like. In severe cold areas, heating and heat supply are needed by utilizing the heating function, especially under the ultralow temperature working condition.
However, under the extreme outdoor temperature, the problems of insufficient heating quantity, low heating efficiency, overhigh exhaust temperature and the like of the traditional single-stage air source heat pump limit the application of the traditional single-stage air source heat pump in a low-temperature environment. To address these issues, a cascade/dual stage compression (including quasi-dual stage compression) heat pump may be employed to reduce the system compression ratio, typically with the cascade/dual stage compression heat pump system operating in a cascade/dual stage compression mode throughout the heating period. However, when the outdoor environment temperature is high, the overlapping/double-stage operation consumes more energy, so that the seasonal heating performance coefficient of the system is greatly reduced. The air source heat pump system with single-stage/cascade mode switching can solve the problems of overlarge compression ratio, overhigh exhaust temperature, reduced compression efficiency, reduced heating performance coefficient and the like of the conventional single-stage air source heat pump in a low-temperature environment, and does not need to adopt cascade operation all the time in the whole heating season.
However, when the current single-stage/cascade mode switching air source heat pump system is operated in the cascade mode, the evaporator of the high-temperature stage or the condenser of the low-temperature stage is closed without participating in heat exchange, so that the equipment utilization rate of the system is low, the initial investment is large and the economical efficiency is poor.
Disclosure of Invention
In order to solve the defects in the background art, the invention provides an ultralow temperature single-stage and double-stage hybrid air source heat pump unit, which can realize the switching of different operation conditions through the arranged evaporator parallel pipeline and condenser parallel pipeline, can simultaneously use two parallel evaporators at a low temperature stage and simultaneously use two parallel condensers at a high temperature stage under the ultralow temperature condition, maximally utilizes the heat exchange area of the evaporators and the condensers, improves the performance coefficient, and can operate in an energy-saving and high-efficiency mode all season.
In order to achieve the above purpose, the invention adopts the following technical scheme: an ultralow temperature single-stage and double-stage hybrid air source heat pump unit comprises a first heat pump loop, a second heat pump loop, an evaporator parallel pipeline, a condenser parallel pipeline and an evaporation condenser, wherein:
the first compressor outlet of the first heat pump loop is connected with a first condenser, a first evaporator and a first gas-liquid separator through a first four-way reversing valve, the first condenser is connected with a first economizer, the main path of the first economizer is connected with the first evaporator through a first electronic expansion valve, and the first evaporator is connected with the first gas-liquid separator;
the second compressor outlet of the second heat pump loop is connected with a second condenser, a second evaporator and a second gas-liquid separator through a second four-way reversing valve, the second evaporator is connected with a second economizer, the main path of the second economizer is connected with the second condenser through a third electronic expansion valve, and the second evaporator is connected with the second gas-liquid separator;
the condensing inlet of the evaporative condenser is provided with a second electromagnetic valve which is connected with the first four-way reversing valve, the condensing outlet of the evaporative condenser is connected with the first economizer, the evaporating inlet of the evaporative condenser is provided with a fourth electromagnetic valve which is connected with the second economizer, and the evaporating outlet of the evaporative condenser is connected with the second four-way reversing valve;
a first three-way valve is arranged at one end of the first condenser corresponding to the first four-way reversing valve, a second three-way valve is arranged at one end of the first condenser corresponding to the first economizer, a third three-way valve is arranged at one end of the second evaporator corresponding to the second economizer, and a fourth three-way valve is arranged at one end of the second evaporator corresponding to the second four-way reversing valve;
the condenser parallel pipeline is divided into two sections, one section is led out from the second condenser and is connected with the first three-way valve through a third check valve, and the other section is led out from the second three-way valve and is connected with the second condenser through a fourth check valve;
the parallel pipeline of the evaporator is divided into two sections, one section is led out by the first evaporator and is connected with the third three-way valve through the first check valve, and the other section is led out by the fourth three-way valve and is connected with the first evaporator through the second check valve.
Compared with the prior art, the invention has the beneficial effects that: the invention provides a single-stage/double-stage mixed air source heat pump unit which can be operated in a cascade mode when the ambient temperature is higher than the switching temperature T in summer and can be operated in a double-stage/double-stage mode when the ambient temperature is lower than the switching temperature T in winter.
Drawings
FIG. 1 is a schematic diagram of a single/double single stage operating condition of an air source heat pump unit of the present invention;
FIG. 2 is a schematic diagram of an air source heat pump unit operating mode of the present invention in cascade mode.
Detailed Description
The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are only some embodiments of the invention, but not all embodiments, and all other embodiments obtained by those skilled in the art without making creative efforts based on the embodiments of the present invention are all within the protection scope of the present invention.
As shown in fig. 1 to 2, an ultralow temperature single-stage and double-stage hybrid air source heat pump unit comprises five parts, namely a first heat pump loop, a second heat pump loop, an evaporator parallel pipeline, a condenser parallel pipeline and an evaporation condenser 13, wherein:
the first heat pump loop is used as a low-temperature-stage heat pump system and comprises a first compressor 1, a first four-way reversing valve 2, a first condenser 4, a first economizer 6, a first electronic expansion valve 7, a first evaporator 10 and a first gas-liquid separator 11, wherein an outlet of the first compressor 1 is connected with the first condenser 4, the first evaporator 10 and the first gas-liquid separator 11 through the first four-way reversing valve 2, the first condenser 4 is connected with the first economizer 6, the first economizer 6 is provided with a main path and a branch path, the branch path of the first economizer 6 returns to the first economizer 6 through a first electromagnetic valve 8 and a second electronic expansion valve 9 and enters the first compressor 1 to complete gas supplement after heat exchange, the main path of the first economizer 6 is connected with the first evaporator 10 through the first electronic expansion valve 7, and the first evaporator 10 is connected with the first gas-liquid separator 11;
the second heat pump loop is used as a high-temperature-stage heat pump system and comprises a second compressor 16, a second four-way reversing valve 17, a second condenser 18, a third electronic expansion valve 19, a second economizer 20, a second evaporator 24 and a second gas-liquid separator 26, wherein an outlet of the second compressor 16 is connected with the second condenser 18, the second evaporator 24 and the second gas-liquid separator 26 through the second four-way reversing valve 17, the second evaporator 24 is connected with the second economizer 20, the second economizer 20 is provided with a main path and a branch path, the branch path of the second economizer 20 returns to the second economizer 20 through a third electromagnetic valve 21 and a fourth electronic expansion valve 22 and enters the second compressor 16 to complete gas supplementing after heat exchange, the main path of the second economizer 20 is connected with the second condenser 18 through the third electronic expansion valve 19, and the second evaporator 24 is connected with the second gas-liquid separator 26;
the condensing inlet of the evaporation condenser 13 is provided with a second electromagnetic valve 12 which is connected with the first four-way reversing valve 2, the condensing outlet of the evaporation condenser 13 is connected with the first economizer 6, the evaporating inlet of the evaporation condenser 13 is provided with a fourth electromagnetic valve 29 which is connected with the second economizer 20, and the evaporating outlet of the evaporation condenser 13 is connected with the second four-way reversing valve 17;
a first three-way valve 3 is arranged at one end of the first condenser 4 corresponding to the first four-way reversing valve 2, a second three-way valve 5 is arranged at one end of the first condenser 4 corresponding to the first economizer 6, a third three-way valve 23 is arranged at one end of the second evaporator 24 corresponding to the second economizer 20, and a fourth three-way valve 25 is arranged at one end of the second evaporator 24 corresponding to the second four-way reversing valve 17;
the condenser parallel pipeline is divided into two sections, one section is led out from the second condenser 18 and is connected with the first three-way valve 3 through a third check valve 27, and the other section is led out from the second three-way valve 5 and is connected with the second condenser 18 through a fourth check valve 28;
the parallel pipeline of the evaporator is divided into two sections, one section is led out from the first evaporator 10 and is connected with the third three-way valve 23 through the first check valve 14, and the other section is led out from the fourth three-way valve 25 and is connected with the first evaporator 10 through the second check valve 15.
The ultralow-temperature single-stage and double-stage hybrid air source heat pump unit consists of five parts: the low-temperature-level heat pump system, the high-temperature-level heat pump system, the evaporator parallel pipeline, the condenser parallel pipeline and the evaporative condenser 13 are closely connected in space, the structure is compact, the system is a complete system, the opening number of the first compressor 1 and the second compressor 16 can be controlled according to the outdoor environment temperature, the requirements of users, different switching states of the first four-way reversing valve 2 and the second four-way reversing valve 17, the on-off states of the second electromagnetic valve 12 and the fourth electromagnetic valve 29 and the communication states of the first three-way valve 3, the second three-way valve 5, the third three-way valve 23 and the fourth three-way valve 25, the operation of a cascade mode under the single-stage/double-stage operation refrigeration heating and ultralow temperature working conditions is realized, and the following detailed explanation of the operation of each working condition is carried out:
1. single stage operating mode
As shown in fig. 1, the second solenoid valve 12 and the fourth solenoid valve 29 are closed, and the ab port of the first three-way valve 3, the second three-way valve 5, the third three-way valve 23, and the fourth three-way valve 25 are communicated.
Low-temperature level single machine operation heating: the first compressor 1 is started, the second compressor 16 is closed, the first four-way reversing valve 2 is electrified, the refrigerant at the outlet of the first compressor 1 enters the first condenser 4 through the first four-way reversing valve 2 and the ab port of the first three-way valve 3 to be condensed and released, then enters the first economizer 6 through the ab port of the second three-way valve 5 to exchange heat and supercool, the refrigerant is separated into two paths after exiting the first economizer 6, the bypass refrigerant enters the second electronic expansion valve 9 through the first electromagnetic valve 8 to be throttled, then enters the first compressor 1 to complete air supplement after exchanging heat through the first economizer 6, the main refrigerant enters the first evaporator 10 to absorb heat through evaporation after being throttled through the first electronic expansion valve 7, then enters the first gas-liquid separator 11 through the first four-way reversing valve 2, and finally is inhaled by the first compressor 1 to complete heating cycle, and thus the cycle is reciprocated to supply heat for users;
low-temperature level single machine operation refrigeration: the first compressor 1 is started to close the second compressor 16, the first four-way reversing valve 2 is powered off, the refrigerant at the outlet of the first compressor 1 enters the first evaporator 10 through the first four-way reversing valve 2 to release heat, then the refrigerant enters the first electronic expansion valve 7 to be throttled and then is divided into two paths, the branch refrigerant enters the second electronic expansion valve 9 to be throttled through the first electromagnetic valve 8, then enters the first compressor 1 to complete air supplementing after exchanging heat through the first economizer 6, the main refrigerant enters the first economizer 6 to exchange heat and supercool, then enters the first condenser 4 to absorb heat through the ba port of the second three-way valve 5, then enters the first gas-liquid separator 11 through the ba port of the first three-way valve 3 and the first four-way reversing valve 2, and finally is inhaled by the first compressor 1 to complete refrigeration cycle, thus the cycle is reciprocated and cooled for users;
high-temperature-level single-machine operation heating: closing the first compressor 1, starting the second compressor 16, electrifying the second four-way reversing valve 17, enabling the refrigerant at the outlet of the second compressor 16 to enter the second condenser 18 through the second four-way reversing valve 17 for condensation and heat release, then throttling the refrigerant through the third electronic expansion valve 19, dividing the refrigerant into two paths, throttling the bypass refrigerant again through the third electromagnetic valve 21 by the fourth electronic expansion valve 22, entering the second economizer 20 for heat exchange, entering the second compressor 16 for air supplementing, entering the second economizer 20 for heat exchange and supercooling after the main refrigerant enters the second evaporator 24 for evaporation and heat absorption through the ab port of the third three-way valve 23, entering the second gas-liquid separator 26 through the ab port of the fourth three-way valve 25 and the second four-way reversing valve 17, finally inhaling by the second compressor 16 for completing the heating cycle, and circularly reciprocating to provide heat for users;
high-temperature-level single-machine operation refrigeration: the first compressor 1 is closed, the second compressor 16 is opened, the second four-way reversing valve 17 is powered off, the refrigerant at the outlet of the second compressor 16 enters the second evaporator 24 through the ba ports of the second four-way reversing valve 17 and the fourth three-way valve 25 to be condensed and released, then enters the second economizer 20 through the ba port of the third three-way valve 23 to exchange heat and cool, the refrigerant is divided into two paths, the branch refrigerant enters the second economizer 20 to exchange heat after being throttled again by the fourth electronic expansion valve 22 through the third electromagnetic valve 21, finally enters the second compressor 16 to complete air supplementing, the main refrigerant enters the second condenser 18 to absorb heat through evaporation after being throttled by the third electronic expansion valve 19, then enters the second gas-liquid separator 26 through the second four-way reversing valve 17, and finally is inhaled by the second compressor 16 to complete refrigeration cycle, thus the cycle is reciprocated and cooled for users.
2. Double single stage operating mode
As shown in fig. 1, the second solenoid valve 12 and the fourth solenoid valve 29 are closed, and the ab port of the first three-way valve 3, the second three-way valve 5, the third three-way valve 23, and the fourth three-way valve 25 are communicated.
The first compressor 1 and the second compressor 16 are simultaneously started, the first four-way reversing valve 2 and the second four-way reversing valve 17 are electrified when heating and are powered off when cooling, and the heating/cooling operation mode is the same as that of the single-stage operation.
3. Operating conditions in cascade mode
As shown in fig. 2, the second solenoid valve 12 and the fourth solenoid valve 29 are opened, the bc ports of the first three-way valve 3 and the third three-way valve 23 are communicated, and the ac ports of the second three-way valve 5 and the fourth three-way valve 25 are communicated.
Cascade mode low temperature stage heating: the first compressor 1 is started, the first four-way reversing valve 2 is electrified, the refrigerant at the outlet of the first compressor 1 enters the evaporative condenser 13 through the first four-way reversing valve 2 and the second electromagnetic valve 12 to be condensed and released, then enters the first economizer 6 to exchange heat and supercool, the refrigerant is separated into two paths after exiting from the first economizer 6, the bypass refrigerant enters the second electronic expansion valve 9 to be throttled through the first electromagnetic valve 8 and enters the first compressor 1 to complete air supplementing after exchanging heat through the first economizer 6, the main refrigerant is separated into two paths after being throttled through the first electronic expansion valve 7, the first path of refrigerant enters the first evaporator 10 to absorb heat by evaporation, the second path of refrigerant enters the second evaporator 24 to absorb heat by evaporation through the cb port of the first check valve 14 and the third three-way valve 23, then enters the first air-liquid separator 11 through the ac port of the fourth three-way valve 25 and the second check valve 15 to be combined with the first path of refrigerant, and finally the refrigerant is sucked into the first compressor 1 to complete low-temperature-level heat circulation, such as heat supply circulation of a user;
cascade mode high temperature stage heating: the second compressor 16 is started, the second four-way reversing valve 17 is electrified, the refrigerant at the outlet of the second compressor 16 is divided into two paths after passing through the second four-way reversing valve 17, the first path of refrigerant enters the second condenser 18 to be condensed and released, the second path of refrigerant enters the first condenser 4 to be condensed and released after passing through the third check valve 27 and the cb port of the first three-way valve 3, then the second path of refrigerant is converged with the first path of refrigerant through the ac port of the second three-way valve 5 and the fourth check valve 28, the refrigerant is divided into two paths after being throttled by the third electronic expansion valve 19, the branch refrigerant enters the second economizer 20 to be subjected to heat exchange after being throttled again by the fourth electronic expansion valve 22 through the third electromagnetic valve 21, finally enters the second compressor 16 to complete the air supplementing, the main path of refrigerant enters the second economizer 20 to be subjected to heat exchange, then enters the evaporation condenser 13 to be evaporated and released through the fourth electromagnetic valve 29, and finally the refrigerant enters the second gas-liquid separator 26 through the second four-way reversing valve 17 to be inhaled by the second compressor 16 to complete the heating cycle, and the cycle is reciprocated in such a way, and heat is supplied to a user.
The refrigerants in the low-temperature-level heat pump system and the high-temperature-level heat pump system are the same refrigerant, the variable-frequency compressors are preferably adopted by the two compressors, the air supplementing and enthalpy increasing pressure system is arranged, whether the compressors need to supplement air or not can be controlled by controlling the on-off of the electromagnetic valve arranged on the air supplementing pipeline, the liquid storage tanks can be arranged in the low-temperature-level heat pump system and the high-temperature-level heat pump system, the refrigerant can be reasonably distributed when the unit is switched between different modes, and the long-term stable operation of the unit is further ensured.
The first heat pump loop and the second heat pump loop are combined into a cascade mode system by combining the intermediate evaporative condenser with the evaporator parallel pipeline and the condenser parallel pipeline, so that a traditional intermediate water loop heat exchange module of the double-stage cascade heat pump system is replaced, the interstage heat transfer temperature difference loss is reduced, and the heat supply/cold performance under the extreme outdoor temperature is improved. In addition, the water loop between the primary heat pump and the secondary heat pump in the traditional single-stage/cascade system and the water loop which is bypassed from the condenser of the primary heat pump to the user side are eliminated, so that the system is more compact, the equipment utilization rate is higher, and the equipment cost is lower. The evaporator condensers at low temperature and high temperature are respectively communicated through the pipeline, and the pipeline is provided with valves such as an electromagnetic valve, a three-way valve and the like, so that the valves can be controlled to realize the operation of single-stage/double-stage operation refrigeration and heating and overlapping modes under the ultralow temperature working condition according to the change of outdoor temperature and the set switching temperature value, the performance coefficient of the air source heat pump system is improved, the applicable temperature range of the air source heat pump is enlarged, and the system can be operated in all seasons in an energy-saving and efficient manner.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Furthermore, it should be understood that although the present disclosure describes embodiments, not every embodiment is provided with a separate embodiment, and that this description is provided for clarity only, and that the disclosure is not limited to the embodiments described in detail below, and that the embodiments described in the examples may be combined as appropriate to form other embodiments that will be apparent to those skilled in the art.
Claims (4)
1. An ultralow temperature single-stage and double-stage hybrid air source heat pump unit is characterized in that: the system comprises five parts, namely a first heat pump loop, a second heat pump loop, an evaporator parallel pipeline, a condenser parallel pipeline and an evaporation condenser (13), wherein:
an outlet of a first compressor (1) of the first heat pump loop is connected with a first condenser (4), a first evaporator (10) and a first gas-liquid separator (11) through a first four-way reversing valve (2), the first condenser (4) is connected with a first economizer (6), a main path of the first economizer (6) is connected with the first evaporator (10) through a first electronic expansion valve (7), and the first evaporator (10) is connected with the first gas-liquid separator (11);
an outlet of a second compressor (16) of the second heat pump loop is connected with a second condenser (18), a second evaporator (24) and a second gas-liquid separator (26) through a second four-way reversing valve (17), the second evaporator (24) is connected with a second economizer (20), a main path of the second economizer (20) is connected with the second condenser (18) through a third electronic expansion valve (19), and the second evaporator (24) is connected with the second gas-liquid separator (26);
a second electromagnetic valve (12) is arranged at a condensation inlet of the evaporation condenser (13) and is connected with the first four-way reversing valve (2), a condensation outlet of the evaporation condenser (13) is connected with the first economizer (6), a fourth electromagnetic valve (29) is arranged at an evaporation inlet of the evaporation condenser (13) and is connected with the second economizer (20), and an evaporation outlet of the evaporation condenser (13) is connected with the second four-way reversing valve (17);
a first three-way valve (3) is arranged at one end of the first condenser (4) corresponding to the first four-way reversing valve (2), a second three-way valve (5) is arranged at one end of the first condenser (4) corresponding to the first economizer (6), a third three-way valve (23) is arranged at one end of the second evaporator (24) corresponding to the second economizer (20), and a fourth three-way valve (25) is arranged at one end of the second evaporator (24) corresponding to the second four-way reversing valve (17);
the condenser parallel pipeline is divided into two sections, one section is led out from the second condenser (18) and is connected with the first three-way valve (3) through a third check valve (27), and the other section is led out from the second three-way valve (5) and is connected with the second condenser (18) through a fourth check valve (28);
the parallel pipeline of the evaporator is divided into two sections, one section is led out from the first evaporator (10) and is connected with the third three-way valve (23) through the first check valve (14), and the other section is led out from the fourth three-way valve (25) and is connected with the first evaporator (10) through the second check valve (15).
2. The ultra-low temperature single-stage and double-stage hybrid air source heat pump unit according to claim 1, wherein: the first compressor (1) and the second compressor (16) are variable frequency compressors.
3. The ultra-low temperature single-stage and double-stage hybrid air source heat pump unit according to claim 1 or 2, wherein: the first compressor (1) and the second compressor (16) are respectively provided with a gas supplementing and enthalpy increasing pressure system.
4. The ultra-low temperature single-stage and double-stage hybrid air source heat pump unit according to claim 3, wherein: the air supplementing and enthalpy increasing pressure system comprises a branch circuit arranged on a first economizer (6), wherein the branch circuit of the first economizer (6) returns to the first economizer (6) through a first electromagnetic valve (8) and a second electronic expansion valve (9) to exchange heat and then enters the first compressor (1) to complete air supplementing, the branch circuit arranged on a second economizer (20) is arranged on the second economizer, and the branch circuit of the second economizer (20) returns to the second economizer (20) through a third electromagnetic valve (21) and a fourth electronic expansion valve (22) to exchange heat and then enters the second compressor (16) to complete air supplementing.
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| CN202310298784.XA CN116123744A (en) | 2023-03-24 | 2023-03-24 | Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310298784.XA CN116123744A (en) | 2023-03-24 | 2023-03-24 | Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit |
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| CN116123744A true CN116123744A (en) | 2023-05-16 |
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| CN202310298784.XA Pending CN116123744A (en) | 2023-03-24 | 2023-03-24 | Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114674090A (en) * | 2022-04-12 | 2022-06-28 | 新科环保科技有限公司 | Low-ambient-temperature heating air-conditioning system |
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| CN105758049A (en) * | 2016-05-03 | 2016-07-13 | 天津商业大学 | Variable-flow single-working medium cascade heat pump system with parallel heat exchangers |
| US20160334143A1 (en) * | 2015-05-12 | 2016-11-17 | Shanghai Ocean University | Switchable two-stage and cascade marine energy-saving ultralow-temperature refrigeration system |
| CN208254010U (en) * | 2018-04-19 | 2018-12-18 | 董建 | A kind of full working scope air-source superposition type high-temperature-hot-water heat pump unit |
| CN115451599A (en) * | 2022-09-08 | 2022-12-09 | 山东力诺瑞特新能源有限公司 | Air source heat pump continuous steam supply system and control method |
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| US20160334143A1 (en) * | 2015-05-12 | 2016-11-17 | Shanghai Ocean University | Switchable two-stage and cascade marine energy-saving ultralow-temperature refrigeration system |
| CN105758049A (en) * | 2016-05-03 | 2016-07-13 | 天津商业大学 | Variable-flow single-working medium cascade heat pump system with parallel heat exchangers |
| CN208254010U (en) * | 2018-04-19 | 2018-12-18 | 董建 | A kind of full working scope air-source superposition type high-temperature-hot-water heat pump unit |
| CN115451599A (en) * | 2022-09-08 | 2022-12-09 | 山东力诺瑞特新能源有限公司 | Air source heat pump continuous steam supply system and control method |
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| CN114674090A (en) * | 2022-04-12 | 2022-06-28 | 新科环保科技有限公司 | Low-ambient-temperature heating air-conditioning system |
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