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WO2017179949A1 - Appareil de chauffage et de refroidissement à pompe à chaleur double - Google Patents

Appareil de chauffage et de refroidissement à pompe à chaleur double Download PDF

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Publication number
WO2017179949A1
WO2017179949A1 PCT/KR2017/004073 KR2017004073W WO2017179949A1 WO 2017179949 A1 WO2017179949 A1 WO 2017179949A1 KR 2017004073 W KR2017004073 W KR 2017004073W WO 2017179949 A1 WO2017179949 A1 WO 2017179949A1
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Prior art keywords
temperature side
low temperature
high temperature
evaporator
condenser
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PCT/KR2017/004073
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English (en)
Korean (ko)
Inventor
이도규
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Sinwoo Total Energy Co Ltd
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Sinwoo Total Energy Co Ltd
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Publication of WO2017179949A1 publication Critical patent/WO2017179949A1/fr
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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • 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

Definitions

  • the present invention relates to a dual heat pump air-conditioning apparatus, and more particularly, to a dual heat pump air-conditioning apparatus capable of normal operation even when the outside air is cryogenic temperature is improved stability and durability of the product.
  • a binary refrigeration cycle is a refrigeration system using refrigerants having different boiling points.
  • the refrigerant changes phase from liquid to gas or gas to liquid before and after the boiling point.
  • the dual refrigeration cycle is provided with a low temperature side refrigeration cycle using a low temperature side first refrigerant boiling at a low temperature and a high temperature side refrigeration cycle using a high temperature side second refrigerant boiling at a relatively high temperature, the evaporation of the high temperature side refrigerant And condensation of the low temperature side refrigerant occurs in one cascade heat exchanger.
  • the refrigerant discharge gas temperature at the high temperature side can be maintained at a constant high temperature of 85 ° C. or higher, which is effective for producing hot water.
  • the low temperature first refrigerant compressed by the low temperature side compressor supplies heat to the high temperature side refrigerant through the casecade heat exchanger, and then passes through the low temperature side expansion valve and the low temperature side evaporator of the outdoor unit to the low temperature side compressor. Reflowed.
  • Patent Document 0001 Korean Unexamined Patent Publication No. 10-2003-0071607
  • the present invention is to provide a binary heat pump cooling and heating device that is capable of normal operation even when the outdoor air is cryogenic temperature improves the stability and durability of the product.
  • the present invention comprises a low temperature side refrigeration cycle and a high temperature side refrigeration cycle, the low temperature side condenser and the high temperature side evaporator comprising a two-way heat exchanger coupled to heat exchange with each other,
  • the discharge side of the compressor is alternately connected to one of the high temperature side hot water condenser arranged to exchange heat with the hot water line of the hot water tank by the solenoid valve control and the high temperature side defrost cooling condenser arranged to exchange heat with the low temperature side external evaporator.
  • the low temperature side external evaporator discharge stage includes an evaporation compensation heat exchanger including the high temperature side subcondenser and the low temperature side evaporator so as to be connected to the low temperature side secondary evaporator inlet end arranged to exchange heat with the high temperature side secondary condenser.
  • the condenser discharge stage is connected to the high temperature according to the outside air temperature of the low temperature side
  • the first solenoid valve of the evaporation compensation line and the first solenoid valve are closed and the second solenoid valve of the high temperature heating line is controlled to be opened, and if the low temperature side external evaporator side outside temperature is less than or equal to a predetermined first evaporation compensation temperature;
  • the low temperature side condenser discharge end is provided to be alternately connected to one of the low temperature side defrost compensator and the low temperature side external evaporator arranged to exchange heat with the cold water line of the cold water tank by the solenoid valve control.
  • the solenoid valve is controlled to be connected to the low temperature side defrost compensator evaporator stage when the high temperature side defrost cooling condenser inlet stage is connected.
  • the low temperature side external evaporator and the high temperature side defrost cooling condenser are provided in pairs, and the low temperature side condenser discharge stage is branched in pairs so as to be connected to each low temperature side external evaporator.
  • the provided external evaporation line is connected, it is preferable that each of the high temperature side defrost cooling condenser discharge end is provided with a pressure control valve for controlling the condensation pressure of the high temperature side second refrigerant.
  • the capacity ratio between the low temperature side compressor of the low temperature side refrigeration cycle and the high temperature side compressor of the high temperature side refrigeration cycle is configured in a ratio of 1: 1, and the outside temperature of the low temperature side external evaporator is used to prevent overcompression of the low temperature side compressor. If the degree is more than a predetermined excessive temperature, it is preferable that the blowing fan rotation speed of the low-temperature external evaporator is controlled to slow down.
  • the present invention provides the following effects.
  • the low temperature side evaporator is connected to a low temperature side secondary evaporator arranged to exchange heat with a high temperature side secondary condenser at the low temperature side external evaporator discharge end, so that the residual heat of the high temperature side second refrigerant used for producing hot water can be supplied to the low temperature side first refrigerant.
  • the low temperature side of the first refrigerant can be smoothly evaporated even in a harsh environment, thereby maintaining stable heating performance and minimizing failure due to the liquid back phenomenon, thereby improving stability and durability of the device.
  • the contact area between the low temperature first refrigerant and the outside air is increased, thereby enabling a smoother evaporation, and also absorbing a large amount of heat from the outside air so as to absorb the high temperature side second refrigerant.
  • the heating efficiency of the device can be improved.
  • the high temperature side second refrigerant discharged from the high temperature side compressor is circulated to the defrost cooling condenser, and the low temperature side first refrigerant is circulated to the defrost compensation evaporator during the defrosting operation and at the same time the defrosting of the low temperature external evaporator is performed. Since the circulation process is absorbed by the low-temperature compressor and the compression process is maintained, the heat source for evaporation of the high-temperature second refrigerant can be continuously supplied to the dual-side heat exchanger, thereby enabling fast and efficient defrosting operation.
  • FIG. 1 is a block diagram of a dual heat pump air conditioning system according to an embodiment of the present invention.
  • Figure 2 is a flow chart showing the evaporation compensation operation of the dual heat pump heating and cooling apparatus according to an embodiment of the present invention.
  • Figure 3 is a flow chart showing the defrosting operation of the dual heat pump air-conditioning device according to an embodiment of the present invention.
  • the high temperature side compressor discharge stage uses hot water by solenoid valve control.
  • the high temperature side condenser selectively The solenoid valve is controlled so as to be connected to the high temperature side evaporator inlet, the hot water side condenser discharge end is connected to the high temperature side evaporator inlet via the high temperature side condenser, and the high temperature side condenser.
  • a high temperature heating line directly connected to the inlet end of the high temperature side evaporator is provided.
  • the first solenoid valve of the evaporation compensation line When the external temperature of the low temperature side evaporator side exceeds a preset first evaporation compensation temperature, the first solenoid valve of the evaporation compensation line is closed and the The second solenoid valve of the high temperature heating line is controlled to open, and if the low temperature side external evaporator side outside temperature is less than or equal to a predetermined first evaporation compensation temperature, the first solenoid valve of the evaporation compensation line and the second electron of the high temperature heating line. The valve is controlled to open, and the second evaporation compensation temperature is set to be less than the first evaporation compensation temperature of the low temperature side external evaporator side outside temperature. The first solenoid valve is opened, but the second solenoid valve is controlled to be closed.
  • the dual heat pump air-conditioning unit can be used in a business center that wants centralized heating and cooling such as a bathroom, a steam room, a swimming pool, and a high-rise building.
  • the heating and cooling can be simultaneously performed by supplying hot and cold water, but the maintenance cost can be reduced with high thermal efficiency.
  • It is an air conditioning unit.
  • FIG. 1 is a block diagram of a dual heat pump heating and cooling device according to an embodiment of the present invention.
  • the dual heat pump air conditioning apparatus 100 has a low temperature side refrigeration cycle using a low temperature side first refrigerant boiling at a relatively low temperature and a high temperature side boiling at a relatively high temperature. It consists of a high temperature side refrigeration cycle using a second refrigerant.
  • the low temperature side first refrigerant is preferably understood to mean a refrigerant boiling at a lower temperature than the high temperature side second refrigerant.
  • R-410a which is a mixed refrigerant of HFC series in which R-32 and R-125 are mixed at a composition ratio of 50:50 may be used, and R-410a may be used at 1 atm. It has a boiling point of -51 ° C.
  • the high temperature side second refrigerant may use R-134a of the HFC series, and the R-134a has a boiling point of ⁇ 26 ° C. at 1 atmosphere.
  • the binary heat pump air-conditioning unit is a low temperature side compressor 10, a binary heat exchanger 30, a low temperature side external evaporator 17, a low temperature side defrost compensator 15, an evaporative compensation heat exchanger 40, a high temperature side compressor. 20, a high temperature side hot water condenser 21, and a high temperature side defrost cooling condenser 28.
  • the low temperature side compressor 10 serves to circulate the refrigerant by supplying heat by compressing the low temperature side first refrigerant in the low temperature side refrigeration cycle and sending it to the binary heat exchanger 30.
  • the binary heat exchanger 30 means a device in which the low temperature side condenser 11 and the high temperature side evaporator 26 are coupled to each other to exchange heat.
  • the low temperature first refrigerant discharged from the low temperature side compressor 10 flows into the low temperature side condenser 11, and the high temperature side evaporator 26 passes through the high temperature side heating expansion valve 25. 2 Refrigerant flows in.
  • the heat of the low temperature side first refrigerant through the condensation of the low temperature side first refrigerant introduced into the low temperature side condenser 11 and the high temperature side second refrigerant introduced into the high temperature side evaporator 26 are increased. It can be delivered to the refrigerant.
  • the low temperature side first refrigerant condensed in the liquid state in the low temperature side condenser 11 flows to the low temperature side external evaporator 17 or the low temperature side defrost compensator 15.
  • the low temperature side first refrigerant flows through the low temperature side heating expansion side 16 to the low temperature side external evaporator 17 and absorbs ambient heat and evaporates.
  • the condensed low temperature first refrigerant passes through the low temperature side cooling expansion piece 14, It flows to the defrost compensator (15).
  • the defrost compensation evaporator 15 is arranged to exchange heat with the cold water line of the cold water tank (c), the first low-temperature side of the coolant is passed through the cooling line as it evaporates to take the heat of the water supplied to the cold water line
  • the water can be cooled to produce cooling water.
  • power consumption can be minimized by simultaneously producing cold water and hot water at the same time when cooling and hot water are required, such as a season change, so that the efficiency of the device can be improved.
  • the fan speed of the low temperature side external evaporator 17 is controlled to be reduced. Is preferred.
  • the excess temperature may be set to 7 ⁇ 40 °C.
  • the low temperature side first refrigerant is a low temperature side compressor 10, a low temperature side condenser 11, a heating expansion valve 16, and an external evaporator 17.
  • the low temperature side first refrigerant may absorb a large amount of heat from the external evaporator 17 due to a high temperature difference from the outside air.
  • the low temperature side first refrigerant has a high heat amount
  • the low temperature side first refrigerant A large amount of energy is required to compress the refrigerant, and there is a fear that the low temperature side compressor 10 and the high temperature side compressor 20 are overloaded.
  • the blowing fan provided in the low temperature side external evaporator 17 is controlled to reduce the rotational speed per hour, and the low temperature side first refrigerant may absorb appropriate heat.
  • the rotational speed of the blowing fan is controlled to decrease as the outside temperature increases, and when the outside temperature is higher than a certain temperature, the blowing fan may be stopped.
  • the high temperature side compressor 20 serves to circulate the high temperature side second refrigerant by compressing and sending the high temperature side second refrigerant to high temperature and high pressure in a high temperature side refrigeration cycle.
  • the inlet end of the high temperature side compressor 20 is connected to the outlet end of the high temperature side evaporator 26 of the binary heat exchanger 30.
  • the high temperature side second refrigerant absorbs heat generated by the condensation of the low temperature side first refrigerant in the high temperature side evaporator 26 and evaporates, and flows through the liquid separator 27 to the high temperature side compressor 20. As it is compressed, it is circulated in a gaseous state of high temperature and high pressure.
  • the high temperature side compressor 20 discharge end is a high temperature side hot water condenser 21 and a low temperature side external evaporator 17 arranged to exchange heat with the hot water line of the hot water tank h by the solenoid valve control 20a, 20b. It is provided to be alternately connected to one of the high-temperature side defrost cooling condenser 28 arranged to heat exchange with.
  • connection is alternately connected to one another when disconnected, but it is preferable to understand that it means to keep the connection state with one of the two.
  • the discharge end of the high temperature side compressor 20 is connected to the inlet end of the high temperature side hot water condenser 21.
  • the second refrigerant of the high temperature and high pressure is condensed in the high temperature side hot water condenser 21 and supplies heat to the water supplied to the hot water line, the water passing through the hot water line may be heated to produce hot water.
  • the high temperature side compressor 20 discharge end is connected to the high temperature side defrost cooling condenser 28 inlet end.
  • the high-temperature high-pressure second refrigerant is condensed in the high-temperature defrost cooling condenser 28 and supply heat to the low-temperature external evaporator 17, such as frost or frost generated in the low-temperature external evaporator 17, etc. This can be removed.
  • the evaporation compensation heat exchanger 40 means a device coupled to the heat exchange between the low temperature side evaporator 18 and the high temperature side auxiliary condenser 23.
  • the low temperature side first refrigerant discharged from the low temperature side external evaporator 17 discharge stage or the low temperature side defrost compensation evaporator 15 discharge stage passes through the evaporation compensation heat exchanger 40 to the low temperature side compressor 10. Flows into.
  • the low temperature side external evaporator 17 discharge end and the low temperature side defrost compensator 15 discharge end are connected to the inlet end of the low temperature side evaporator 18 arranged to exchange heat with the high temperature side auxiliary condenser 23. do.
  • the high temperature side hot water condenser 21 discharge end and the high temperature side defrost cooling condenser 28 discharge end selectively pass through the high temperature side auxiliary condenser 23 according to the outside air temperature of the low temperature side external evaporator 17 side.
  • the solenoid valve controls 22a and 22b are connected to the inlet end of the high temperature side evaporator 26.
  • the high temperature side auxiliary condenser 23 it may be circulated to the receiver 24, the high temperature side heating expansion 25 and the high temperature side evaporator 26.
  • the low outside air temperature is preferably understood to mean that the outdoor temperature at which the low temperature side external evaporator 17 is disposed is low enough that the low temperature side first refrigerant cannot be evaporated smoothly. It can be different depending on, but generally means a temperature lower than -7 °C.
  • the high temperature side second refrigerant of about 30 to 50 ° C. which is condensed and discharged after producing hot water in the high temperature side hot water condenser 21, passes through the high temperature side auxiliary condenser 23, One latent heat for evaporation of the refrigerant can be supplied.
  • the high temperature side second refrigerant does not pass through the high temperature side auxiliary condenser 23 and receives the receiver 24.
  • the high temperature side heating expansion piece 25 may be circulated to the high temperature side evaporator 26.
  • the low temperature side first refrigerant absorbs heat of outdoor air in which the low temperature side external evaporator 17 is disposed and is first evaporated to the low temperature side secondary evaporator 18. Flows.
  • the high temperature side second refrigerant of 30 ° C. to 50 ° C., which is primarily condensed, produces hot water.
  • the high temperature side secondary refrigerant is secondary condensed in the high temperature side secondary condenser 23, and residual heat of 30 to 50 ° C. remaining in the high temperature side secondary refrigerant after hot water is produced may be generated in the low temperature side secondary evaporator 18.
  • the low temperature side second refrigerant may be supplied, and the low temperature side first refrigerant may be supplied with sufficient heat to be secondarily evaporated.
  • the low temperature side first refrigerant completely evaporated through the second evaporation process flows to the low temperature side compressor 10 via the liquid separator 19. Accordingly, even when the outdoor temperature is excessively reduced, the failure of the device due to incomplete evaporation of the low temperature side first refrigerant can be significantly reduced.
  • the failure of the side compressor 10 can be significantly reduced.
  • Table 1 shows the result of measuring the heating efficiency (COP) according to the outside air temperature by comparing the present invention applied to the evaporation compensation heat exchanger and the conventional invention applied only to the binary heat exchanger.
  • the low temperature side first refrigerant is R-410a
  • the high temperature side second refrigerant is R-134a
  • Each heating efficiency (COP) was measured with the side compressor and the low temperature side compressor configured to have the same capacity ratio of 1: 1.
  • the present invention to which the evaporative compensation heat exchanger is applied shows a high heating efficiency as compared with the conventional binary heat exchanger only, and the present invention is 0.1 to 0.2 when the ambient temperature is -7 ° C. or more. It shows a somewhat higher heating efficiency (COP).
  • both the present invention and the conventional invention appears to decrease the heating efficiency (COP), in the case of the present invention at a normal temperature state (at a heating efficiency of 2 or more to -38 °C) 7 °C) was maintained at 60% performance and appeared to operate normally.
  • COP heating efficiency
  • the decrease in the heating efficiency according to the decrease in the external temperature is shown to be larger than the present invention.
  • the heating efficiency is drastically reduced to less than 2 during operation. It was found that, under -25 °C driving is impossible.
  • the evaporation compensating heat exchanger 40 is provided at the discharge end of the low temperature side external evaporator 17 so that the heat exchange between the high temperature side auxiliary condenser 23 and the low temperature side evaporator 18 is possible when the outside temperature is reduced. Heating efficiency and stability can be improved.
  • the residual heat of 30 to 50 ° C. remaining in the second refrigerant on the high temperature side is supplied to the first refrigerant on the low temperature side through the evaporative compensation heat exchanger 40, so that the low-temperature first refrigerant is completely completed even in a cryogenic environment. It can be evaporated to maintain a stable heating performance, and the occurrence of failure due to the liquid back phenomenon can be minimized to significantly improve the heating stability and durability of the device.
  • an evaporation compensation line (o, k, t, m, w) connected to the inlet end of the high temperature side evaporator 26 via the high temperature side auxiliary condenser 23 at the discharge end of the hot side hot water condenser 21.
  • a high temperature heating line (o, p, m, w) directly connected to the inlet end of the high temperature side evaporator 26 without passing through the high temperature side auxiliary condenser (23).
  • the second solenoid valve 22a of the lines o, p, m, and w may be controlled to open.
  • the first evaporation compensation temperature may be set corresponding to the boiling point of the low temperature side first refrigerant, and set to ⁇ 7 ° C. when the low temperature side first refrigerant has a boiling point similar to that of R-410a. desirable.
  • the first solenoid valve 22b is opened and the second solenoid valve 22a is opened. Can be controlled to close.
  • the second evaporation compensation temperature is set to a temperature lower than the first evaporation compensation temperature, and is preferably set to -15 ° C when the low temperature side first refrigerant has a boiling point similar to that of R-410a.
  • the high temperature side hot water condenser 21 discharge end and the high temperature side defrost cooling condenser 28 discharge end are connected to a first confluence part o, and the evaporation compensation line o, k, t, m, w ) And the high temperature heating line (o, p, m, w) is branched from the first confluence (o) is connected to the inlet end of the high temperature side evaporator (26).
  • the evaporation compensation line is provided with a first confluence part (o), the first solenoid valve (22b), but the evaporation inlet portion connecting the first confluence part (o) and the inlet end of the high temperature side auxiliary condenser (23) ( k), the evaporation discharge part (t) connected to the discharge end of the high temperature side auxiliary condenser (23).
  • the high temperature heating line includes a shielding portion p provided with a first confluence portion o and a second solenoid valve 22a. At this time, the end of the evaporation discharge portion (t) and the end of the shielding portion (p) are merged into one (m), and connected to the inlet end of the high temperature side evaporator (26) (w).
  • the evaporation compensation line and the high temperature heating line are joined to the first confluence part o, the evaporation discharge part t and the shielding part p, and are connected to the high temperature side evaporator 26 inlet end (m). , w)
  • the circulation path of the high temperature side second refrigerant during the solenoid valve control can be accurately classified. That is, the circulation path through which the high temperature side second refrigerant flows to the evaporator 26 without passing through the sub condenser 23 or the sub condenser 23 corresponding to the outdoor temperature where the low temperature side external evaporator 17 is disposed is It can be driven accurately.
  • Figure 2 is a flow chart showing the evaporation compensation operation of the dual heat pump cooling and heating apparatus according to an embodiment of the present invention.
  • the first solenoid valve 22b of the evaporation compensation line is closed, and the second solenoid valve 22a of the high temperature heating line is opened (s21). That is, the high temperature side second refrigerant is circulated without passing through the evaporation compensation heat exchanger 40.
  • the low temperature side refrigeration cycle during the heating operation is the low temperature side compressor (10), low temperature side condenser when the outside temperature exceeds -7 °C
  • the high temperature side refrigeration cycle includes a high temperature side evaporator 26, a liquid separator 27, a high temperature side compressor 20, a high temperature side hot water condenser 21, a receiver 24, and a high temperature side heating expansion valve 25. It has a circulation structure.
  • heat exchange between the high temperature side second refrigerant and the low temperature side first refrigerant is performed between the binary heat exchanger 30, that is, the low temperature side condenser 11 and the high temperature side evaporator 26, and the condensation step of the low temperature side first refrigerant.
  • Exothermic heat generated at may be used as a heat source for evaporation of the high temperature side second refrigerant.
  • the heat generated during the condensation of the low temperature side first refrigerant in the low temperature side condenser 11 is smoothly transferred to the high temperature side second refrigerant, and the heat loss of the high temperature side second refrigerant is reduced, 2
  • the refrigerant can be heated quickly.
  • the low temperature side first refrigerant is compressed in the low temperature side compressor 10, condensed in the low temperature side condenser 11 of the binary heat exchanger 30, and supplies heat to the high temperature side second refrigerant. Then, the condensed low temperature side first refrigerant flows through the receiver 12 to the low temperature side heating expansion side 16, expands, and is evaporated in the low temperature side external evaporator 17 to absorb heat from the outside air.
  • the low temperature side external evaporator 17 is preferably provided in pairs, and the low temperature side condenser 11 is branched in pairs so as to be connected to each of the low temperature side external evaporators 17a and 17b.
  • the external evaporation line s equipped with the low temperature side heating expansion sides 16a and 16b may be connected.
  • the low temperature side first refrigerant discharged from the low temperature side condenser 11 flows to the external evaporation line s through the receiver 12 and is divided along the branched portion of the external evaporation line s. It expands through the heating expansion sides 16a and 16b.
  • the low temperature side first refrigerant that is partially expanded at each of the heating expansion sides 16a and 16b may be flowed to each of the external evaporators 17a and 17b to be evaporated.
  • the low-temperature first refrigerant discharged from the low-temperature side condenser 11 is divided and expanded through each of the heating expansion sides 16a and 16b and flows along a pair of low-temperature external evaporators 17a and 17b, thereby contacting the outside air.
  • the evaporation can be more smoothly, and a large amount of heat can be absorbed from the outside air and supplied to the high temperature side second refrigerant, thereby improving the heating efficiency of the device.
  • the low temperature side first refrigerant flows to the low temperature side cooling expansion side 14, expands, and is then evaporated in the low temperature side defrost compensator. Can be.
  • a third solenoid valve 13a is provided at the discharge end of the low temperature side condenser 11 along an external evaporation line s connected to the low temperature side external evaporator 17 and at a low temperature in the external evaporation line s.
  • a fourth solenoid valve 13b is provided along the defrost compensation line branched to the side defrost compensator 15.
  • the low temperature side first refrigerant of the low temperature side condenser 11 passes through the low temperature side external evaporator 17 and the low temperature side auxiliary evaporator ( 18), when the third solenoid valve 13a is closed and the fourth solenoid valve 13b is opened, the low temperature first refrigerant of the low temperature side condenser 11 passes through the low temperature side defrost compensator 15 Flow to the side auxiliary evaporator (18).
  • the evaporated low temperature side first refrigerant passes through the low temperature side secondary evaporator 18 of the evaporation compensating heat exchanger 40, but is closed without closing the first solenoid valve 22b without the heat exchange with the high temperature side second refrigerant. 19) flows into the low temperature side compressor (10).
  • the high temperature side second refrigerant absorbs the heat of the low temperature side first refrigerant from the high temperature side evaporator 26 of the binary heat exchanger 30 and evaporates, and flows through the liquid separator 27 to the high temperature side compressor 20. do.
  • the high temperature side second refrigerant becomes gas of high temperature and high pressure by heat absorbed by the binary heat exchanger 30 and compression through the compressor 20.
  • the sixth solenoid valve 20b is provided at the discharge end of the high temperature side compressor 20 along the defrost line connected to the high temperature side defrost cooling condenser 28 and is heated to the hot water condenser 21.
  • a fifth solenoid valve 20a is provided along the line.
  • the fifth solenoid valve 20a is opened and the sixth solenoid valve 20b is closed, and the high temperature side second refrigerant flows to the high temperature side hot water condenser 21 to condense and is supplied to the hot water line. Heat with water.
  • the defrost waiting time Is preferably set according to the external humidity.
  • the defrost waiting time is preferably understood to mean a time required for defrosting operation to remove frost or frost from the external evaporator after the start of heating, defrosting operation is started when the defrost waiting time after the start of heating, defrosting If the waiting time has not elapsed, the heating operation is maintained.
  • the defrost waiting time is set to decrease as the external humidity increases, and as the defrost waiting time decreases, the time interval between the start of heating and the defrosting operation is shortened.
  • the defrost waiting time is set to increase, and as the defrost waiting time increases, the time interval between the heating start and the defrosting operation becomes longer.
  • the defrosting operation may be performed by preserving the heat of the high temperature side second refrigerant as much as possible.
  • both the first solenoid valve 22b of the evaporation compensation line and the second solenoid valve 22a of the high temperature heating line are opened (s41), and the external temperature is second evaporation.
  • the first solenoid valve 22b of the evaporation compensation line is opened, but the second solenoid valve 22a of the high temperature heating line is closed (s42).
  • the residual heat of some of the high-temperature second refrigerant may be preserved, but the remaining heat of the other part may be transferred from the evaporative compensation heat exchanger 40 to the low-temperature first refrigerant, so that the heating efficiency of the apparatus is optimized and the low temperature is low.
  • Complete evaporation of the side first refrigerant may be performed smoothly.
  • the low temperature side refrigeration cycle during the heating operation when the external temperature is less than the second preset evaporation compensation temperature is the low temperature side compressor (10), the low temperature side condenser (11), the receiver (12), the low temperature side heating expansion valve (16).
  • the low temperature side evaporator 17, the low temperature side evaporator 18, and the liquid separator 19 have a circulation structure.
  • the high temperature side refrigeration cycle includes a high temperature side evaporator 26, a liquid separator 27, a high temperature side compressor 20, a high temperature side hot water condenser 21, a high temperature side auxiliary condenser 23, a receiver 24, It has a circulation structure comprised of the high temperature side heating expansion edge 25.
  • the heat exchange between the high temperature side second refrigerant and the low temperature side first refrigerant is carried out between the binary heat exchanger 30, that is, between the low temperature side condenser 11 and the high temperature side evaporator 26, and the evaporation compensation heat exchanger 40, that is, the low temperature side. Between the subevaporator 18 and the hot side subcondenser 23.
  • the high temperature side second refrigerant is discharged from the high temperature side hot water condenser 21 and flows to the high temperature side auxiliary condenser 23.
  • the high temperature side second refrigerant is first condensed in the high temperature side hot water condenser 21, the hot water is heated and has a residual heat of 30 ⁇ 50 °C, secondary condensation in the secondary condenser 23 and the low temperature side agent
  • One refrigerant can supply heat.
  • the low temperature side first refrigerant evaporated to the low temperature side external evaporator 17 may flow to the low temperature side secondary evaporator 18 and may be secondly evaporated by the heat of the high temperature side second refrigerant.
  • the heat exchange between the high temperature side second refrigerant and the low temperature side first refrigerant may be performed at both sides of the binary heat exchanger 30 and the evaporative compensation heat exchanger 40 at a temperature lower than the first evaporation compensation temperature preset during the heating operation.
  • Figure 3 is a flow chart showing the defrosting operation of the dual heat pump air-conditioning apparatus according to an embodiment of the present invention.
  • the low temperature side condenser 11 discharge end is a low temperature side defrost compensator 15 arranged to exchange heat with the cold water line of the cold water tank (c) by the solenoid valve control (13a, 13b) And it is preferably provided to be alternately connected to one of the low-temperature external evaporator (17).
  • the low temperature side condenser 11 discharge end is connected to the low temperature side defrost compensation evaporator 15 inlet end when the high temperature side compressor 20 discharge end and the high temperature side defrost cooling condenser 28 inlet end are connected.
  • Valve controlled 13a, 13b is preferred.
  • the sixth solenoid valve 20b provided between the discharge end of the high temperature side compressor 20 and the inlet end of the high temperature side defrost cooling condenser 28 is opened, the discharge end and the low temperature of the low temperature side condenser 11 are opened.
  • the fourth solenoid valve 13b provided between the side defrost compensators 15 may be interlocked so as to be opened.
  • the low temperature side refrigeration cycle includes a low temperature side compressor (10), a low temperature side condenser (11), a receiver (12), a low temperature side cooling expansion valve (14), a low temperature side defrost compensator (15), and a low temperature side assistance. It has a circulation structure composed of an evaporator 18 and a liquid separator 19.
  • the high temperature side refrigeration cycle includes a high temperature side evaporator 26, a liquid separator 27, a high temperature side compressor 20, a high temperature side defrost cooling condenser 28, a receiver 24, and a high temperature side heating expansion valve 25. It has a configured circulation structure.
  • the blowing fan of the low temperature side evaporator 17 does not rotate and prevents endothermic evaporation of the low temperature side first refrigerant to reduce heating efficiency. do.
  • the elapsed time after the start of heating is compared with the preset defrost waiting time (s120).
  • the defrosting operation may be started when the external temperature is equal to or less than the predetermined defrost temperature and the elapsed time after the start of heating is equal to or greater than the preset defrost waiting time.
  • the defrost temperature and the defrost waiting time can be set by calculating the time point when the frost or frost occurs in the cold winter season through a test operation, the defrost waiting time is preferably calculated according to the algorithm applied defrost temperature and external humidity. .
  • a high humidity and a lot of dropping between 0 °C ⁇ 7 °C can reduce the evaporation efficiency of the low-temperature external evaporator 17, at -1 °C or less, the humidity is less than 40%, low dropping occurs after heating 90 Defrosting has been shown to be necessary after more than minutes of operation.
  • the waiting time can be set.
  • the defrosting operation may be started when the defrost waiting time is set according to the external humidity after the start of heating.
  • the sixth solenoid valve 20b is opened and the fifth solenoid valve 20a is closed so that the discharge end of the high temperature side compressor 10 is connected to the inlet end of the high temperature side defrost cooling condenser 28, but the low temperature side condenser 11 is closed.
  • the fourth solenoid valve 20b is opened and the third solenoid valve 20a is closed (s130) so that the discharge end is connected to the inlet end of the low temperature side defrost compensator.
  • the driving of the low temperature side compressor 10 is stopped (s140).
  • the low temperature side compressor 10 is restarted when a predetermined waiting time elapses after the start of the defrosting operation (s150) (s160).
  • the low temperature side compressor 10 is re-driven after the waiting time of about 20 seconds for efficient defrosting operation. This is preferred.
  • the low temperature side first refrigerant is a low temperature side compressor (10), a low temperature side condenser (11), a cooling expansion valve (14), a defrost compensation evaporator (15), a low temperature side evaporator (18), a liquid separator (19). It has a configured circulation path, and absorbs the heat of the cold water line is compressed in the evaporated state to supply heat from the low temperature side condenser 11 to the high temperature second refrigerant.
  • the high temperature side second refrigerant includes a high temperature side evaporator 26, a liquid separator 27, a high temperature side compressor 20, a defrost cooling condenser 28, a receiver 24, and a heating expansion valve 25. It has a path, and absorbs the heat of the low-temperature first refrigerant and is condensed in the defrost cooling condenser 28 in the compressed state to remove the frost or frost of the low-temperature external evaporator 17.
  • the high temperature side defrost cooling condenser 28 is preferably provided in pairs to correspond to the low temperature side external evaporator 17, it can be made more efficient defrosting operation.
  • the high temperature side second refrigerant may be continuously supplied with heat from the low temperature side first refrigerant and thus heated to a high temperature, thereby enabling rapid defrosting operation.
  • the fifth solenoid valve 20a is opened and the sixth solenoid valve is opened so that the discharge end of the high temperature side compressor 20 is connected to the inlet end of the high temperature side hot water condenser 21.
  • the solenoid valve 20b is closed, but the third solenoid valve 13a is opened and the fourth solenoid valve 13b is closed so that the low temperature side condenser 11 discharge end is connected to the low temperature side external evaporator 17 inlet end (s180). ).
  • the defrosting operation time may be set in response to the external temperature, it is preferably set to about 180 seconds between -7 ⁇ 7 °C, 300 seconds between -7 ⁇ -10 °C, -10 ⁇ -40 It is preferable that the temperature is set between 400 and 700 seconds.
  • the outside temperature is -10 ⁇ -40 °C, the humidity is very small, one defrosting operation is required every 6 to 9 hours.
  • the defrosting operation time elapses, the defrosting operation is terminated and the heating operation for generating hot water may be restarted.
  • the high temperature side second refrigerant heated along the high temperature side refrigeration cycle is circulated to the high temperature side defrost cooling condenser 28 which is heat-exchanged with the low temperature side external evaporator 17 to remove the drop of frost, frost and the like. Since the first refrigerant is circulated to the defrost compensation evaporator and absorbs heat from the cold water line and is compressed through the low temperature compressor, a heat source for evaporation of the high temperature second refrigerant may be continuously supplied to the binary heat exchanger.
  • the low temperature side first refrigerant has a low temperature side compressor (10), a low temperature side condenser (11), a cooling expansion valve (14), a defrost compensation evaporator (15), and a low temperature side. It has a circulation path composed of the auxiliary evaporator 18, the liquid separator 19, absorbs the heat of the cold water line and is compressed in the evaporated state to supply heat from the low temperature side condenser 11 to the high temperature side second refrigerant.
  • the high temperature side second refrigerant includes a high temperature side evaporator 26, a liquid separator 27, a high temperature side compressor 20, a defrost cooling condenser 28, a receiver 24, and a heating expansion valve 25. It has a path, absorbs the heat of the low temperature side first refrigerant, is condensed in the defrost cooling condenser 28 in the compressed state and releases heat to the outside air.
  • the high temperature side defrost cooling condenser 28 is preferably provided in pairs, and heat discharge to the outside air can be made more smoothly by increasing the contact area with the outside air.
  • each of the high temperature side defrost cooling condenser (28a, 28b) is preferably provided with a control valve for controlling the condensation pressure of the high temperature side second refrigerant. Accordingly, even when the outside air temperature is high, the high temperature side second refrigerant may be more liquefied more smoothly, and rapid heat dissipation is possible.
  • the dual heat pump air-conditioning apparatus of the present invention stable heating performance is maintained and failure occurrence due to the liquid back phenomenon is minimized, thereby improving stability and durability of the apparatus, and a pair of external evaporators are connected to the low-temperature condenser discharge end. 1
  • the contact area between the refrigerant and the outside air is increased, so that the evaporation can be more smoothly, and a large amount of heat can be absorbed from the outside air and supplied to the second refrigerant on the high temperature side, thereby improving the heating efficiency of the device. Since the heat source for evaporation of the refrigerant can be continuously supplied, there is an effect that can enable a fast and efficient defrosting operation is an invention of high industrial availability.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'objet de la présente invention est d'améliorer la stabilité et la durabilité des produits en permettant un fonctionnement normal même si l'air extérieur présente une température extrêmement basse. À cet effet, l'invention concerne un appareil de chauffage et de refroidissement à pompe à chaleur double comprenant un cycle frigorifique côté basse température et un cycle frigorifique côté haute température et comportant un échangeur de chaleur double dans lequel un condenseur côté basse température et un évaporateur côté haute température sont accouplés de façon à échanger de la chaleur entre eux, une extrémité de sortie du compresseur côté haute température étant disposée de façon à être reliée en alternance, au moyen de la commande d'une valve électronique, soit à un condenseur à eau chaude côté haute température disposé de façon à échanger de la chaleur avec une ligne d'eau chaude d'un réservoir d'eau chaude, soit à un condenseur de dégivrage et de refroidissement côté haute température disposé de façon à échanger de la chaleur avec un évaporateur externe côté basse température; une extrémité de sortie de l'évaporateur externe côté basse température étant disposée de façon à être reliée à une extrémité d'entrée d'un évaporateur auxiliaire côté basse température disposée de façon à échanger de la chaleur avec un condenseur auxiliaire côté haute température; et une extrémité de sortie du condenseur à eau chaude côté haute température étant commandée par la valve électronique de façon à être reliée à une extrémité d'entrée de l'évaporateur côté haute température au moyen du passage sélectif à travers le condenseur auxiliaire côté haute température en fonction de la température de l'air extérieur de l'évaporateur externe côté basse température.
PCT/KR2017/004073 2016-04-15 2017-04-14 Appareil de chauffage et de refroidissement à pompe à chaleur double Ceased WO2017179949A1 (fr)

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WO2025007269A1 (fr) * 2023-07-04 2025-01-09 华为数字能源技术有限公司 Dispositif d'échange de chaleur doté d'évaporateurs séparés, et système d'échange de chaleur

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109030059A (zh) * 2018-09-08 2018-12-18 湖南东尤水汽能热泵制造有限公司 一种低温热源热泵实验检测平台及检测方法
CN109030059B (zh) * 2018-09-08 2023-10-03 湖南东尤水汽能热泵制造有限公司 一种低温热源热泵实验检测平台及检测方法
WO2025007269A1 (fr) * 2023-07-04 2025-01-09 华为数字能源技术有限公司 Dispositif d'échange de chaleur doté d'évaporateurs séparés, et système d'échange de chaleur

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