EP1624260B1 - Climatiseur - Google Patents

Climatiseur Download PDF

Info

Publication number
EP1624260B1
EP1624260B1 EP20050016680 EP05016680A EP1624260B1 EP 1624260 B1 EP1624260 B1 EP 1624260B1 EP 20050016680 EP20050016680 EP 20050016680 EP 05016680 A EP05016680 A EP 05016680A EP 1624260 B1 EP1624260 B1 EP 1624260B1
Authority
EP
European Patent Office
Prior art keywords
cooling water
temperature
cooling
auxiliary
path
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20050016680
Other languages
German (de)
English (en)
Other versions
EP1624260A3 (fr
EP1624260A2 (fr
Inventor
Kei Akatsuka
Ryota Hirata
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanyo Electric Co Ltd
Original Assignee
Sanyo Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of EP1624260A2 publication Critical patent/EP1624260A2/fr
Publication of EP1624260A3 publication Critical patent/EP1624260A3/fr
Application granted granted Critical
Publication of EP1624260B1 publication Critical patent/EP1624260B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/004—Outdoor unit with water as a heat sink or heat source
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0213—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
    • F25B2313/02521—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses during cooling
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02543—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during heating
    • 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
    • F25B2327/00—Refrigeration system using an engine for driving a compressor

Definitions

  • the present invention relates to a gas heat pump type air conditioner in which a compressor is driven by a gas engine, and particularly to a technique for keeping the water temperature of cooling water for cooling the gas engine.
  • a gas heat pump type air conditioner equipped with a refrigerant circuit including a compressor driven by a gas engine serving as an internal combustion engine, a four-way valve, an outdoor heat exchanger and an indoor heat exchanger which are connected to one another through a refrigerant pipe, and a cooling water circuit for feeding cooling water to the gas engine by a cooling water pump to cool the gas engine (for example, see JP-A-2003-232582 ).
  • the exit side of the engine for the cooling water and the suction side of the cooling water pump for the cooling water are short-circuited to each other to increase the temperature of the cooling water, and a wax three-way valve (automatic temperature adjusting valve) for preventing the cooling water from passing through the outdoor heat exchanger is provided at the exit side of the engine, thereby controlling the temperature of the cooling water.
  • a wax three-way valve automated temperature adjusting valve
  • the conventional technique described above has a problem that the cost is increased because it uses a wax three-way valve for the temperature control of the cooling water. Furthermore, it has also a problem that it is impossible to sufficiently control the temperature of the cooling water through the temperature control of the cooling water based on the wax three-way valve.
  • EP 1 275 913 A2 discloses an air conditioner according to the preamble of claim 1.
  • Fig. 1 is a diagram showing the construction of a gas heat pump type air conditioner 100.
  • a refrigerant circuit is indicated by one-dotted chain lines and a cooling water circuit is indicated by heavy solid lines.
  • the air conditioner 100 has an indoor unit 1 and an outdoor unit 3, and an indoor heat exchanger 7 having a flow divider 5 appended thereto, a fan 9, etc. are disposed in the indoor unit 1.
  • an indoor heat exchanger 7 having a flow divider 5 appended thereto, a fan 9, etc.
  • a compressor 11 an electromagnetic type four-way valve 13
  • an auxiliary evaporator (sub evaporator) 15 appended with a flow divider 17, a fan 21, an expansion valve 72, etc.
  • reference numeral 43 represents an exhaust pipe connected to the inside of the exhaust heat exchanger 33
  • reference numeral 45 represents an inverter used to control the rotational number of the cooling water pump 39
  • reference numeral 47 represents a fan motor for driving the fan 21
  • reference numeral 49 represents a flexible coupling for coupling the engine 31 and the compressor 11 to each other.
  • the expansion valve 72 serves to adjust the flow amount of refrigerant flowing from the indoor heat exchanger 7 to the outdoor heat exchanger 19, and the radiator 20 serves to radiate the heat of the cooling water.
  • the radiator 20 is disposed at the downstream side of the fan 21 with respect to the outdoor heat exchanger 19 so as to suppress the thermal effect of the radiator 20 on the outdoor heat exchanger 19.
  • a control unit 61 for controlling the driving of the four-way valve 13, the electrically-operated three-way valve 37, the inverter 45, the fan motor 47, etc. is disposed in the outdoor unit 3.
  • the control unit 61 comprises CPU, an input/output interface, ROM, RAM, a timer counter, etc., and the input interface thereof is connected to a water temperature sensor 63 provided to a cooling water pipe 87 at the exit side of the engine 31, a heat exchange temperature sensor 65 secured to the outdoor heat exchanger 19, an exhaust temperature sensor 67 provided to an exhaust pipe 43, an outside air temperature sensor 69 secured to the outer wall surface, etc.
  • the control unit 61 is connected to a control unit (not shown) at the indoor unit 1 side, and these control units mutually transmit/receive signals therebetween.
  • liquid refrigerant flows from the refrigerant pipe 71 to the outdoor unit 3 side, and then passes through the expansion valve 72, the flow divider 17, the outer heat exchanger 19, the refrigerant pipe 75, the four-way valve 13 and the refrigerant pipe 77 into the auxiliary evaporator 15. At this time, the refrigerant is heated when passing through the heat exchanger 19 and the auxiliary evaporator 15.
  • a double-pipe type heat exchanger in which cooling water passes around the refrigerant pipe is adopted as the auxiliary evaporator 15, and a plate fin type heat exchanger in which the refrigerant pipe and the cooling water pipe are connected to each other through a plate fin is adopted as the outdoor heat exchanger 19 (see the outdoor heat exchanger 19 and the radiator 20 in Fig. 1 ).
  • Gas refrigerant heated in both the heat exchangers 19, 15 passes through the refrigerant pipe 78 and flows into the compressor 11 to be compressed, so that the refrigerant is heated.
  • High-temperature gas refrigerant discharged from the compressor 11 passes through a refrigerant pipe 79, the four-way valve 13 and a refrigerant pipe 81 and flows into the indoor heat exchanger 7 at the indoor unit 1 side. At this time, the refrigerant discharges heat energy to indoor air blow out from the fan 9 to be liquefied, and then the liquid refrigerant flows from the refrigerant pipe 71 to the outdoor unit 3 side again.
  • the auxiliary evaporator 15 for utilizing the heat of the cooling water of the engine 31 during heating operation and the exhaust heat exchanger 33 for utilizing the heat of the exhaust gas of the engine 31 for heating operation are provided in the outdoor unit 3, and thus even when the outside air temperature is lowered during heating operation, sufficient heating can be performed.
  • the four-way valve 6 is switched. That is, high-temperature gas refrigerant discharged from the compressor 11 passes through the refrigerant pipe 79, the four-way valve 13 and the refrigerant pipe 75, and then flows into the outdoor heat exchanger 19. At this time, the refrigerant is cooled and liquefied by low-temperature outside air in the outdoor heat exchanger 19. The refrigerant thus liquefied passes through the refrigerant pipe 71, and flows into the indoor heat exchanger 7 at the indoor unit 1 side. The refrigerant absorbs heat from the indoor air and it is evaporated.
  • the refrigerant thus evaporated passes through the refrigerant pipe 81, flows to the outdoor unit 3 side again and then flows through the four-way valve 13, the refrigerant pipe 77, the auxiliary evaporator 15 and the refrigerant pipe 78 into the compressor 78 again.
  • the circulation of the cooling water into the auxiliary evaporator 15 is stopped and thus the refrigerant is not heated in the auxiliary evaporator 15 except for a case where heating operation is carried out or a case where the temperature of the cooling water is lowered.
  • the cooling water circuit has a main cooling path in which the coolingwater discharged from the cooling water pump 39 is passed through the exhaust heat exchanger 33, the engine 31, the electrically-operated three-way valve 37 and the radiator 20 in this order and then flows back to the cooling water pump 39, and an auxiliary cooling path in which the cooling water discharged from the engine 31 is passed through the electrically-operated three-way valve 37 and the auxiliary evaporator 15 and then flows back to the cooling water pump 39.
  • the flow of the cooling water under heating operation will be described.
  • the cooling water discharged from the cooling water pump 39 passes through the cooling water pipe 85 and then flows into the exhaust heat exchanger 33 to be heated by the exhaust gas. Thereafter, the cooling water thus heated flows into the engine 31.
  • the high-temperature cooling water passes through the cooling water pipe 87, the electrically-operated three-way valve 37 and the cooling water pipe 89, and flows into the radiator 20 to radiate the heat energy thereof.
  • the cooling water which radiates the heat energy in the radiator 20 is passed through the cooling water pipe 91, and flows back to the cooling water pump 39 again.
  • the high-temperature cooling water may pass through not only the radiator 20, but also the auxiliary evaporator 15 as described later, whereby it subsidiarily heats the refrigerant. Furthermore, under cooling operation, the high-temperature cooling water passes through only the radiator 20, and radiates the heat energy.
  • the outdoor heat exchanger 19 and the radiator 20 may be integrally assembled with each other, so that these heat exchangers can be regarded as a single outdoor heat exchanger functioning as both a condenser for refrigerant and a radiator.
  • the cooling water discharged from the cooling water pump 39 passes through the cooling water pipe 85, and flows into the exhaust heat exchanger 33.
  • the refrigerant is heated by exhaust gas, and then flows into the engine 31.
  • the cooling water which cools the engine 31 and thus is increased in temperature passes through the cooling water pipe 87, the electrically-operated three-way valve 37 and the cooling water pipe 95 and then flows into the auxiliary evaporator 15 to heat the refrigerant and thus radiate the heat energy thereof.
  • the cooling water which radiates the heat energy in the auxiliary evaporator 15 is passed through the cooling water pipes 97, 91 and confluent into the cooling water pipe 91. Then, the cooling water passes through the cooling water pipe 91 and then flows back to the cooling water pump 39.
  • the cooling water temperature when the cooling water temperature is low, the cooling water is circulated through only the auxiliary cooling water, whereby the cooling water temperature is quickly increased.
  • the control unit 61 closes the port at the radiator 20 side of the electrically-operated three-way valve 37 while opening the port at the auxiliary evaporator 15 side of the electrically-operated three-way valve 37, whereby the entire amount of the cooling water is circulated to the auxiliary cooling path.
  • the heat radiation amount of the cooling water in the auxiliary evaporator 15 is smaller than that in the radiator 20 provided to the main cooling path, and thus the reduction level of the cooling water temperature when the cooling water is circulated through the auxiliary cooling path is smaller than that of the cooling water temperature when the cooling water is circulated through the main cooling path. Therefore, the cooling water temperature is higher in this case.
  • the auxiliary evaporator 15 having a smaller heat radiation amount than the radiator 20
  • the heat radiation amount of the cooling water when the cooling water is circulated through the auxiliary cooling path is reduced to a smaller value, and the cooing water temperature can be more increased.
  • the heat radiation amount of the auxiliary evaporator 15 is excessively small, the pressure loss of the refrigerant is increased in accordance with the type of the outdoor heat exchanger 19, which contributes to reduction in power of the refrigerant circuit.
  • a bypass pipe 99 is provided as shown in Fig. 1 so that the cooling water is split at the entrance side of the auxiliary evaporator 15 and a part of the cooling water bypasses the auxiliary evaporator 15. Accordingly, the heat radiation amount of the cooling water in the auxiliary cooling path can be suppressed to a lower level without increasing the pressure loss of the refrigerant, and the cooling water temperature can be quickly increased. Furthermore, in the construction that the bypass pipe 99 is provided as described above, the diameter of the bypass pipe 99 may be properly changed so that the ratio of the flow amounts of the cooling water flowing in the auxiliary evaporator 15 and the bypass pipe 99 is varied, and thus the heat radiation amount in the auxiliary cooling path can be simply adjusted.
  • a valve (not shown) whose opening degree is freely adjustable may be provided to the bypass pipe.
  • the flow amount of the cooling water distributed to the bypass pipe 99 can be freely varied by adjusting the opening degree of the valve, thereby adjusting the ratio of the flow amounts of the cooling water to be distributed to both the auxiliary evaporator 15 and the bypass pipe 99.
  • the electrically-operated three-way valve 37 is controlled so that the entire amount of the cooling water is circulated through the auxiliary cooling path having a smaller heat radiation amount than the main cooling path, whereby the cooling water temperature is increased to quickly reach the target temperature.
  • the cooling water pump 39 may be rotated at the lowest rotational number than the rotational number of the pump under normal operation so that the trap time of the cooling water in the engine 31 is lengthened and the increase of the cooling water temperature is promoted. Accordingly, the cooling water temperature can be made to reach the target temperature more early.
  • the control unit 61 gradually opens the port at the radiator 20 side of the electrically-operated three-way valve 37, so that the relatively high-temperature cooling water flows into the radiator 20.
  • the cooling water temperature can be quickly increased up to the target temperature just after the start of the engine, and thus the warm-up operation can be quickly completed.
  • waste heat can be withdrawn in the auxiliary evaporator even when the cooling water temperature is being increased in the warm-up operation, and thus the rise-up characteristic of the heating operation can be enhanced.
  • the rotational number of the cooling water pump 39 is controlled on the basis of the outside air temperature and the cooling water temperature to adjust the cooling water flow amount and keep the cooling water temperature to the target temperature so that water contained in the exhaust gas of the engine 31 is prevented from being condensed in the exhaust path or at the head portion of the engine 31 (the place at which the exhaust gas is discharged from the engine 31) and mixed with engine oil to generate sludge.
  • five judgment temperature levels A to E for providing the temperature ranges of the cooling water temperature are set and the rotational number of the cooling water pump 39 is controlled in accordance with which one of the judgment temperature levels A to E the present cooling water temperature belongs to as shown in Fig. 2 .
  • the judgment temperature levels A to E will be described in more detail.
  • a case where the present cooling water temperature is lower than the target temperature by a predetermined temperature is set as a judgment temperature level B
  • a case where the present cooling water temperature is further lower than that in the judgment temperature level B by a predetermined temperature is set as a judgment temperature level A
  • a case where the present cooling water temperature is higher than the target temperature by a predetermined temperature is set as a judgment temperature level D
  • a case where the present cooling water temperature is further higher than that in the judgment temperature level Dby a predetermined temperature is set as a judgment temperature level E.
  • the water temperature condition required to the cooling water as to whether the cooling water is used to heat the refrigerant is different between cooling operation and heating operation, and thus different temperature ranges are set to each of the judgment temperature levels A to E between cooling operation and heating operation. Furthermore, even under heating operation, different temperature ranges are set in accordance with the outside air temperature.
  • a case where the cooling water temperature is equal to the target temperature is set as the judgment temperature level C
  • a case where the cooling water temperature is lower than the target temperature by 2°C is set as the judgment temperature level B
  • a case where the cooling water temperature is lower than the target temperature by 10°C is set as the judgment temperature level A.
  • a case where the cooling water temperature is higher than the target temperature by 10°C is set as the judgment temperature level D
  • a case where the cooling water temperature is higher than the target temperature by 20°C is set as the judgment temperature E.
  • a case where the cooling water temperature is lower than the target temperature by 2°C is set as the judgment temperature level C
  • a case where the cooling water temperature is lower than the target temperature by 5°C is set as the judgment temperature level B
  • a case where the cooling water temperature is lower than the target temperature by 10°C is set as the judgment temperature level A
  • a case where the cooling water temperature is equal to the target temperature is set as the judgment temperature level D
  • a case where the cooling water temperature is higher than the target temperature by 10°C is set as the judgment temperature level E.
  • the rotational number of the cooling water pump 39 is gradually lowered to increase the cooling water temperature.
  • the rotational number of the cooling water pump 39 is reduced every 100rpm every time 200 seconds elapse until the cooling water temperature is equal to the judgment temperature level C or more.
  • the rotational number of the cooling water pump 39 is further reduced by only 100rpm.
  • the rotational number of the cooling water pump 39 is reduced by only 200rpm.
  • the rotational number of the cooling water pump 39 is gradually increased to suppress the increase of the cooling water temperature.
  • the rotational number of the cooling water pump 39 is increased every 100rpm every time 200 seconds elapses until the cooling water temperature is equal to the judgment temperature level D or less.
  • the rotational number of the cooling water pump 39 is further increased by only 100rpm.
  • the setting of the judgment temperature levels A to E shown in Fig. 2 and the increase amount (decrease amount) of the cooling water pump 39 shown in Fig. 3 are examples, and they can be properly changed in accordance with the performance of the air conditioner 100 or the type of the cooling water pump 39. Furthermore, during cooling operation, the cooling water is circulated through only the radiator 20 on the main cooling path without being circulated through the auxiliary cooling path, and the rotational number of the cooling water pump 39 is preferentially controlled to thereby carry out the control of keeping the cooling water temperature. At this time, only when the cooling water temperature is not increased even by the rotational number control of the cooling water pump 39, the cooling water is split to the auxiliary cooling path to promote the increase of the cooling water temperature.
  • the refrigerant circuit is provided with the auxiliary evaporator 15 in which the cooling water of the engine 31 is circulated, and also the cooling refrigerant circuit is provided with the main cooling path in which the cooling water passing through the engine 31 flows through the radiator 20 to the cooling water pump 39, the auxiliary cooling path in which the cooling water passing through the engine 31 passes through the auxiliary evaporator 15 and flows to the cooling water pup 39, and the electrically-operated three-way valve 39 for distributing the cooling water to the main cooling path and the auxiliary cooling path.
  • the electrically-operated three-way valve 37 is controlled on the basis of the temperature difference between the cooling water temperature and the target temperature, so that the cooling water are distributed to both the main cooling path and the auxiliary cooling path, or the overall amount of the cooling water is distributed to the auxiliary cooling path and the rotational number of the cooling water pump 39 is lowered. Therefore, the following effects can be achieved.
  • the cooling water is distributed to the auxiliary cooling path having a smaller heat radiation amount than that of the main cooling path, and further the rotational number of the cooling pump 39 is reduced so that the flow amount of the cooling water is reduced. Therefore, the heat radiation amount in the radiator 20 is suppressed, and also the trap time of the cooling water in the engine 31 is lengthened, so that the heat withdrawing amount from the engine 31 is also increased. Therefore, the reduction of the heat radiation amount of the cooling water and the increase of the heating amount of the cooling water are promoted, so that the cooling water temperature can be quickly increased.
  • the entire amount of the cooling water is distributed to the auxiliary cooling path to minimize the heat radiation of the cooling water, so that the cooling water temperature can be made to quickly reach the predetermined target temperature, and thus the time required until the warm-up operation is completed can be shortened.
  • the increase of the cooling water temperature can be promoted by reducing the rotational number of the cooling water pump 39.
  • the cooling water is distributed to both the main cooling path and the auxiliary cooling path, or the entire amount of the cooling water is distributed to the auxiliary cooling path, whereby the heat radiation amount of the cooling water can be adjusted and the coolingwater temperature can be accurately controlled.
  • the rotational number of the cooling water pump 39 is lowered while the entire amount of the cooling water is circulated through the radiator 20 of the main cooling path when the cooling water temperature is lowered, thereby promoting increase of the cooling water temperature.
  • the coolingwater is also distributed to the auxiliary cooling passage to suppress the heat radiation amount of the cooling water, thereby promoting increase of the cooling water temperature.
  • the cooling water temperature can be controlled by both the distribution of the cooling water to the main cooling path and the auxiliary cooling path and the control of the rotational number of the cooling water pump 39, and no wax three-way value is not needed unlike the prior art, so that the cost can be suppressed.
  • the rotational number of the cooling water pump 39 is increased on the basis of the temperature difference between the cooling water temperature and the target temperature. Therefore, in addition to the increase of the temperature of the cooling water temperature, it is possible to suppress the increase of the temperature. Accordingly, the cooling water temperature can be kept to the target temperature.
  • the cooling water flowing through the auxiliary cooling path is split to the auxiliary cooling path, and the bypass 99 for making the cooling water bypass the auxiliary evaporator 15 is provided. Therefore, the heat radiation amount of the cooling water in the cooling path can be suppressed to the low level without increasing the pressure loss of the refrigerant, and the cooling water temperature can be quickly increased.
  • the present invention is not limited to the embodiment described above, andanymodificationmaybemade to the embodiment without departing from the subj ect matter of the present invention.
  • the heat radiation amount of the cooling water in the auxiliary evaporator 15 is lowered.
  • the present invention is not limited to this mode.
  • the cooling water temperature is lower than the target temperature
  • the flow amount of the refrigerant flowing into the auxiliary evaporator 15 may be reduced by narrowing down the expansion valve 72, whereby the heat radiation amount of the cooling water in the auxiliary evaporator 15 is suppressed.
  • the opening degree of the expansion valve 72 may be controlled in combination with the construction that the bypass pipe 99 is provided.
  • the AC pump is used as the cooling water pump 39 and the rotational amount of the cooling water pump 39 is controlled by the inverter 45.
  • the present invention is not limited to this mode, and it may be modified so that a DC pump is used as the cooling water pump 39 and the rotational number is controlled by using no inverter 45.
  • a plate type heat exchanger may be used as the auxiliary heat exchanger 15.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Other Air-Conditioning Systems (AREA)

Claims (4)

  1. Climatiseur équipé d'un circuit de réfrigération comprenant un compresseur (11) entraîné par un moteur (31), une vanne à quatre voies (13), un échangeur de chaleur extérieur (19) et un échangeur de chaleur intérieur (7) qui sont reliés les uns aux autres par un conduit de fluide frigorigène, et d'un circuit d'eau de refroidissement pour amener de l'eau de refroidissement au moteur (31) au moyen d'une pompe d'eau de refroidissement (39) afin de refroidir le moteur (31), dans lequel le circuit de fluide frigorigène est en outre équipé d'un évaporateur auxiliaire (15) dans lequel on fait circuler l'eau de refroidissement pour le moteur (31) ; le circuit d'eau de refroidissement est en outre équipé d'un chemin de refroidissement principal par lequel l'eau de refroidissement qui traverse le moteur (31) revient par l'intermédiaire de l'échangeur de chaleur extérieur (19) à la pompe à eau de refroidissement (39), d'un chemin de refroidissement auxiliaire par lequel l'eau froide traversant le moteur (31) revient par l'intermédiaire de l'évaporateur auxiliaire (15) à la pompe d'eau de refroidissement (39), et d'une électrovanne à trois voies (37) pour aiguiller l'eau de refroidissement vers le chemin de refroidissement principal et le chemin de refroidissement auxiliaire ; et il est prévu une unité de commande (61) pour commander l'électrovanne à trois voies (37) sur la base de la différence de température entre la température d'eau de l'eau de refroidissement et une température de consigne de sorte que l'eau de refroidissement soit distribuée à la fois au chemin de refroidissement principal et au chemin de refroidissement auxiliaire ou seulement au chemin de refroidissement auxiliaire, caractérisé en ce que
    lorsque la température d'eau de l'eau de refroidissement est inférieure à la température de consigne, l'unité de commande (62) commande l'électrovanne à trois voies (37) de sorte que l'eau de refroidissement soit distribuée seulement au chemin de refroidissement auxiliaire (95), et elle réduit la vitesse de rotation de la pompe d'eau de refroidissement (39).
  2. Climatiseur selon la revendication 1, dans lequel, lorsque la température d'eau de l'eau de refroidissement est supérieure à la température de consigne, l'unité de commande augmente la vitesse de rotation de la pompe à eau de refroidissement sur la base de la différence de température entre la température de l'eau de refroidissement et la température de consigne.
  3. Climatiseur selon la revendication 1, dans lequel le chemin de refroidissement auxiliaire est en outre équipé d'un chemin de contournement (99) par lequel l'eau de refroidissement circulant dans le chemin de refroidissement auxiliaire est divisée de sorte que l'eau de refroidissement contourne l'évaporateur auxiliaire (15)
  4. Climatiseur selon la revendication 1, dans lequel le circuit de fluide frigorigène est en outre équipé d'une vanne de détente (72) pour modifier le débit de fluide frigorigène traversant l'échangeur de chaleur extérieur (19) et circulant dans l'évaporateur auxiliaire (15), et, lorsque la température d'eau de l'eau de refroidissement est inférieure à la température de consigne, l'unité de commande (61) réduit le degré d'ouverture de la vanne de détente (72) de sorte que le débit du fluide frigorigène circulant dans l'évaporateur auxiliaire (15) soit réduit.
EP20050016680 2004-08-03 2005-08-01 Climatiseur Expired - Fee Related EP1624260B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004226676A JP4565923B2 (ja) 2004-08-03 2004-08-03 空気調和装置

Publications (3)

Publication Number Publication Date
EP1624260A2 EP1624260A2 (fr) 2006-02-08
EP1624260A3 EP1624260A3 (fr) 2007-02-14
EP1624260B1 true EP1624260B1 (fr) 2008-10-08

Family

ID=35355612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050016680 Expired - Fee Related EP1624260B1 (fr) 2004-08-03 2005-08-01 Climatiseur

Country Status (5)

Country Link
EP (1) EP1624260B1 (fr)
JP (1) JP4565923B2 (fr)
KR (1) KR100597145B1 (fr)
CN (1) CN100462649C (fr)
DE (1) DE602005010159D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106338112A (zh) * 2016-10-21 2017-01-18 珠海格力电器股份有限公司 一种空调热回收***

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5057710B2 (ja) * 2006-06-30 2012-10-24 関西電力株式会社 ヒートポンプ式熱回収装置
KR101270616B1 (ko) * 2006-07-27 2013-06-07 엘지전자 주식회사 코제너레이션
FR2937589B1 (fr) * 2008-10-29 2012-07-13 Valeo Systemes Thermiques Boucle thermodynamique de climatisation integree a une installation de chauffage,ventilation et/ou climatisation equipant un vehicule,notamment a propulsion electrique.
JP5405161B2 (ja) * 2009-03-23 2014-02-05 三洋電機株式会社 空気調和装置およびエネルギー機器
JP5571978B2 (ja) * 2010-03-10 2014-08-13 大阪瓦斯株式会社 ヒートポンプシステム
CN102022804B (zh) * 2010-12-22 2013-06-12 广东美的电器股份有限公司 一种空调器的防凝露控制方法
CN103158488B (zh) * 2011-12-19 2016-09-28 杭州三花研究院有限公司 一种汽车空调***
CN103158486B (zh) * 2011-12-19 2016-06-15 杭州三花研究院有限公司 一种汽车空调***
CN103158490B (zh) * 2011-12-19 2016-05-25 杭州三花研究院有限公司 一种汽车空调***
CN103158489B (zh) * 2011-12-19 2016-06-15 杭州三花研究院有限公司 一种汽车空调***
CN103158487B (zh) * 2011-12-19 2016-05-04 杭州三花研究院有限公司 一种汽车空调***
CN103192681B (zh) * 2012-01-05 2016-05-04 杭州三花研究院有限公司 一种汽车空调***
EP3081881A1 (fr) * 2015-04-17 2016-10-19 Daikin Europe N.V. Unité de compresseur pour climatiseur et unité de source de chaleur pour un climatiseur comprenant l'unité de compresseur et une unité de source de chaleur
DE102016104730A1 (de) * 2016-03-15 2017-09-21 Connaught Electronics Ltd. Verfahren zum Detektieren eines Objekts entlang einer Straße eines Kraftfahrzeugs, Rechenvorrichtung, Fahrerassistenzsystem sowie Kraftfahrzeug
KR20180078049A (ko) * 2016-12-29 2018-07-09 포스코에너지 주식회사 폐열회수 장치와, 폐열회수 시스템 및, 이를 포함한 복합발전 플랜트
CN108312805B (zh) * 2018-01-04 2019-12-24 英格索兰（中国）工业设备制造有限公司 空调机组的控制方法及其控制装置
CN110285530A (zh) * 2019-06-12 2019-09-27 特灵空调***(中国)有限公司 控制方法、空调控制***、机器可读存储介质及空调***
JP2020201019A (ja) * 2019-06-13 2020-12-17 三菱重工エンジン＆ターボチャージャ株式会社 コジェネレーションシステム、制御方法及びプログラム
CN111098665B (zh) * 2020-01-19 2020-11-20 湖南汽车工程职业学院 一种内燃机汽车多模式温度管理***
JP2021156441A (ja) * 2020-03-25 2021-10-07 ヤンマーパワーテクノロジー株式会社 ヒートポンプ
CN112013606B (zh) * 2020-08-12 2024-01-30 浙江天旭机电设备有限公司 一种新型冷却水站
CN112188799B (zh) * 2020-09-21 2024-03-15 珠海格力电器股份有限公司 冷却***及其控制方法、冷水机组和空调器
CN113905594B (zh) * 2021-10-28 2023-03-14 珠海格力电器股份有限公司 变频器功率模块的散热控制方法、装置、介质及空调

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2538210B2 (ja) * 1986-06-06 1996-09-25 三洋電機株式会社 エンジン駆動式ヒ−トポンプ装置
JPS63207962A (ja) * 1987-02-24 1988-08-29 松下電器産業株式会社 エンジン駆動ヒ−トポンプ装置
JP2932312B2 (ja) * 1990-10-09 1999-08-09 ヤマハ発動機株式会社 エンジン駆動熱ポンプの空調装置
JP3059601B2 (ja) * 1992-12-29 2000-07-04 ヤンマーディーゼル株式会社 冷暖房混在型エンジン駆動ヒートポンプシステム
JP3600906B2 (ja) * 1995-02-08 2004-12-15 ヤマハ発動機株式会社 空気調和装置
JPH09158723A (ja) * 1995-12-08 1997-06-17 Toyota Motor Corp 冷却水回路のエア除去装置
JPH10103791A (ja) * 1996-09-30 1998-04-21 Toshiba Corp 冷凍サイクル装置および空気調和機
JP3358521B2 (ja) * 1997-12-25 2002-12-24 ダイキン工業株式会社 冷凍装置
JP3889529B2 (ja) * 1999-07-30 2007-03-07 三洋電機株式会社 エンジン冷却装置及びこのエンジン冷却装置を備えたガスヒートポンプ式空気調和装置
JP2001116392A (ja) * 1999-10-12 2001-04-27 Aisin Seiki Co Ltd 空調装置
JP2001330341A (ja) * 2000-03-14 2001-11-30 Mitsubishi Heavy Ind Ltd 空気調和装置
JP4097405B2 (ja) * 2001-01-30 2008-06-11 三洋電機株式会社 エンジン冷却方法及び装置並びに冷凍装置
JP4306136B2 (ja) * 2001-03-19 2009-07-29 株式会社デンソー ハイブリッドカーのエンジン冷却装置およびその制御方法
JP3798254B2 (ja) * 2001-03-29 2006-07-19 北海道瓦斯株式会社 空調方法、ヒートポンプおよび空調装置
JP4590777B2 (ja) * 2001-05-16 2010-12-01 アイシン精機株式会社 ヒートポンプ
JP4898025B2 (ja) * 2001-06-26 2012-03-14 三菱重工業株式会社 マルチ型ガスヒートポンプ式空気調和装置
EP1275913A3 (fr) * 2001-06-26 2003-08-13 Mitsubishi Heavy Industries, Ltd. Système multiforme de conditionnement d'air de type pompe à chaleur à gaz
JP2003035467A (ja) * 2001-07-24 2003-02-07 Sanyo Electric Co Ltd エンジン冷却装置
JP5030344B2 (ja) * 2001-08-31 2012-09-19 三菱重工業株式会社 ガスヒートポンプ式空気調和装置、エンジン冷却水加熱装置及びガスヒートポンプ式空気調和装置の運転方法
JP3973438B2 (ja) * 2002-02-06 2007-09-12 三洋電機株式会社 空気調和装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106338112A (zh) * 2016-10-21 2017-01-18 珠海格力电器股份有限公司 一种空调热回收***
CN106338112B (zh) * 2016-10-21 2018-07-17 珠海格力电器股份有限公司 一种空调热回收***

Also Published As

Publication number Publication date
JP4565923B2 (ja) 2010-10-20
CN1734214A (zh) 2006-02-15
CN100462649C (zh) 2009-02-18
KR100597145B1 (ko) 2006-07-06
JP2006046755A (ja) 2006-02-16
EP1624260A3 (fr) 2007-02-14
EP1624260A2 (fr) 2006-02-08
KR20060047781A (ko) 2006-05-18
DE602005010159D1 (de) 2008-11-20

Similar Documents

Publication Publication Date Title
EP1624260B1 (fr) Climatiseur
US6735969B2 (en) Gas heat pump type air conditioning device, engine-coolant-water heating device, and operating method for gas heat pump type air conditioning device
KR101758179B1 (ko) 히트 펌프식 급탕장치
KR101394051B1 (ko) 차량용 엔진 냉각 시스템 및 그 제어방법
JPH05223357A (ja) 空調装置
JP2003322388A (ja) 空気調和機
CN111251813B (zh) 车辆的热管理***及车辆
EP1334852B1 (fr) Appareil de climatisation avec dispositif de refroidissement d'un moteur
JP2017013561A (ja) 車両用のヒートポンプシステム
KR20200132373A (ko) 차량용 통합 열관리 시스템의 제어 방법
CN117136144A (zh) 车辆用空气调节***以及车辆用空气调节方法
EP1500536A1 (fr) Dispositif de refroidissement et procédé de commande d'un ventilateur de refroidissement de véhicule
JP4097405B2 (ja) エンジン冷却方法及び装置並びに冷凍装置
JP4169453B2 (ja) 貯湯式の給湯熱源装置
JP2016090174A (ja) 給湯空調システム
JP2002235968A (ja) 空気調和装置
JP3851847B2 (ja) 貯湯式の給湯熱源装置
JP7399321B2 (ja) チラーシステム及びチラーシステムを有する空気調和装置
JP3546102B2 (ja) エンジン駆動式空気調和機
US11446984B2 (en) Cooling system and cooling method
JP4144996B2 (ja) 貯湯式の給湯熱源装置
JP2952357B1 (ja) 空気調和装置
JP4620908B2 (ja) 貯湯式の給湯装置
WO2008018698A1 (fr) Appareil de chauffage de type pompe à chaleur
JP3594426B2 (ja) 空調装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050801

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17Q First examination report despatched

Effective date: 20070516

AKX Designation fees paid

Designated state(s): DE FR GB HU IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB HU IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 602005010159

Country of ref document: DE

Date of ref document: 20081120

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090709

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: HU

Payment date: 20100726

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20100728

Year of fee payment: 6

Ref country code: FR

Payment date: 20100824

Year of fee payment: 6

Ref country code: IT

Payment date: 20100814

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20100728

Year of fee payment: 6

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110802

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20120430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110801

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602005010159

Country of ref document: DE

Effective date: 20120301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110801

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120301