WO2004010060A1 - Cycle de refrigeration - Google Patents

Cycle de refrigeration Download PDF

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Publication number
WO2004010060A1
WO2004010060A1 PCT/JP2003/009319 JP0309319W WO2004010060A1 WO 2004010060 A1 WO2004010060 A1 WO 2004010060A1 JP 0309319 W JP0309319 W JP 0309319W WO 2004010060 A1 WO2004010060 A1 WO 2004010060A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
evaporator
refrigeration cycle
temperature
adjustment container
Prior art date
Application number
PCT/JP2003/009319
Other languages
English (en)
Japanese (ja)
Inventor
Shinichi Sakamoto
Yasuhiko Oka
Takayuki Sugimoto
Original Assignee
Daikin Industries, 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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to AU2003252242A priority Critical patent/AU2003252242A1/en
Priority to EP03765359A priority patent/EP1541939A4/fr
Publication of WO2004010060A1 publication Critical patent/WO2004010060A1/fr

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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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/01—Heaters
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a refrigeration cycle, for example, a refrigeration cycle that can be used for a heat source unit of a heat pump water heater.
  • the heat pump water heater generally includes a tank unit 51 having a hot water storage tank 50 and a heat source unit 53 having a refrigeration cycle 52.
  • the refrigeration cycle 52 is configured by connecting a compressor 54, a water heat exchanger (condenser) 55, an expansion valve 57, and an evaporator 58 in this order.
  • the tank unit 51 includes the hot water storage tank 50 and a circulation path 59, and a water circulation pump 60 and a heat exchange path 61 are interposed in the circulation path 59.
  • the heat exchange path 61 is constituted by a water heat exchanger 55.
  • the stored water flows out from the intake port provided at the bottom of the hot water storage tank 50 into the circulation path 59. This flows through the heat exchange path 61. At this time, the hot water is heated (boiled) by the water heat exchanger 55 and returned to the upper portion of the hot water storage tank 50 from the hot water inlet. With this, high-temperature hot water is stored in the hot water storage tank 50.
  • refrigerants such as dichlorodifluoromethane (R-12) and chlorodifluoromethane (R-22) have been used as refrigerants in the refrigeration cycle.
  • R-134a 1,1,1,1,2-tetrahydrofluoretane
  • R_134a still has problems such as high global warming ability.
  • a supercritical refrigerant such as carbon dioxide is useful as the natural refrigerant.
  • changes in the outside air temperature cause load fluctuations on the water heat exchanger (gas cooler) side and the evaporator side, and the amount of circulated refrigerant differs every season. That is, as shown in Fig.
  • a refrigerant regulating container 65 is provided on the high pressure side, and a flow regulating valve is provided.
  • the amount of refrigerant in the refrigerant adjustment container (receiver) 65 may be increased or decreased to obtain a refrigerant circulation amount according to the outside air temperature.
  • a bypass circuit 67 is provided which branches off at a position downstream of the branch portion, and the receiver 65 is provided in the bypass circuit 67.
  • a flow control valve 66 is provided at the outlet side of 65. That is, the bypass circuit 67 includes a first passage 68 branched from the upstream side of the water heat exchanger 55 and connected to the receiver 65, and a first passage 68 derived from the receiver 65. And a second passage 69 that joins the gas cooler 55 at a downstream side of the branching part of the second passage.
  • the above-mentioned regulating valve 66 is interposed in the second passage 69.
  • a refrigerant passage 70 connecting the expansion valve 57 and the evaporator 58 passes through the inside of the receiver 65.
  • heat exchange is performed between the high-pressure refrigerant flowing into the receiver 65 via the bypass circuit 67 and the low-pressure refrigerant flowing through the refrigerant passage 70. Then, by adjusting the opening degree of the adjusting valve 66, the flow rate of the refrigerant passing through the receiver 65 is adjusted, and the temperature of the refrigerant in the receiver 65 is adjusted. In other words, by controlling the opening degree of the flow control valve 66, the required refrigerant temperature can be maintained, and the receiver 65 ⁇ can have an appropriate refrigerant capacity, and the refrigerant circulation amount in this circuit can be reduced. The optimal amount can be used.
  • the present invention has been made in order to solve the above-mentioned conventional drawbacks.
  • the purpose of the present invention is to provide a refrigerant circulation amount according to each season, thereby avoiding overheating operation and wet operation.
  • Another object of the present invention is to provide a refrigeration cycle that can be configured at low cost without using a flow control valve or the like.
  • a refrigeration cycle of the present invention is a refrigeration cycle in which refrigerant discharged from a compressor is returned to the compressor through a gas cooler, a decompression mechanism, and an evaporator in order.
  • the refrigerant adjustment container is connected to a refrigerant passage between the container and the refrigerant via a connection passage, and the refrigerant adjustment container is arranged in a temperature environment that changes depending on the outside air temperature.
  • the refrigerant passage between the decompression mechanism and the evaporator and the refrigerant adjustment container are connected via the connection passage, so that the inside of the refrigerant adjustment container is provided between the decompression mechanism and the evaporator.
  • Refrigerant gas refrigerant
  • the refrigerant adjustment container is placed in a temperature environment that changes depending on the outside air temperature. Therefore, for example, since the outside air is hot in summer, the refrigerant adjustment container is kept at a high temperature side, the amount of refrigerant stored in the refrigerant adjustment container decreases, and the refrigerant circulation amount in the circulation path of the refrigeration cycle decreases. Can be added.
  • the refrigerant adjustment container since the outside air is cold in winter, the refrigerant adjustment container is kept at a low temperature, the amount of refrigerant stored in the refrigerant adjustment container increases, and the amount of refrigerant circulating in the circulation path of the refrigeration cycle is reduced. Can be done. That is, by placing the refrigerant adjustment container in a temperature environment that changes depending on the outside air temperature, the amount of refrigerant stored in the refrigerant adjustment container can be increased or decreased to achieve a refrigerant circulation amount according to the outside air temperature. Monkey
  • the refrigerant can be circulated with the amount of refrigerant corresponding to each season, and it is possible to prevent an excessive overheating operation or a wet operation.
  • the amount of circulating refrigerant varies depending on the outside air temperature without providing a bypass circuit or the like in which a regulating valve is interposed. Can be adjusted according to the temperature environment.
  • the refrigeration cycle of one embodiment is characterized in that the temperature environment that changes depending on the outside air temperature is formed by a refrigerant ranging from the evaporator outlet to the compressor inlet.
  • the refrigerant ranging from the evaporator outlet to the compressor inlet changes according to the outside air temperature. Therefore, a temperature environment that changes depending on the outside air temperature can be stably formed by the refrigerant, and the amount of the circulated refrigerant corresponding to the outside air temperature can be ensured.
  • the refrigerant adjustment container is attached to a refrigerant pipe extending from the evaporator outlet to the compressor suction port, and the refrigerant in the refrigerant pipe and the refrigerant in the refrigerant adjustment container are heated. It is characterized by being exchanged.
  • the refrigerant adjustment container is attached to the refrigerant pipe extending from the evaporator outlet to the compressor intake, the reliability of heat exchange between the refrigerant in the refrigerant pipe and the refrigerant in the refrigerant adjustment container is reduced.
  • the refrigerant circulation rate is high, and the refrigerant circulation amount can be stably set according to the outside air temperature.
  • the refrigeration cycle of one embodiment is characterized in that, in a refrigerant passage between the decompression mechanism and the evaporator, a throttle is provided on the evaporator side from a connection portion of the connection passage.
  • the refrigeration cycle of one embodiment is characterized in that the refrigerant adjustment container is arranged so as to be exposed to the outside air.
  • the refrigerant in the refrigerant adjustment container is warmed or cooled by the outside air.
  • the amount of refrigerant in the refrigerant adjustment container increases and decreases according to the outside air temperature, and the amount of refrigerant circulated according to each season.
  • the refrigeration cycle of one embodiment is characterized in that the refrigerant adjustment container is arranged in an air passage formed by a fan attached to the evaporator.
  • the refrigerant adjustment container is provided with a fan attached to the evaporator.
  • the temperature of the refrigerant adjustment container can be adjusted by this wind, since it is arranged in the wind passage generated by the above.
  • the refrigeration cycle is characterized in that the refrigerant adjustment container is arranged on the leeward side downstream of the evaporator.
  • the refrigerant adjustment container is arranged downstream of the evaporator on the leeward side, which is preferable in terms of heat exchange, and the temperature of the refrigerant adjustment container can be surely adjusted.
  • the refrigeration cycle of one embodiment is characterized in that the temperature environment that changes depending on the outside air temperature is configured by heating or cooling the refrigerant adjustment container with a Peltier element or the like.
  • the refrigerant adjustment container can be heated or cooled by a Peltier element or the like, so that the refrigerant in the refrigerant adjustment container can be reliably increased or decreased according to the outside air temperature.
  • the refrigerant circulation amount can be adjusted stably according to the season.
  • the refrigeration cycle of one embodiment is characterized in that the refrigerant adjustment container is arranged to exchange heat with water whose temperature changes depending on the outside air temperature.
  • the temperature of the refrigerant adjustment container is adjusted by water whose temperature depends on the outside air. That is, the amount of refrigerant in the refrigerant adjustment container increases and decreases according to the outside air temperature, and the amount of refrigerant circulated according to each season.
  • a refrigeration cycle includes a refrigerant passage between the decompression mechanism and the evaporator, wherein a throttle is provided on the evaporator side of a connection portion of the connection passage, and a refrigerant in the refrigerant adjustment container is provided. And heat exchange between the refrigerant and the refrigerant in the vicinity of the inlet of the evaporator on the downstream side of the throttle. Further, the refrigerant adjustment container is provided with a heater H for adjusting the amount of refrigerant.
  • the refrigerant in the refrigerant adjustment container exchanges heat with the low-temperature refrigerant immediately after passing through the throttle, so that the heat exchange can be reliably performed. Since a heater for adjusting the amount of refrigerant is provided, the temperature of the refrigerant adjustment container can be adjusted according to the outside air temperature by the heater.
  • the refrigeration cycle of one embodiment is characterized in that the high pressure side operates at supercritical pressure. ing.
  • FIG. 1 is a simplified diagram showing an embodiment of the refrigeration cycle of the present invention.
  • FIG. 2 is a Mollier diagram of the refrigeration cycle.
  • FIG. 3 is a Mollier diagram of a conventional refrigeration cycle.
  • FIG. 4 is a simplified view of a main part showing another embodiment of the refrigeration cycle of the present invention.
  • FIG. 5 is a simplified diagram showing a comparative example of a refrigeration cycle.
  • FIG. 6 is a simplified diagram of a conventional refrigeration cycle. BEST MODE FOR CARRYING OUT THE INVENTION
  • FIG. 1 shows a simplified diagram of a heat pump water heater using this refrigeration cycle.
  • This heat pump water heater has a tank unit 1 and a heat source unit 2, and heats water (hot water) in tank unit 1 with heat source unit 2. Is what you do.
  • the tank unit 1 has a hot water storage tank 3, and the hot water stored in the hot water storage tank 3 is supplied to a bathtub or the like (not shown). That is, the hot water storage tank 3 is provided with a water supply port 5 on a bottom wall thereof and a tap hole 6 on an upper wall thereof.
  • the hot water storage tank 3 has a water inlet 7 at the bottom wall and a hot water inlet 8 at the top of the side wall (peripheral wall), and the water inlet 7 and the hot water inlet 8 pass through the circulation path 9.
  • the circulation path 9 is provided with a water circulation pump 10 and a heat exchange path 11.
  • the heat source unit 2 includes the refrigeration cycle R according to this embodiment.
  • the freezing cycle R consists of a compressor 15, a water heat exchanger (gas cooler) 16, which constitutes the heat exchange path 11, a pressure reducing mechanism (electric expansion valve) 17, and an air heat exchanger (evaporator). 1) and 8 are connected in order. That is, the discharge port of the compressor 15 and the gas cooler 16 are connected through the refrigerant passage 20, the gas cooler 16 and the electric expansion valve 1 are connected through the refrigerant passage 21, The expansion valve 17 and the evaporator 18 are connected by a refrigerant passage 22, and the evaporator 18 and the compressor 15 are connected by a refrigerant passage 24 provided with an accumulator 23.
  • the refrigerant for example, carbon dioxide gas (C 0 2 ) whose high pressure side is used at a supercritical pressure is used.
  • the gas cooler as the water heat exchanger 16 has a function of cooling the high-temperature and high-pressure supercritical refrigerant compressed by the compressor 15.
  • the refrigerant passage 20 is provided with an HPS 25 as a pressure protection switch and a pressure sensor 26. Further, the evaporator 18 is provided with a fan 40 for adjusting the capacity.
  • the refrigeration cycle R includes a liquid-gas heat exchanger 27 for cooling the high-pressure refrigerant flowing out of the gas cooler 16.
  • the liquid-gas heat exchanger 27 has, for example, a double-pipe structure, in which a first passage 28 through which the refrigerant from the gas cooler 16 passes, and a refrigerant from the evaporator 18.
  • a second passage 29 passing therethrough That is, the first passage 28 constitutes a part of the refrigerant passage 21 connecting the gas cooler 16 and the electric expansion valve 17, and the second passage 29 constitutes the evaporator 18 and the compressor 1.
  • a part of the refrigerant passage 24 that connects to the refrigerant passage 5 is formed.
  • the refrigerant adjustment container 30 is a refrigerant pipe extending from the outlet of the evaporator to the inlet of the compressor, and more specifically, the liquid gas heat exchanger 2. 7 between the second passage 29 and the accumulator 23). Therefore, the refrigerant adjustment container 30 comes into contact with the refrigerant passage 24, and heat exchange between the refrigerant in the refrigerant adjustment container 30 and the refrigerant in the refrigerant passage 24 is enabled.
  • a connection passage 31 is connected to the refrigerant adjustment container 30. That is, the connection passage 3] is connected to the refrigerant passage 22 (a refrigerant passage between the pressure reducing mechanism 17 and the evaporator 18), It connects the container 30.
  • the refrigerant (gas refrigerant) of the refrigeration cycle R is drawn out from between the decompression mechanism 17 and the evaporator 18 and stored in the refrigerant adjustment container 30 as a liquid refrigerant.
  • the capacity of the refrigerant adjustment container 30 is determined by the cycle (compressor 15 ⁇ gas cooler 16 ⁇ decompression mechanism 17 ⁇ evaporator 18 ⁇ compressor 15 ⁇ circulation path through which the refrigerant circulates) About 1/10 of the total capacity (for example, about 300 to 400 cc).
  • a throttle 33 is provided on the evaporator 18 side from the connection portion 32 (point A) of the connection passage 31.
  • a force capable of using a fixed throttle such as a capillary tube or the like can be used as well as an electric expansion valve or the like.
  • a throttle having a suction superheat of 3 to 5 ° C is selected. Is preferred.
  • this heat pump water heater has a temperature sensor (input water thermistor) 34 that detects the temperature of the circulation path 9 on the upstream side of the heat exchange path 11, and the temperature sensor on the downstream side of the heat exchange path 11 of the circulation path 9.
  • Temperature sensor (outlet hot water thermistor) 35 that detects the temperature
  • temperature sensor (air heat exchange thermistor) 36 that detects the temperature of the evaporator 18, temperature sensor (the discharge pipe) that detects the discharge temperature of the compressor 15 Thermistor) 37
  • a temperature sensor (outside air temperature thermistor) 38 that detects the outside air temperature are provided. Then, data (detected temperature) from these sensors is input to a control unit (not shown) (not shown) of the heat pump water heater, and various controls are performed based on the data. Done.
  • the temperature of the discharge pipe is detected by the discharge pipe thermistor 37, and the opening of the electric expansion valve 17 is adjusted so that the discharge pipe temperature becomes the target discharge pipe temperature. It can be adjusted (controlled). If the temperature of the water input thermistor 34 is equal to or higher than a predetermined temperature (for example, 60 ° C.), it is determined that the hot water in the hot water storage tank 3 is boiling, and the operation is stopped. Based on the temperature, the operating frequency of the compressor 15 can be controlled to adjust the hot water heating capacity (boiling capacity) and the like.
  • a predetermined temperature for example, 60 ° C.
  • the compressor 15 is driven and the water circulation pump 10 is driven (operated). Then, the stored water (hot water) flows out of the water intake port 7 provided at the bottom of the hot water storage tank 3 and flows through the heat exchange path 11 of the circulation path 9. Further, the refrigerant discharged from the compressor 15 is returned to the compressor 15 via the gas cooler 16, the pressure reducing mechanism 17, and the evaporator 18 in order. Therefore, the water flowing through the heat exchange path 11 of the circulation path 9 is heated (boiled) by the water heat exchanger which is the gas cooler 16, and is returned from the hot water inlet 8 to the upper part of the hot water storage tank 3. You.
  • hot water is stored in the hot water storage tank 3.
  • the unit price of electricity at night is set lower than that of daytime, so it is preferable to perform this operation during the late night hours when the cost is low to reduce costs.
  • the Mollier diagram for this operation is shown in Figure 2. That is, in this refrigeration cycle, the high-pressure refrigerant in the state 1 is discharged from the compressor 15 and the high-pressure refrigerant is introduced into the gas cooler 16 (water heat exchanger). The gas cooler 16 exchanges heat with water passing through the heat exchange path 11. As a result, the water passing through the heat exchange path 11 is heated (boiled). Then, due to this heat exchange, the high-pressure refrigerant radiates heat to the water, and its enthalpy drops from 1 to 2. The high-pressure refrigerant in these two states is sent to the low-pressure mechanism 17 (expansion valve).
  • the high-pressure refrigerant is depressurized to the point A by the pressure reducing mechanism 17, and further reduced to the state of 3 by the throttle 33. Then, the low-pressure refrigerant is introduced into the evaporator 18. In the evaporator 18, the low-pressure refrigerant exchanges heat with air. Due to this heat exchange, the low-pressure refrigerant absorbs heat and evaporates. That is, the enthalpy increases from 3 to 4, and the low-pressure refrigerant in this 4 state is sent to the compressor 15.
  • the refrigerant at the connection point 32 (point A) of the refrigerant passage 22 between the pressure reducing mechanism 17 and the evaporator 18 and the connection passage 31 flows from the evaporator outlet to the compressor inlet. And heat is exchanged with the refrigerant between the second passage 29 of the liquid-gas heat exchanger 27 and the accumulator 23 (point B). For this reason, if the temperature at the point B rises in accordance with the outside air, the temperature of the refrigerant regulating container 30 also rises, and the refrigerant storage amount decreases, and the temperature at the point B rises in accordance with the outside air. If the temperature decreases, the temperature in the refrigerant adjustment container 30 also decreases, and the amount of stored refrigerant increases.
  • the refrigerant pipe (refrigerant passage 24) from the evaporator outlet to the compressor inlet is affected by the outside air temperature, and in summer when the outside air temperature is high, it is higher than in winter when the outside air temperature is low. is there. Therefore, as shown in Fig. 3, when the outside air temperature is high (high outside air), a cycle like I occurs, and when the outside air temperature is low (low outside air temperature), a cycle like ⁇ ⁇ ⁇ occurs. At the time of temperature), the density inside the evaporator 18 is higher than in winter (at low outside temperature). Therefore, there is a large difference in the amount of refrigerant in the evaporator 18 between the high outside temperature and the low outside temperature. And the amount of circulating refrigerant was large at low outside air temperatures, despite the small amount of circulating refrigerant.
  • the refrigerant adjustment container 30 since the outside air has a high temperature in summer, the refrigerant adjustment container 30 is kept on the high temperature side and stored in the refrigerant adjustment container 30. As a result, the amount of refrigerant to be cooled is reduced, and the amount of refrigerant circulated in the circulation path of the refrigeration cycle can be increased. In winter, since the outside air is at a low temperature, the refrigerant adjustment container 30 is kept at a low temperature, the amount of refrigerant stored in the refrigerant adjustment container 30 increases, and the refrigerant circulation amount in the circulation path of the refrigeration cycle. Can be reduced.
  • the amount of refrigerant in the refrigerant adjustment container 30 is increased or decreased to obtain a refrigerant circulation amount according to the outside air temperature. be able to. For this reason, it is possible to circulate the refrigerant with the amount of refrigerant according to each season, and it is possible to prevent an excessive overheating operation or a wet operation.
  • the circulation amount according to the outside air temperature becomes natural as described above, The operation can be performed with the circulation amount according to the outside air temperature for each operation, and it is possible to prevent overheating operation and wet operation. Therefore, if the refrigerant adjustment container 30 is not provided in the refrigerant passage 24 or the like and is placed in another temperature environment that changes depending on the outside air temperature, the operation is performed with the circulation amount according to the outside air temperature. It is possible.
  • the refrigerant in the refrigerant passage (refrigerant pipe) 24 and the refrigerant in the refrigerant adjustment container 30 are heated by attaching the refrigerant adjustment container 30 to the refrigerant passage 24.
  • the refrigerant adjustment container 30 may be arranged along a pipe between the throttle 33 and the evaporator 18. That is, heat exchange between the refrigerant in the refrigerant adjustment container 30 and the refrigerant near the inlet of the evaporator 18 downstream of the throttle 33 is enabled.
  • the refrigerant adjustment container 30 is provided with a heater H for adjusting the amount of the refrigerant.
  • the refrigerant in the refrigerant adjustment container 30 exchanges heat with the low-temperature refrigerant immediately after passing through the throttle 33, so that the heat exchange can be reliably performed.
  • the refrigerant adjustment container 30 is provided with a heater H for adjusting the amount of refrigerant, the heater H can adjust the temperature of the refrigerant adjustment container 30.
  • the refrigeration cycle can be reliably operated with the refrigerant circulation amount corresponding to each season. That is, in this case, a temperature environment that changes depending on the outside air temperature is formed by heat exchange with the low-temperature refrigerant and heating of the heater H.
  • the refrigerant adjustment container 30 is simply arranged at a position exposed to the outside air (for example, outside the casing in which the frozen cycle is stored). In this case, if the refrigerant adjustment container 30 is exposed to the outside air, the refrigerant adjustment container 30 is heated or cooled according to the temperature of the outside air. Further, since the evaporator 18 is provided with a fan 4 °, the refrigerant adjusting container 30 is arranged in an air passage formed by the fan 40. In this case, either upstream of the evaporator 18 or downstream of the evaporator 18. Also in this case, the temperature in the air passage depends on the outside air.
  • the refrigerant regulating container 30 on the leeward side downstream of the evaporator 18.
  • a Peltier element or the like may be used.
  • the ⁇ ⁇ / che element means that when current flows through the contacts of different types of conductors (or semiconductors), This element can exhibit the Peltier effect, which is a phenomenon that generates or absorbs heat in addition to the heat generated. Therefore, in this case, the outside air temperature is detected (detected) by the outside air temperature thermistor 38, and the Peltier element is caused to generate heat * by the refrigerant adjustment container 30 based on the outside air temperature.
  • the refrigerant adjustment container 30 may be configured to exchange heat with water.
  • the cooling water can be composed of city water (tap water), water flowing out from the intake port 7 of the hot water storage tank 3 to the circulation path 9, and the like. Water
  • the present invention is not limited to the above embodiments, and can be implemented with various modifications within the scope of the present invention.
  • the refrigerant regulating container 30 when the refrigerant regulating container 30 is disposed in the refrigerant conduit 24 extending from the evaporator outlet to the compressor inlet, the refrigerant regulating container 30 is disposed closer to the evaporator 18 than the second passage 29 of the liquid-gas heat exchanger 27. It is also possible. Further, it may be either a structure without the throttle 33 or a structure without the liquid-gas heat exchanger 27.
  • This refrigeration cycle can be used in various refrigeration systems such as air conditioners and showcases other than heat pump water heaters.
  • refrigerants include ethylene.
  • It may be a refrigerant used in supercritical conditions such as petane or nitric oxide.
  • refrigerant used in supercritical conditions such as petane or nitric oxide.

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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

La présente invention concerne un cycle de réfrigération qui fournit des quantités de circulation de réfrigérant en fonction des saisons, qui permet d'éviter un fonctionnement à l'état de surchauffe ou à l'état humide, qui ne nécessite pas l'utilisation d'une soupape de régulation d'écoulement ou analogue, et qui peut être construit pour un coût peu élevé. Dans ce cycle de réfrigération, un réfrigérant distribué par un compresseur (15) est amené à retourner au compresseur en passant successivement par un refroidisseur de gaz (16), un mécanisme réducteur de pression (17) et un évaporateur (18). Un passage de réfrigérant (22) et une cuve de régulation de réfrigérant (30), qui sont disposés entre le mécanisme réducteur de pression (17) et l'évaporateur (18), sont reliés entre eux par un passage de raccordement (31). La cuve de régulation de réfrigérant (30) est disposée dans un environnement de température qui change en fonction de la température de l'air extérieur.
PCT/JP2003/009319 2002-07-23 2003-07-23 Cycle de refrigeration WO2004010060A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU2003252242A AU2003252242A1 (en) 2002-07-23 2003-07-23 Refrigerating cycle
EP03765359A EP1541939A4 (fr) 2002-07-23 2003-07-23 Cycle de refrigeration

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JP2002213624A JP3963134B2 (ja) 2002-07-23 2002-07-23 冷凍サイクル
JP2002-213624 2002-07-23

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WO2004010060A1 true WO2004010060A1 (fr) 2004-01-29

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PCT/JP2003/009319 WO2004010060A1 (fr) 2002-07-23 2003-07-23 Cycle de refrigeration

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EP (1) EP1541939A4 (fr)
JP (1) JP3963134B2 (fr)
AU (1) AU2003252242A1 (fr)
WO (1) WO2004010060A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP2012007864A (ja) * 2010-06-28 2012-01-12 Mitsubishi Electric Corp 受液器及びそれを用いた冷凍サイクル装置

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JPH0414975U (fr) * 1990-05-25 1992-02-06
WO1999008053A1 (fr) * 1997-08-12 1999-02-18 Zexel Corporation Cycle de refroidissement
JP2000179958A (ja) * 1998-12-16 2000-06-30 Matsushita Electric Ind Co Ltd 空気調和装置
JP2002115924A (ja) * 2000-07-31 2002-04-19 Daikin Ind Ltd ヒートポンプ式給湯装置

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JPS6089627A (ja) * 1983-10-21 1985-05-20 Mitsubishi Electric Corp 暖房装置
US4546616A (en) * 1984-02-24 1985-10-15 Carrier Corporation Heat pump charge optimizer
US5611211A (en) * 1994-09-07 1997-03-18 General Electric Company Refirgeration system with electrically controlled refrigerant storage device
JP3475203B2 (ja) * 1996-07-04 2003-12-08 株式会社鷺宮製作所 キャピラリチューブの過熱度制御装置
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JP2000346472A (ja) * 1999-06-08 2000-12-15 Mitsubishi Heavy Ind Ltd 超臨界蒸気圧縮サイクル
JP3990524B2 (ja) * 2000-01-28 2007-10-17 株式会社前川製作所 臨界未満及び超臨界運転共用圧縮冷凍装置

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JPS6162757A (ja) * 1984-08-31 1986-03-31 三菱電機株式会社 暖房装置
JPH0414975U (fr) * 1990-05-25 1992-02-06
WO1999008053A1 (fr) * 1997-08-12 1999-02-18 Zexel Corporation Cycle de refroidissement
JP2000179958A (ja) * 1998-12-16 2000-06-30 Matsushita Electric Ind Co Ltd 空気調和装置
JP2002115924A (ja) * 2000-07-31 2002-04-19 Daikin Ind Ltd ヒートポンプ式給湯装置

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Also Published As

Publication number Publication date
EP1541939A4 (fr) 2008-04-23
AU2003252242A1 (en) 2004-02-09
JP3963134B2 (ja) 2007-08-22
EP1541939A1 (fr) 2005-06-15
JP2004053191A (ja) 2004-02-19

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