EP2009371A1 - Alimentation en eau chaude d'une pompe à chaleur - Google Patents

Alimentation en eau chaude d'une pompe à chaleur Download PDF

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Publication number
EP2009371A1
EP2009371A1 EP07740149A EP07740149A EP2009371A1 EP 2009371 A1 EP2009371 A1 EP 2009371A1 EP 07740149 A EP07740149 A EP 07740149A EP 07740149 A EP07740149 A EP 07740149A EP 2009371 A1 EP2009371 A1 EP 2009371A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
compressor
heat exchanger
muffler
hot water
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.)
Granted
Application number
EP07740149A
Other languages
German (de)
English (en)
Other versions
EP2009371A4 (fr
EP2009371B1 (fr
Inventor
Shinichi Sakamoto
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.)
Daikin Industries Ltd
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Daikin Industries Ltd
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Filing date
Publication date
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Publication of EP2009371A1 publication Critical patent/EP2009371A1/fr
Publication of EP2009371A4 publication Critical patent/EP2009371A4/fr
Application granted granted Critical
Publication of EP2009371B1 publication Critical patent/EP2009371B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/804—Accumulators for refrigerant circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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

Definitions

  • the present invention relates to a refrigerating apparatus that is disposed with a rotary type compressor (including a swing type).
  • Patent Document 1 JP-A No. 2003-247490
  • a refrigerating apparatus comprises a compressor, a first heat exchanger, an expansion mechanism, a second heat exchanger and a muffler.
  • the compressor is a rotary type compressor that compresses a refrigerant.
  • the first heat exchanger causes the refrigerant of a high temperature and a high pressure that has been compressed by the compressor to exchange heat with a first fluid.
  • the expansion mechanism reduces the pressure of the refrigerant that has been condensed inside the first heat exchanger.
  • the second heat exchanger causes the refrigerant whose pressure has been reduced by the expansion mechanism to exchange heat with a second fluid.
  • the muffler is disposed between the second heat exchanger and the compressor and reduces the pulsation of the flow of the refrigerant.
  • an accumulator is disposed on a suction side of a rotary type (including a swing type) compressor.
  • a liquid accumulating mechanism such as an accumulator is disposed, the compressor becomes short of suction gas and the refrigerant becomes uselessly necessary.
  • a muffler that does not include a refrigerant liquid accumulating function is installed instead of an accumulator, whereby it can be ensured that surplus refrigerant does not occur in the refrigerant circuit, and a shortage of suction gas in the compressor can be prevented. Further, the occurrence of noise in the vicinity of the rotary type compressor can be suppressed.
  • a refrigerating apparatus is the refrigerating apparatus according to the first aspect of the present invention, wherein the muffler is disposed on a side of the compressor and is fixed to, so as to become integrated with, a side wall portion of the compressor.
  • the muffler and the compressor are fixed so as to become integrated, whereby the vibration of the compressor can be suppressed. For this reason, the occurrence of noise in the compressor can be suppressed.
  • a refrigerating apparatus is the refrigerating apparatus according to the first or the second aspect of the present invention, wherein the muffler includes a muffler body component and a filter component.
  • the muffler body component is a cylindrical component that has a flow path cross-sectional area that is larger than a flow path cross-sectional area of a gas refrigerant pipe that interconnects the second heat exchanger and the compressor.
  • the filter component is supported inside the muffler body component and traps foreign particles in the refrigerant that flows from the second heat exchanger toward the compressor.
  • the filter component that is disposed inside the muffler body component.
  • the muffler body component in which the filter component is disposed has a flow path cross-sectional area that is larger than the flow path cross-sectional area of the gas refrigerant pipe, so the flow path cross-sectional area of the filter component can be enlarged.
  • a refrigerating apparatus is the refrigerating apparatus according to any of the first to the third aspect of the present invention, wherein the muffler takes in, from a top portion of the muffler, the low pressure gas refrigerant that has flowed out from the second heat exchanger and causes the low pressure gas refrigerant to flow out from a bottom portion of the muffler to the compressor.
  • the muffler is disposed vertically such that the muffler takes in the low pressure gas refrigerant from its top portion and causes the low pressure gas refrigerant to flow out from its bottom portion to the compressor.
  • the muffler has a structure where it is difficult for the liquid refrigerant to accumulate and the muffler can efficiently use the refrigerant that fills the inside of the refrigerant circuit. For this reason, a shortage of suction gas in the compressor can be suppressed, and the used refrigerant can be reduced.
  • a refrigerating apparatus is the refrigerating apparatus according to any of the first to the fourth aspect of the present invention, wherein the refrigerating apparatus further comprises a liquid-gas heat exchanger.
  • the liquid-gas heat exchanger performs heat exchange between the liquid refrigerant that flows out from the first heat exchanger and flows into the expansion mechanism and the gas refrigerant that flows out from the second heat exchanger and flows into the compressor.
  • the refrigerating apparatus is disposed with the liquid-gas heat exchanger, whereby the refrigerant gas that is to be sent to the compressor is placed in a superheated state such that wet compression and liquid compression can be prevented.
  • the supercooling degree of the liquid refrigerant that is to be sent to the evaporator is increased, whereby the occurrence of flash gas in the liquid refrigerant pipe can be prevented.
  • a drop in the capability of the expansion mechanism can be prevented.
  • a refrigerating apparatus is the refrigerating apparatus according to any of the first to the fifth aspect of the present invention, wherein the first fluid is water, and the first heat exchanger is a heat exchanger for hot water supply that heats the water by causing the refrigerant to exchange heat with the water.
  • the heat exchanger for hot water supply is used as the first heat exchanger and heats the water by causing the refrigerant to exchange heat with the water to obtain hot water.
  • the refrigerating apparatus can ensure that surplus refrigerant does not occur in the refrigerant circuit and a shortage of suction gas in the compressor can be prevented. Further, the occurrence of noise in the vicinity of the compressor can be suppressed.
  • a muffler that does not include a refrigerant liquid accumulating function is installed instead of an accumulator, whereby it can be ensured that surplus refrigerant does not occur in the refrigerant circuit and a shortage of suction gas in the compressor can be prevented. Further, the occurrence of noise in the vicinity of the rotary type compressor can be suppressed.
  • the muffler and the compressor are fixed so as to become integrated, whereby the vibration of the compressor can be suppressed. For this reason, the occurrence of noise in the compressor can be suppressed.
  • foreign particles in the refrigerant can be prevented from circulating inside the refrigerant circuit, and damage to the devices or a drop in the capability of the devices can be prevented from being triggered by foreign particles. Further, an increase in pressure loss in the filter component can be suppressed.
  • the muffler has a structure where it is difficult for the liquid refrigerant to accumulate and the muffler can efficiently use the refrigerant that fills the inside of the refrigerant circuit. For this reason, a shortage of suction gas in the compressor can be suppressed, and the used refrigerant can be reduced.
  • the refrigerating apparatus is disposed with the liquid-gas heat exchanger, whereby the refrigerant gas that is to be sent to the compressor is placed in a superheated state such that wet compression and liquid compression can be prevented.
  • the refrigerant gas that is to be sent to the compressor is placed in a superheated state such that wet compression and liquid compression can be prevented.
  • an abnormal rise in the internal pressure of the compressor can be suppressed, and damage to the compressor can be prevented.
  • the supercooling degree of the liquid refrigerant that is to be sent to the evaporator is increased, whereby the occurrence of flash gas in the liquid refrigerant pipe can be prevented.
  • a drop in the capability of the expansion mechanism can be prevented.
  • the refrigerating apparatus can ensure that surplus refrigerant does not occur in the refrigerant circuit and a shortage of suction gas in the compressor can be prevented. Further, the occurrence of noise in the vicinity of the compressor can be suppressed.
  • FIG. 1 is a general configural diagram of the heat pump hot water supplier 1 pertaining to the embodiment of the present invention.
  • the heat pump hot water supplier 1 is an apparatus that heats tap water and supplies hot water to household bathtubs and the like by performing a vapor compression type refrigeration cycle operation using a CO2 refrigerant.
  • the heat pump hot water supplier 1 is mainly disposed with a hot water storage unit 3, which includes a hot water storage tank 31 that stores hot water, and a heat pump unit 2, which includes a refrigerant circuit 20.
  • the hot water storage unit 3 is mainly configured by the hot water storage tank 31, a circulation pump 32 and a three-way valve 39.
  • a water supply opening 33 is disposed in a bottom wall of the hot water storage tank 31, and a hot water exit opening 34 is disposed in a top wall of the hot water storage tank 31.
  • Tap water is supplied from the water supply opening 33 to the hot water storage tank 31, and high temperature hot water that has been stored in the hot water storage tank 31 exits from the hot water exit opening 34 such that the hot water storage tank 31 is capable of supplying the hot water to bathtubs and the like.
  • a flow path 38 for water supply that supplies the tap water is connected to the water supply opening 33.
  • a water intake opening 35 is disposed in the bottom wall of the hot water storage tank 31, and a hot water supply opening 36 is disposed in an upper portion of a side wall (peripheral wall) of the hot water storage tank 31.
  • the water intake opening 35 and the hot water supply opening 36 are connected to a circulation path 6, and the circulation pump 32 and a water heat exchanger 22 of the later-described heat pump unit 2 are connected to the circulation path 6.
  • the circulation pump 32 is connected in the vicinity of the water intake opening 35 in the hot water storage tank 31. Further, the water heat exchanger 22 is connected to a discharge side of the circulation pump 32.
  • the circulation pump 32 causes unheated water inside the hot water storage tank 31 to flow out from the water intake opening 35 to the circulation path 6 and causes the unheated water to flow into a heat exchange path 61 inside the water heat exchanger 22.
  • the unheated water that has flowed into the water heat exchanger 22 is heated in the heat exchange path 61 inside the water heat exchanger 22 and reversely flows back inside the hot water storage tank 31 from the hot water supply opening 36.
  • the three-way valve 39 is disposed on the hot water supply opening 36 side of the inside of the circulation path 6 and is connected to a bypass-use flow path 62 that is connected to a water return opening 37 that is disposed in the bottom wall of the hot water storage tank 31.
  • the three-way valve 39 can perform normal operation, where the hot water does not flow through the bypass-use flow path 62 but rather the water (warm water) that has entered the circulation path 6 from the water intake opening 35 flows through the circulation path 6 and returns to the hot water storage tank 31 from the hot water supply opening 36, and bypass operation, where the water (warm water) that has entered the circulation path 6 from the water intake opening 35 flows through the circulation path 6, passes through the bypass-use flow path 62 via the three-way valve 39, and returns to the hot water storage tank 31 from the water return opening 37.
  • a remaining hot water (50 L) temperature sensor T6 disposed in the peripheral wall of the hot water storage tank 31 at a pitch of 50 L from the top in the vertical direction.
  • a remaining hot water (50 L) temperature sensor T6 disposed in the peripheral wall of the hot water storage tank 31 at a pitch of 50 L from the top in the vertical direction.
  • a remaining hot water (100 L) temperature sensor T7 disposed in the peripheral wall of the hot water storage tank 31 at a pitch of 50 L from the top in the vertical direction
  • a remaining hot water (200 L) temperature sensor T9 disposed in the lowermost portion of the hot water storage tank 31.
  • the remaining hot water (50 L) temperature sensor T6, the remaining hot water (100 L) temperature sensor T7, the remaining hot water (150 L) temperature sensor T8, the remaining hot water (200 L) temperature sensor T9 and the water supply temperature sensor T10 comprise thermistors.
  • the heat pump unit 2 is installed outdoors and includes the refrigerant circuit 20.
  • the refrigerant circuit 20 is mainly configured as a result of a compressor 21, the water heat exchanger 22 that configures the heat exchange path 61, an electrically powered expansion valve 23 that serves as an expansion mechanism, an evaporator 24, a liquid-gas heat exchanger 25 and a muffler 26 being connected in order.
  • the compressor 21 is a compressor whose operating capacity is capable of being varied and, in the present embodiment, is a swing type compressor that is driven by a motor whose rotational speed is controlled by an inverter.
  • a swing type compressor is one type of rotary type compressor. The details of this swing type compressor will be described later.
  • the water heat exchanger 22 is a heat exchanger that functions as a condenser of the refrigerant.
  • the water heat exchanger 22 causes the gas refrigerant of a high temperature and a high pressure that has been compressed in the compressor 21 to exchange heat with unheated water that is delivered from the circulation pump 32 (heats the unheated water), to thereby condense the gas refrigerant.
  • a gas side of the water heat exchanger 22 is connected to a discharge side of the compressor 21, and a liquid side of the water heat exchanger 22 is connected to the electrically powered expansion valve 23.
  • the electrically powered expansion valve 23 is connected to a liquid side of the evaporator 24 and performs adjustment of the pressure and flow rate of the refrigerant that flows inside the evaporator 24.
  • the evaporator 24 is a cross-fin type fin-and-tube heat exchanger that is configured by heat transfer tubes and numerous fins, performs heat exchange with outdoor air, and causes the liquid refrigerant that flows in to evaporate.
  • the liquid-gas heat exchanger 25 is disposed with a liquid refrigerant passage 25a through which passes the liquid refrigerant that has flowed out from the water heat exchanger 22 and a gas refrigerant passage 25b through which passes the gas refrigerant that has flowed out from the evaporator 24, and the liquid-gas heat exchanger 25 causes heat to be exchanged between the liquid refrigerant that has flowed out from the water heat exchanger 22 and the gas refrigerant that has flowed out from the evaporator 24.
  • the liquid refrigerant passage 25a configures part of a liquid refrigerant pipe 28 that couples together the water heat exchanger 22 and the electrically powered expansion valve 23, and the gas refrigerant passage 25b configures part of a gas refrigerant pipe 29 that couples together the evaporator 24 and the compressor 21.
  • the liquid-gas heat exchanger 25 performs heat exchange between the high pressure refrigerant that flows out from the water heat exchanger 22 and flows into the electrically powered expansion valve 23 and the low pressure refrigerant that flows out from the evaporator 24 and flows into the compressor 21, whereby the liquid-gas heat exchanger 25 can impart supercooling to the refrigerant that has flowed out from the water exchanger 22 and can heat the refrigerant that flows into the compressor 21 to bring that refrigerant close to a superheated state. For this reason, the liquid-gas heat exchanger 25 can increase the supercooling degree of the liquid refrigerant that is to be sent to the evaporator 24 and can prevent the occurrence of flash gas in the liquid refrigerant pipe 28. Further, the liquid-gas heat exchanger 25 can prevent wet compression of the compressor 21 and enable stable operation.
  • the heat pump unit 2 includes an outdoor fan 27 that serves as a blowing fan for sucking outdoor air into the inside of the unit and, after heat has been exchanged between the air and the refrigerant in the evaporator 24, discharging the air after heat exchange to the outdoors.
  • This outdoor fan 27 is a fan whose flow rate Wo of the air that is to be supplied to the evaporator 24 is capable of being varied and, in the present embodiment, is configured by an outdoor fan motor 27a that comprises a DC fan motor and a propeller fan 27b that is driven by the outdoor fan motor 27a.
  • the muffler 26 is connected between the liquid-gas heat exchanger 25 and a suction side of the compressor 21 and is a device for reducing the pulsation of the flow of the refrigerant. Further, the muffler 26 prevents the compressor 21 from becoming short of suction gas by ensuring the gas refrigerant that the compressor 21 sucks in and improves the volumetric efficiency of the compressor 21.
  • the configuration of the muffler 26 will be described later.
  • various types of sensors are disposed in the heat pump unit 2. Specifically, a discharge temperature sensor T1 that detects the discharge temperature of the compressor 21, an HPS 40 that serves as a pressure protection switch, an evaporation temperature sensor T2 that detects the temperature of the refrigerant (that is, the refrigerant temperature that corresponds to the evaporation temperature) that flows inside the evaporator 24 and an outdoor air temperature sensor T3 that detects the temperature of the outdoor air that flows into the inside of the unit are disposed in the heat pump unit 2.
  • a discharge temperature sensor T1 that detects the discharge temperature of the compressor 21, an HPS 40 that serves as a pressure protection switch, an evaporation temperature sensor T2 that detects the temperature of the refrigerant (that is, the refrigerant temperature that corresponds to the evaporation temperature) that flows inside the evaporator 24 and an outdoor air temperature sensor T3 that detects the temperature of the outdoor air that flows into the inside of the unit are disposed in the heat pump unit 2.
  • an exiting hot water temperature sensor T4 is disposed on the downstream side of the heat exchange path 61 (specifically, between the water heat exchanger 22 and the three-way valve), and an entering water temperature sensor T5 is disposed on the upstream side of the heat exchange path 61 (specifically, between the circulation pump 32 and the water heat exchanger 22).
  • the discharge temperature sensor T1, the evaporation temperature sensor T2, the outdoor air temperature sensor T3, the exiting hot water temperature sensor T4 and the entering water temperature sensor T5 comprise thermistors.
  • a controller 7 is configured using a microcomputer that includes a CPU, a memory and an input/output interface, for example. Further, as shown in FIG. 2 , the controller 7 is connected such that it can receive the detection signals of the various types of sensors T1 to T10 and 40 and is connected such that it can control the various types of devices and valves 21, 23, 27, 32 and 39 on the basis of these detection signals and the like.
  • FIG. 3 is a plan general diagram of the swing type compressor pertaining to the embodiment of the present invention.
  • This compressor 21 is used as a compressor of a refrigerating apparatus that uses a CO2 refrigerant.
  • This compressor 21 includes a piston 44 where a substantially circular cylinder-shaped roller 42 and a blade 43 that projects outward in the radial direction of the roller 42 are integrally formed.
  • the roller 42 fits together with an eccentric component 45 that is formed integrally with a drive shaft 41.
  • the piston 44 is housed inside a cylinder chamber 48 that is formed in a cylinder 46 and has a substantially circular cross section.
  • a bush fitting hole 47 is formed in the cylinder 46 close to the cylinder chamber 48, and substantially semicircular column-shaped bushes 49 are fitted into the bush fitting hole 47.
  • the flat surfaces of the bushes 49 are caused to face each other, and both side surfaces of the blade 43 of the piston 44 are slidably held between the flat surfaces of the bushes 49.
  • the cylinder chamber 48 is partitioned into two chambers by the piston 44, and the chamber on the right side of the blade 43 in FIG. 3(b) is one where a suction opening 50 opens to the inner peripheral surface of the cylinder chamber 48 to form a suction chamber 51.
  • the chamber on the left side of the blade 43 in FIG. 3(b) is one where an unillustrated discharge opening opens to the inner peripheral surface of the cylinder chamber 48 to form a discharge chamber 52.
  • the muffler 26 is configured by a muffler body 26a and a filter 26b.
  • the muffler body 26a comprises a cylindrical part that has a pipe inner diameter that is larger than a pipe inner diameter of the gas refrigerant pipe 29.
  • an inlet pipe 12 is attached to the top of the muffler body 26a and an outlet pipe 13 is attached to the bottom of the muffler body 26a.
  • the inlet pipe 12 and the outlet pipe 13 are part of the gas refrigerant pipe 29.
  • the hemispherical filter 26b that crosses the inside of the muffler body 26a is attached between the inlet pipe 12 and the outlet pipe 13.
  • the outer shape of the filter 26b when seen from above coincides with the inner diameter of the muffler body 26a. Further, the filter 26b traps foreign particles in the refrigerant that flows from the evaporator 24 side toward the compressor 21 side.
  • the gas refrigerant flows in from the inlet pipe 12 on the top of the muffler 26, foreign particles are removed therefrom as the gas refrigerant passes through the filter 26b, and the gas refrigerant flows in from the outlet pipe 13 on the bottom of the muffler 26 to the suction side of the compressor 21.
  • an attachment bracket 10 that comprises a plate material that is bent in a general sideways U shape when seen from above is fixed to the body upper portion of the compressor 21 body as a result of the intermediate portion of the attachment bracket 10 being welded to the outer peripheral surface of the compressor 21 body. Both end portions of the attachment bracket 10 project from the compressor 21 body and spread in circular arc shapes, with a threaded attachment portion 10a being formed in one end portion thereof and with an engagement hole 10b being formed in the other end portion.
  • a fastening band 11 that comprises a long and narrow plate-shaped metal is wrapped around the muffler body 26a of the muffler 26, with one end portion of the fastening band 11 being engaged with the engagement hole 10b in the attachment bracket 10 and with the other end portion being attached to the threaded attachment portion 10a of the attachment bracket 10 by an attachment screw 14. Additionally, because of the fastening of the attachment screw 14, the fastening band 11 is pulled toward the attachment bracket 10, and the muffler body 26a is fixed to the compressor 21 body in a state where the muffler body 26a is held between the fastening band 11 and the attachment bracket 10. In other words, the muffler 26 is supported so as to become integrated with the compressor 21 body at two positions above and below by this attachment bracket 10 and the outlet pipe 13.
  • the compressor 21 is driven and the circulation pump 32 is driven.
  • the low pressure gas refrigerant that has been sucked into the compressor 21 is compressed and becomes high pressure gas refrigerant.
  • the high pressure gas refrigerant is sent to the water heat exchanger 22, performs heat exchange with unheated water that is supplied by the circulation pump 32, condenses, and becomes high pressure liquid refrigerant.
  • this high pressure liquid refrigerant flows into the liquid-gas heat exchanger 25, performs heat exchange with the gas refrigerant that has been evaporated in the evaporator 24, is cooled, and reaches a supercooled state.
  • the pressure of the high pressure liquid refrigerant that has reached a supercooled state is reduced until it becomes close to the suction pressure of the compressor 21 by the electrically powered expansion valve 23, the refrigerant becomes low pressure refrigerant in a gas-liquid two-phase state, is sent to the evaporator 24, performs heat exchange with outdoor air that is supplied by the outdoor fan 27 in the evaporator 24, evaporates, and becomes low pressure gas refrigerant.
  • the low pressure gas refrigerant flows into the liquid-gas heat exchanger 25, performs heat exchange with the liquid refrigerant that has been condensed in the water heat exchanger 22, is heated, and reaches a superheated state.
  • This low pressure gas refrigerant flows into the muffler 26, and the low pressure gas refrigerant that has flowed into the muffler 26 is again sucked into the compressor 21.
  • the stored water flows out from the water intake opening 35 that is disposed in the bottom portion of the hot water storage tank 31, and this flows through the heat exchange path 61 of the circulation path 6.
  • the unheated water that flows through the heat exchange path 61 of the circulation path 6 is heated (boiled) by the water heat exchanger 22 that functions as a condenser and reversely flows back to the upper portion of the hot water storage tank 31 from the hot water supply opening 36 via the three-way valve 39. Additionally, by continuously performing this operation, high temperature warm water is supplied to the hot water storage tank 31.
  • the controller 7 detects that control signal and switches the three-way valve 39 such that the warm water inside the circulation path circulates through the bypass-use flow path 62. That is, when the boiling temperature is equal to or less than the predetermined temperature, the controller 7 performs bypass operation and causes warm water of a low temperature that is equal to or less than the predetermined temperature to reversely flow back to the hot water storage tank 31 from the water return opening 37 without causing the warm water to reversely flow back to the hot water storage tank 31 from the hot water supply opening 36.
  • the controller 7 When the boiling temperature is a low temperature, water (warm water) of a low temperature reversely flows back toward the lower portion of the hot water storage tank 31, whereby it is ensured that the water (warm water) of a low temperature does not mix with the warm water of a high temperature in the upper portion of the hot water storage tank 31. Then, when this boiling temperature exceeds the predetermined temperature, the controller 7 performs switching of the three-way valve 39 to switch to a normal operating state where the warm water is not caused to circulate through the bypass-use flow path 62. In other words, the warm water that has reached a high temperature is caused to reversely flow back to the hot water storage tank 31 via the hot water supply opening 36 such that the warm water in the upper portion of the hot water storage tank 31 is maintained at a high temperature.
  • controller 7 performs various types of control on the basis of these data. For example, the controller 7 adjusts the opening of the electrically powered expansion valve 23 such that the boiling temperature that has been detected by the exiting hot water temperature sensor T4 is made into a target boiling temperature. Further, when the temperature of the entering water temperature sensor T5 is equal to or greater than a predetermined temperature, the controller 7 determines that the hot water inside the hot water storage tank 31 is boiling and stops operation, and, on the basis of the outdoor air temperature sensor T3, the controller 7 controls the operating frequency of the compressor 21 to adjust its hot water heating capability and the like.
  • the refrigerating apparatus pertaining to the present invention can suppress a shortage of suction gas in a compressor and the occurrence of noise in the vicinity of the compressor and is useful as a refrigerating apparatus and the like that is disposed with a rotary type compressor (including a swing type).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP07740149.5A 2006-03-31 2007-03-28 Alimentation en eau chaude d'une pompe à chaleur Not-in-force EP2009371B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006099382A JP2007271211A (ja) 2006-03-31 2006-03-31 冷凍装置
PCT/JP2007/056711 WO2007114187A1 (fr) 2006-03-31 2007-03-28 Alimentation en eau chaude d'une pompe à chaleur

Publications (3)

Publication Number Publication Date
EP2009371A1 true EP2009371A1 (fr) 2008-12-31
EP2009371A4 EP2009371A4 (fr) 2015-11-18
EP2009371B1 EP2009371B1 (fr) 2018-11-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07740149.5A Not-in-force EP2009371B1 (fr) 2006-03-31 2007-03-28 Alimentation en eau chaude d'une pompe à chaleur

Country Status (3)

Country Link
EP (1) EP2009371B1 (fr)
JP (1) JP2007271211A (fr)
WO (1) WO2007114187A1 (fr)

Cited By (3)

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CN104968942A (zh) * 2013-01-28 2015-10-07 株式会社日立产机系统 油冷式气体压缩机的余热回收系统
US10578339B2 (en) 2013-01-28 2020-03-03 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
US20210095889A1 (en) * 2019-09-30 2021-04-01 Kyungdong Navien Co., Ltd. Filter assembly structure and water heater including the same

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JP2010048466A (ja) * 2008-08-21 2010-03-04 Daikin Ind Ltd 冷凍装置
JP5749475B2 (ja) * 2010-11-16 2015-07-15 三菱電機株式会社 ヒートポンプ式給湯室外機
CN102645021A (zh) * 2011-03-16 2012-08-22 江苏浴普太阳能有限公司 一种热泵热水器压缩机余热回收系统
JP5630421B2 (ja) * 2011-11-04 2014-11-26 三菱電機株式会社 ヒートポンプ式給湯熱源機
JP2018179352A (ja) * 2017-04-07 2018-11-15 パナソニックＩｐマネジメント株式会社 給湯装置、二元温水生成ユニット
JP6841350B2 (ja) 2017-12-26 2021-03-10 三菱電機株式会社 ヒートポンプ給湯室外機

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US6220050B1 (en) * 1998-11-24 2001-04-24 Tecumseh Products Company Suction accumulator
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JP2004293805A (ja) * 2003-03-25 2004-10-21 Daikin Ind Ltd 空気調和装置
JP4254532B2 (ja) * 2003-12-26 2009-04-15 ダイキン工業株式会社 ヒートポンプ式給湯装置

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104968942A (zh) * 2013-01-28 2015-10-07 株式会社日立产机系统 油冷式气体压缩机的余热回收系统
US10041698B2 (en) 2013-01-28 2018-08-07 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
US10578339B2 (en) 2013-01-28 2020-03-03 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
US11300322B2 (en) 2013-01-28 2022-04-12 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
US11821657B2 (en) 2013-01-28 2023-11-21 Hitachi Industrial Equipment Systems Co., Ltd. Waste-heat recovery system in oil-cooled gas compressor
US20210095889A1 (en) * 2019-09-30 2021-04-01 Kyungdong Navien Co., Ltd. Filter assembly structure and water heater including the same
US12050029B2 (en) * 2019-09-30 2024-07-30 Kyungdong Navien Co., Ltd Filter assembly structure and water heater including the same

Also Published As

Publication number Publication date
EP2009371A4 (fr) 2015-11-18
JP2007271211A (ja) 2007-10-18
EP2009371B1 (fr) 2018-11-14
WO2007114187A1 (fr) 2007-10-11

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