US20110197616A1 - Heat pump apparatus - Google Patents

Heat pump apparatus Download PDF

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Publication number
US20110197616A1
US20110197616A1 US13/124,740 US201013124740A US2011197616A1 US 20110197616 A1 US20110197616 A1 US 20110197616A1 US 201013124740 A US201013124740 A US 201013124740A US 2011197616 A1 US2011197616 A1 US 2011197616A1
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United States
Prior art keywords
refrigerant
sound
container
centrifugal compressor
heat pump
Prior art date
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Abandoned
Application number
US13/124,740
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English (en)
Inventor
Kenichiro Nishii
Kenji Ueda
Kazuki Wajima
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: NISHII, KENICHIRO, UEDA, KENJI, WAJIMA, KAZUKI
Publication of US20110197616A1 publication Critical patent/US20110197616A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine 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
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves

Definitions

  • the present invention relates to a heat pump apparatus and, more specifically, relates to a heat pump apparatus using a centrifugal chiller.
  • centrifugal compressors used in centrifugal chillers are known to enter a state known as surging in which stable operation cannot be carried out when the compressor is operating at a specific level of performance, i.e., with an air volume smaller than a specific value, due to the characteristics of the compressor.
  • surging a state known as surging in which stable operation cannot be carried out when the compressor is operating at a specific level of performance, i.e., with an air volume smaller than a specific value, due to the characteristics of the compressor.
  • the heat pump apparatus is operated in a partial-load state to prevent the occurrence of surging, operation at a condition below the lower limit of the capacity at which surging does not occur at the centrifugal compressor (which is a condition at which surging occurs) can be carried out, the air volume for the lower limit must be ensured at the centrifugal compressor by bypassing part of the refrigerant discharged from the centrifugal compressor directly to the suction side of the centrifugal compressor.
  • the high-temperature, high-pressure refrigerant discharged from the centrifugal compressor flows through a bypass channel into a low-pressure pipe connected to the suction side of the centrifugal compressor or an evaporator. At this time, there is a problem that significant noise is generated.
  • the bypass pipe is directly returned in a T-shape to the suction pipe of the centrifugal compressor.
  • a high-pressure refrigerant flows into a pipe whose internal pressure is low (low-pressure pipe), such as a suction pipe
  • the high-pressure refrigerant suddenly expands. Consequently, there is a problem in that the flow rate of the refrigerant inside the low-pressure pipe increases, and noise generated when the refrigerant strikes the wall of the merging pipe increases.
  • the evaporator is a shell-and-tube type heat exchanger and part of the refrigerant discharged from the centrifugal compressor is directly returned to the evaporator, the noise generated when inflow refrigerant gas strikes the inner surface of the evaporator is lowered since the size of the evaporator is sufficiently large and the flow rate of the refrigerant is sufficiently reduced.
  • the fluid noise of the refrigerant gas resonates in the evaporator, the evaporator itself becomes a noise source. Therefore, the entire evaporator needs to be covered to prevent noise generated in such a manner, and thus, the cost of sound-insulating increases.
  • the present invention has been conceived in light of the problems described above, and an object thereof is to provide a heat pump apparatus that easily prevents noise generated during partial-load operation.
  • the present invention provides the following solutions to achieve the object described above.
  • the heat pump apparatus includes a centrifugal compressor configured to compress a refrigerant; a condenser configured to condense the compressed refrigerant; an expansion valve configured to adiabatically expand the condensed refrigerant; an evaporator configured to vaporize the adiabatically-expanded refrigerant; a container into which the vaporized refrigerant flows and from which the refrigerant that has flowed in flows out to the centrifugal compressor; a sound-insulating member configured to cover the container and prevent sound generated inside the container from leaking outside; a bypass channel configured to guide part of the refrigerant from an area between the centrifugal compressor and the condenser to the container; and a flow control valve configured to control the flow rate of the refrigerant flowing through the bypass channel.
  • the heat pump apparatus when the heat pump apparatus carries out partial-load operation and part of the refrigerant discharged from the centrifugal compressor is guided through the bypass channel to the container, the sound generated when the refrigerant flows into the container can be prevented.
  • the area to be covered with the sound-insulating member can be reduced compared with that of a method covering the entire evaporator with the sound-insulating member, and, thus, sound-insulating can be easily achieved.
  • the sound generated when the bypassed refrigerant merges can be reduced by letting the bypassed refrigerant flow into the container having a cross-sectional area larger than that of the bypass channel.
  • a silencing part configured to prevent the generation of sound due to an inflow refrigerant be provided in an area of the container where the refrigerant flows in from the bypass channel.
  • the silencing part since the silencing part is provided, the noise generated when the bypassed refrigerant flows into the container can be further reduced.
  • An example of the silencing part is a cylindrical member through which the bypassed refrigerant flows, protruding inward from the container, and a plurality of through-holes may be formed in the sidewall of the cylinder.
  • the container have a substantially cylindrical shape with both ends closed, and the cross-sectional diameter of the substantially cylindrical shape be approximately ten times or more larger than the cross-sectional diameter of the bypass channel.
  • the sound generated when the bypassed refrigerant flows into the container can be more reliably prevented from leaking outside.
  • the heat pump apparatus according to the present invention is advantageous in that, since part of the refrigerant discharged from the centrifugal compressor is guided to the container through the bypass channel, noise generated during partial-load operation can be easily prevented.
  • FIG. 1 is a schematic view of the circuit configuration of the heat pump apparatus according to an embodiment of the present invention.
  • FIG. 2 is a front view of the internal arrangement of the heat pump apparatus illustrated in FIG. 1 .
  • FIG. 3 is a right side view of the internal arrangement of the heat pump apparatus illustrated in FIG. 2 .
  • FIG. 4 is a schematic view of a connecting part between a sound-insulating tank and a bypass channel.
  • a heat pump apparatus according to an embodiment of the present invention will be described below with reference to FIGS. 1 to 4 .
  • FIG. 1 is a schematic view of the circuit configuration of the heat pump apparatus according to this embodiment.
  • a heat pump apparatus 1 is a substantially rectangular cuboid and receives heat-source water to supply warm water.
  • the heat pump apparatus 1 is mainly constituted of a condenser 2 , an expansion valve 3 , an evaporator 4 , a sound-insulating tank (container) 5 , a centrifugal compressor 6 , an inverter 7 , a bypass channel 8 , and a flow control valve 9 .
  • FIG. 2 is a front view of the internal arrangement of the heat pump apparatus illustrated in FIG. 1 .
  • FIG. 3 is a right side view of the internal arrangement of the heat pump apparatus illustrated in FIG. 2 .
  • the condenser 2 is a plate-type heat exchanger formed in a substantially rectangular cuboid shape and cools and condenses a high-temperature, high-pressure refrigerant discharged from the centrifugal compressor 6 . That is, the condenser 2 performs heat exchange between the refrigerant and warm water, liquefies the refrigerant, and heats the warm water.
  • One of the ends of the condenser 2 is connected to a discharge part of the centrifugal compressor 6 via an oil-mist separating tank 12 in such a manner that the refrigerant can flow therefrom, and the other end is connected to the expansion valve 3 via an economizer 10 in such a manner that the refrigerant can flow thereto.
  • the condenser 2 is disposed in parallel with the evaporator 4 .
  • a warm-water inlet 21 into which warm water flows before being heated by the condenser 2 is provided in the bottom area, and a warm-water outlet 22 from which warm water flows out after being heated by the condenser 2 is provided in the top area.
  • the economizer 10 is a heat exchanger that is formed in a substantially cylindrical shape and further cools the refrigerant that has flowed out from the condenser 2 .
  • One of the ends of the economizer 10 is connected to the condenser 2 in such a manner that the refrigerant can flow therefrom, and the other end is connected to the expansion valve 3 in such a manner that the refrigerant can flow thereto.
  • This embodiment will be described as applied to an example in which heat exchange is performed at the economizer 10 between a low-temperature, low-pressure refrigerant acquired by adiabatically expanding part of the refrigerant that has flowed from the condenser 2 and a refrigerant supplied to the expansion valve 3 .
  • the refrigerant used for cooling the expansion valve 3 flows into the centrifugal compressor 6 .
  • the configuration of the economizer 10 is not particularly limited, and a known configuration thereof may be employed.
  • the expansion valve 3 adiabatically expands the refrigerant supplied to the condenser 2 via the economizer 10 and reduces the pressure of the refrigerant.
  • One of the ends of the expansion valve 3 is connected to the economizer 10 in such a manner that the refrigerant can flow therefrom, and the other end is connected to the evaporator 4 in such a manner that the refrigerant can flow thereto.
  • the expansion valve 3 is not particularly limited, and any known one may be used.
  • the evaporator 4 is a plate-type heat exchanger that is formed in a substantially rectangular cuboid shape and evaporates the refrigerant adiabatically expanded by the expansion valve 3 . That is, the evaporator 4 applies heat from the heat-source water to the refrigerant and vaporizes the refrigerant by performing heat exchange between the refrigerant and the heat-source water.
  • One of the ends of the evaporator 4 is connected to the expansion valve 3 in such a manner that the refrigerant can flow therefrom, and the other end is connected to a suction part of the centrifugal compressor 6 via a sound-insulating tank 5 .
  • a heat-source-water inlet 41 in to which heat-source water flows before heat is absorbed therefrom by the evaporator 4 is provided in the top area
  • a heat-source-water outlet 42 from which heat-source water flows out after heat is absorbed therefrom by the evaporator 4 is provided in the bottom area.
  • a control panel 11 has a collection of operating devices, etc. for controlling various types of equipment in the heat pump apparatus 1 and has a substantially rectangular cuboid case that accommodates the operating devices, etc.
  • the sound-insulating tank 5 is a container formed in a substantially cylindrical shape that receives the refrigerant from the bypass channel 8 and prevents sound generated when the refrigerant flows in from the bypass channel 8 from leaking outside. Furthermore, the sound-insulating tank 5 receives the refrigerant from the evaporator 4 and functions as an accumulator that sends gas refrigerant to the centrifugal compressor 6 .
  • a sound-insulating member 51 which is made of a sound absorbent material, is disposed around the sound-insulating tank 5 .
  • the sound absorbent material, constituting the sound-insulating member 51 is not particularly limited, and any known sound absorbent material may be used.
  • One of the ends of the sound-insulating tank 5 is connected to the evaporator 4 in such a manner that the refrigerant can flow therefrom, and the other end is connected to the centrifugal compressor 6 in such a manner that the refrigerant can flow thereto. Furthermore, the sound-insulating tank 5 is connected to an end of the bypass channel 8 in such a manner that the refrigerant can flow.
  • the sound-insulating tank 5 is not particularly limited, and any known one may be used.
  • the centrifugal compressor 6 takes in the refrigerant vaporized at the evaporator 4 through the sound-insulating tank 5 and discharges the refrigerant, after compression, to the condenser 2 through the oil-mist separating tank 12 .
  • the suction part of the centrifugal compressor 6 to which the refrigerant flows in is connected to the evaporator 4 via the sound-insulating tank 5
  • the discharge part from which the refrigerant flows out is connected to the condenser 2 via the oil-mist separating tank 12 .
  • the centrifugal compressor 6 is integrated with an electric motor 61 that supplies a rotational driving force and a suction vane 62 that controls the amount of air intake.
  • the electric motor 61 is rotationally driven by electrical power supplied from the inverter 7 such that the rotational speed is controlled.
  • the suction vane 62 is mounted on a compressor intake part to increase or decrease the amount of refrigerant gas taken in by the compressor by changing the degree of opening.
  • the centrifugal compressor 6 , the electric motor 61 , and the suction vane 62 are not particularly limited, and any known ones may be used.
  • the inverter 7 supplies electrical power to the electric motor 61 , and also controls the rotational speed of the electric motor 61 , and has a case that is substantially rectangular cuboid.
  • the inverter 7 is not particularly limited, and any known one may be used.
  • the oil-mist separating tank 12 formed in a substantially cylindrical shape separates lubricants contained in the refrigerant discharged from the centrifugal compressor 6 and lubricant mist from the refrigerant.
  • One of the ends of the oil-mist separating tank 12 is connected to the discharge part of the centrifugal compressor 6 in such a manner that the refrigerant can flow therefrom, and the other end is connected to the condenser 2 .
  • the oil-mist separating tank 12 supplies the lubricant separated from the refrigerant to an oil tank 13 .
  • the oil-mist separating tank 12 is not particularly limited, and any known one may be used.
  • the oil tank 13 formed in a substantially cylindrical shape retains the lubricant used for lubricating the centrifugal compressor 6 , and also supplies the lubricant to the centrifugal compressor 6 , and receives the lubricant discharged from the centrifugal compressor 6 .
  • the oil tank 13 is connected to the centrifugal compressor 6 such that the lubricant can be supplied to and received from the centrifugal compressor 6 and such that the lubricant is supplied from the oil-mist separating tank 12 .
  • the bypass channel 8 is a channel that directly sends part of the refrigerant discharged from the centrifugal compressor 6 to the sound-insulating tank 5 during partial-load operation of the heat pump apparatus 1 . It is desirable that the cross-sectional diameter of the bypass channel 8 be at least ten times larger than that of the cross-sectional diameter of the sound-insulating tank 5 .
  • one of the ends of the bypass channel 8 is connected to the channel connecting the oil-mist separating tank 12 and the condenser 2 , and the other end is connected to the sound-insulating tank 5 .
  • a silencing part 81 shaped such that the bypass channel 8 protrudes inward from the sound-insulating tank 5 is provided in the area where the bypass channel 8 is connected to the sound-insulating tank 5 .
  • FIG. 4 is a schematic view of the connecting part between the sound-insulating tank 5 and the bypass channel 8 .
  • the silencing part 81 is a cylindrical member extending inward from the inner surface of the sound-insulating tank 5 and suppresses sound generated when the refrigerant flows into the sound-insulating tank 5 from the bypass channel 8 .
  • a plurality of through-holes 82 is formed in the side surface of the silencing part 81 .
  • the flow control valve 9 is a valve that controls the flow of the refrigerant in the bypass channel 8 .
  • the flow control valve 9 is closed. In contrast, during partial-load operation of the heat pump apparatus 1 , the flow control valve 9 is open, and part of the refrigerant discharged from the centrifugal compressor 6 is guided through the bypass channel 8 to the sound-insulating tank 5 .
  • the high-temperature, high-pressure gas refrigerant compressed by the centrifugal compressor 6 is discharged from the discharge part of the centrifugal compressor 6 and flows into the oil-mist separating tank 12 .
  • lubricant mist contained in the refrigerant is separated from the refrigerant.
  • the lubricant mist separated from the refrigerant flows out from the oil-mist separating tank 12 into the condenser 2 .
  • heat exchange is performed between the high-temperature refrigerant and warm water supplied from an external unit.
  • the high-temperature refrigerant is condensed and liquefied by releasing heat to the warm water.
  • the warm water absorbs heat from the high-temperature refrigerant, is subjected to a temperature rise, and flows out from the condenser 2 into an external unit.
  • the refrigerant liquefied at the condenser 2 flows out from the condenser 2 into the economizer 10 .
  • Part of the inflow refrigerant branches off at the economizer 10 , and a low-temperature, low-pressure refrigerant is generated through adiabatic expansion.
  • heat exchange is performed between the branched-off low-temperature refrigerant and the remaining refrigerant to further cool the remaining refrigerant.
  • the branched-off refrigerant is used to cool the remaining refrigerant, it flows into the suction part of the centrifugal compressor 6 .
  • the refrigerant cooled by the economizer 10 flows to the expansion valve 3 and is adiabatically expanded to a low-temperature, low-pressure liquid refrigerant while passing through the expansion valve 3 .
  • the adiabatically-expanded refrigerant flows into the evaporator 4 .
  • heat exchange is performed between the low-temperature refrigerant and heat-source water supplied from an external unit.
  • the low-temperature refrigerant is vaporized to gas by absorbing heat from the heat-source water.
  • the heat-source water becomes heat-source water with a reduced temperature by releasing heat to the low-temperature refrigerant and flows out from the evaporator 4 .
  • the vaporized gas refrigerant flows out from the evaporator 4 into the sound-insulating tank 5 .
  • the liquid refrigerant that has flowed out from the evaporator 4 together with the gas refrigerant is separated from the gas refrigerant, and only the gas refrigerant flows out from the sound-insulating tank 5 .
  • the gas refrigerant from which the liquid refrigerant has been separated at the sound-insulating tank 5 flows into the suction part of the centrifugal compressor 6 , is compressed at the centrifugal compressor 6 , and is discharged from the discharge part of the centrifugal compressor 6 again as a high-pressure refrigerant, and the cycle described above is repeated.
  • the rotational speed of the electric motor 61 is reduced by the inverter 7 , and the airflow capacity of the centrifugal compressor 6 is reduced by closing the suction vane 62 .
  • the airflow capacity of the centrifugal compressor 6 is reduced in such a manner that the operational point associated with the centrifugal compressor 6 does not enter the surging region.
  • the closed flow control valve 9 opens. As a result, part of the refrigerant that has been discharged from the centrifugal compressor 6 and that has flown into the condenser 2 through the oil-mist separating tank 12 flows into the bypass channel 8 .
  • the refrigerant that flowed into the bypass channel 8 flows into the sound-insulating tank 5 and merges with the refrigerant from the evaporator 4 .
  • the flow rate of the refrigerant flowing into the condenser 2 and the evaporator 4 is reduced even more to reduce the load associated with the heat pump apparatus 1 even more.
  • partial-load operation of the heat pump apparatus 1 is carried out, and part of the refrigerant discharged from the centrifugal compressor 6 is guided through the bypass channel 8 to the sound-insulating tank 5 covered with the sound-insulating member 51 so as to easily prevent sound that is generated when the bypassed refrigerant flows into the sound-insulating tank 5 from leaking outside.
  • the area that needs to be covered by the sound-insulating member 51 is small compared with that of a method of covering the entire evaporator with the sound-insulating member 51 . Therefore, sound can be easily prevented.
  • the silencing part 81 is disposed in the area where the bypassed refrigerant flows into the sound-insulating tank 5 , the noise generated when the bypassed refrigerant flows into the sound-insulating tank 5 can be reduced even more.
  • the cross-sectional diameter of the sound-insulating tank 5 is at least ten times larger than that of the bypass channel 8 , sound generated when the bypassed refrigerant flows into the sound-insulating tank 5 can be even more reliably prevented from leaking outside.
US13/124,740 2009-03-30 2010-03-29 Heat pump apparatus Abandoned US20110197616A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2009083368A JP5582713B2 (ja) 2009-03-30 2009-03-30 ヒートポンプ装置
JP2009-083368 2009-03-30
PCT/JP2010/055543 WO2010113858A1 (ja) 2009-03-30 2010-03-29 ヒートポンプ装置

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US20110197616A1 true US20110197616A1 (en) 2011-08-18

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US13/124,740 Abandoned US20110197616A1 (en) 2009-03-30 2010-03-29 Heat pump apparatus

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US (1) US20110197616A1 (ja)
EP (1) EP2416094A4 (ja)
JP (1) JP5582713B2 (ja)
UA (1) UA103204C2 (ja)
WO (1) WO2010113858A1 (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9239183B2 (en) 2012-05-03 2016-01-19 Carrier Corporation Method for reducing transient defrost noise on an outdoor split system heat pump
EP3382301A1 (de) * 2017-03-31 2018-10-03 BSH Hausgeräte GmbH Haushaltsgerät und verfahren zum schwingungs- und/oder geräuschreduzierten betreiben eines haushaltgerätes
US10443912B2 (en) 2013-10-25 2019-10-15 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and acid suppression method
US10465959B2 (en) 2013-10-25 2019-11-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and method for suppressing isomerization

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1966620A (en) * 1932-11-26 1934-07-17 Fluor Corp Muffler
US4557115A (en) * 1983-05-25 1985-12-10 Mitsubishi Denki Kabushiki Kaisha Heat pump having improved compressor lubrication
JPH09133434A (ja) * 1995-11-09 1997-05-20 Matsushita Electric Ind Co Ltd パルス式電子膨張弁冷媒回路
US5906225A (en) * 1997-09-10 1999-05-25 General Motors Corporation Orifice tube type refrigerant expansion valve assembly with combined particulate and noise attenuation filters
US20020035844A1 (en) * 2000-09-28 2002-03-28 Lee In Seop Suction muffler for compressor
US6427464B1 (en) * 1999-01-15 2002-08-06 York International Corporation Hot gas bypass control for centrifugal chillers
US20060150668A1 (en) * 2005-01-10 2006-07-13 Samsung Electronics Co., Ltd. Refrigerating apparatus with turbo compressor
US20080314036A1 (en) * 2007-06-20 2008-12-25 Denso Corporation Exhaust gas cleaning apparatus for lean burn internal combustion engine
US20100011791A1 (en) * 2006-12-23 2010-01-21 Roger Nicholas Strickland R422d heat transfer systems and r22 systems retrofitted with r422d

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5783367U (ja) * 1980-11-12 1982-05-22
JPH0440130Y2 (ja) * 1985-07-29 1992-09-21
JPH01285760A (ja) * 1988-05-13 1989-11-16 Hitachi Ltd 密閉形庄縮機用アキュムレータ
JPH05133566A (ja) * 1991-11-14 1993-05-28 Matsushita Electric Ind Co Ltd 空気調和機の室外ユニツト
JP3408309B2 (ja) * 1994-02-10 2003-05-19 株式会社東芝 密閉形コンプレッサならびにこのコンプレッサを用いた冷凍装置
AU706566B2 (en) * 1996-03-01 1999-06-17 Murray James Kite Emission control and/or silencer and/or separator and/or mixing apparatus
JP2002090004A (ja) * 2000-09-20 2002-03-27 Fujitsu General Ltd アキュムレータ
JP2003222412A (ja) * 2002-01-29 2003-08-08 Daikin Ind Ltd 冷凍装置
JP2004177015A (ja) * 2002-11-27 2004-06-24 Fujitsu General Ltd 冷凍サイクルの膨張弁装置
JP2006284034A (ja) 2005-03-31 2006-10-19 Mitsubishi Heavy Ind Ltd 空気調和装置およびその膨張弁制御方法
JP4859480B2 (ja) * 2006-02-21 2012-01-25 三菱重工業株式会社 ターボ冷凍機およびその制御装置ならびにターボ冷凍機の制御方法

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1966620A (en) * 1932-11-26 1934-07-17 Fluor Corp Muffler
US4557115A (en) * 1983-05-25 1985-12-10 Mitsubishi Denki Kabushiki Kaisha Heat pump having improved compressor lubrication
JPH09133434A (ja) * 1995-11-09 1997-05-20 Matsushita Electric Ind Co Ltd パルス式電子膨張弁冷媒回路
US5906225A (en) * 1997-09-10 1999-05-25 General Motors Corporation Orifice tube type refrigerant expansion valve assembly with combined particulate and noise attenuation filters
US6427464B1 (en) * 1999-01-15 2002-08-06 York International Corporation Hot gas bypass control for centrifugal chillers
US20020035844A1 (en) * 2000-09-28 2002-03-28 Lee In Seop Suction muffler for compressor
US20060150668A1 (en) * 2005-01-10 2006-07-13 Samsung Electronics Co., Ltd. Refrigerating apparatus with turbo compressor
US20100011791A1 (en) * 2006-12-23 2010-01-21 Roger Nicholas Strickland R422d heat transfer systems and r22 systems retrofitted with r422d
US20080314036A1 (en) * 2007-06-20 2008-12-25 Denso Corporation Exhaust gas cleaning apparatus for lean burn internal combustion engine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9239183B2 (en) 2012-05-03 2016-01-19 Carrier Corporation Method for reducing transient defrost noise on an outdoor split system heat pump
US10443912B2 (en) 2013-10-25 2019-10-15 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and acid suppression method
US10465959B2 (en) 2013-10-25 2019-11-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Refrigerant circulation device, method for circulating refrigerant and method for suppressing isomerization
EP3382301A1 (de) * 2017-03-31 2018-10-03 BSH Hausgeräte GmbH Haushaltsgerät und verfahren zum schwingungs- und/oder geräuschreduzierten betreiben eines haushaltgerätes

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EP2416094A4 (en) 2012-09-05
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JP2010236726A (ja) 2010-10-21
UA103204C2 (en) 2013-09-25
WO2010113858A1 (ja) 2010-10-07

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