WO2010017536A2 - Système de pompe à chaleur - Google Patents

Système de pompe à chaleur Download PDF

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Publication number
WO2010017536A2
WO2010017536A2 PCT/US2009/053236 US2009053236W WO2010017536A2 WO 2010017536 A2 WO2010017536 A2 WO 2010017536A2 US 2009053236 W US2009053236 W US 2009053236W WO 2010017536 A2 WO2010017536 A2 WO 2010017536A2
Authority
WO
WIPO (PCT)
Prior art keywords
heat
chamber
refrigerant
temperature
tube
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.)
Ceased
Application number
PCT/US2009/053236
Other languages
English (en)
Other versions
WO2010017536A4 (fr
WO2010017536A3 (fr
Inventor
David Sooil Koh
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.)
WORLD WIDE SAVE ENERGY Inc
Original Assignee
WORLD WIDE SAVE ENERGY Inc
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 WORLD WIDE SAVE ENERGY Inc filed Critical WORLD WIDE SAVE ENERGY Inc
Priority to US13/058,178 priority Critical patent/US20110138829A1/en
Publication of WO2010017536A2 publication Critical patent/WO2010017536A2/fr
Publication of WO2010017536A3 publication Critical patent/WO2010017536A3/fr
Publication of WO2010017536A4 publication Critical patent/WO2010017536A4/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B21/00—Machines, plants or systems, using electric or magnetic effects
    • F25B21/02—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect
    • F25B21/04—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the present invention relates to a heat pump for and cooling and or heating.
  • Heat pumps have been particularly useful for refrigeration and for air conditioning and heating.
  • the present invention includes a heat exchanger having an improved flow within for greater heat transfer efficiency.
  • the present invention improves efficiency by placing a heat exchanger between an output line and a suction line of a heat pump system.
  • the present invention also may include an electronic suction pressure control which optimizes the suction line temperature, and thereby limits pressure on the suction line.
  • Fig. 1 is a block diagram a refrigeration system embodiment of the present invention.
  • Fig. 2 is a block diagram another embodiment the refrigeration system of the present invention.
  • Fig. 3 is a flow diagram in the nature of a simplified elevation in section of an improved heat
  • Fig. 4 is a flow diagram in the nature of a simplified elevation in section of an improved but less expensive embodiment of a heat exchanger.
  • Fig. 5 is a block diagram another embodiment the refrigeration system which optimizes suction line temperature.
  • Fig. 6 is a block diagram another embodiment the refrigeration system which optimizes suction line temperature.
  • Fig. 7 is an elevation in section of the Peltier thermocouple device shown twice in fig. 6, which optimizes suction line temperature.
  • Fig. 8 is a block diagram of the present invention in heating mode.
  • Fig. 9 is a block diagram of the present invention in air-conditioning mode.
  • Fig 1 illustrates an embodiment of the invention, installed in s system for cooling a refrigeration case, such as in a retail food store.
  • a Heat Exchanger 102 Inserted into a conventional suction line 100 coming from a refrigeration case 100, is a Heat Exchanger 102, of the present invention, which raises the temperature and the vapor ratio in the suction line. This relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid. The less liquid, the less compressor load, and the less power consumption by compressor 106.
  • Compressor 106 outputs through line 108 through three alternative heat absorbers: Hot water tank 110 supplies hot water to the building. In winter, Heat reclaimer 111 heats the building. Any heat not so absorbed is sent to outside condenser 112 for dissipation outdoors.
  • Receiver tank 114 receives the outflow of those heat absorbers 110-112. From receiver tank 114, mostly liquid refrigerant at 75 to 90 degrees F is output at pipe 116 towards the refrigeration case [not shown] to cool the case. But, in the present invention, diverter valve 118 maybe closed to send refrigerant through heat exchanger 102, to be further cooled, and to heat refrigerant that is output through output 104, to make the fluid more vapor and less liquid, to relieve strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
  • valves 119 and 120 may be used with the diverter valve 118, for testing, bypass, and repair purposes. If an operator opens valve 118 to bypass the heat exchanger 102, the operator should close valves 119 & 120; and visa- versa. The system will be more efficient with valve 118 closed, and valves 119 & 120 open.
  • Fig 2 shows a similar arrangement as Fig. 1, but where heat exchanger 102 is mounted in output line 116 towards the refrigeration case, rather than in suction line 100 & 104. But the flow, through valve 119, around closed bypass valve 138, through heat exchanger 102, and through valve 120, also results in a similar flow pattern to Fig. 1. Thus heat transfer between output line 116 and suction line 104 may be similar between figs 1& 2. This again relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
  • Valves 138, 119, 120, 140, and 142 allow heat exchanger 102 to be bypassed.
  • Fig. 3 shows an improved heat exchanger 102 of the present invention.
  • Fluid such as R-22 refrigerant from, in fig. 1, the refrigeration case, flows through inlet 200, Figs 1 & 3, through manifold 202 (fig. 3), through a plurality of distribution holes, such as 205-206.
  • the presently preferred embodiment has from sixteen to twenty such holes 205-206.
  • Fluid flows from the holes through a corresponding number of sealed large-diameter tubes 107-208. As the fluid passes through tubes 207-8 some heat transfers between chamber 210 and the large diameter tubes such as 207-208.
  • Hot compressor output fluid from line 116 enters through inlet 212 into hot liquid filled middle chamber 214, where heat is transferred to large diameter tubes
  • Fluid in tubes 207-208 passes through chamber 230, where more heat is transferred through the tube walls into the tubes 207-8, which then turn 180 degrees back, to flow towards middle chamber 214, through middle chamber 214, transferring more heat from middle chamber 214 to tubes 207-208.
  • the fluid discharges from tubes 207-208 through outlets 247-248 into chamber 210. Fluid then flows through chamber 210, warming tubes 207-208, out through about forty smaller diameter tubes such as 220-222, wherein fluid in chamber 214 heats smaller diameter tubes 220-222 and thereby the fluid in those tubes 220-222, which is next discharged into chamber 230 to heat larger tubes 207-208 and then flow out through outlet 250.
  • This improved heat exchanger has about three times the heat transfer efficiency of a similar sized conventional heat exchanger: wherein in input chamber communicates with through a plurality of tubes, through a middle chamber, to an output chamber, having no designed- in backflow.
  • Fig. 4 is a less expensive but still effective mode of heat exchanger 102 from Fig. 1.
  • Suction line 100-104 is partly replaced by exchanger section 122A of Fig. 4.
  • exchanger section 122A refrigerant flows from compressor 106 through pipe 116 through valve 120 into chamber 300, where manifold 304 splits flow through several copper coils, preferably three coils, of about 30 turns each, shown here as coil 311, and the other two coils shown in part as 312-313.
  • coil 311, and the other two coils shown in part as 312-313 where refrigerant flows through coiled tubes 311-313 and is cooled by fluid in chamber 300. Fluid in chamber 300 is thereby heated so that it leaves chamber 300 as mostly vapor, about 97% vapor, with the refrigerant flowing from line 104 to compressor 106. This again relieves strain on compressor 106, which strain would occur from trying to compress incompressible liquid.
  • this embodiment optimizes the temperature of the fluid in the suction line 104, for maximum efficiency, to maximize vapor without overheating it.
  • optimum temperatures all between 40 and 88 degrees F.
  • Thermostat 400 is set to, above 60 degrees F, close a circuit 401 and open solenoid valve 404, admitting cold 5 degree F gas to mixing chamber 405, and cooling the fluid flowing into suction line 104 to the optimum 60 degrees F, plus about 5 degrees for hysteresis.
  • Thermostat 400 is set to, below 40 degrees F, close a circuit 408 and open solenoid valve 409, admitting hot 131 degree F gas from output line 108 to mixing chamber 405, and heating the fluid in suction line 104 to the optimum 40 degrees F plus about 5 degrees for hysteresis.
  • the fluid lines can be difficult to install, and can be vulnerable.
  • FIG. 6 A presently preferred embodiment of suction temperature control is in Fig. 6.
  • Fig. 7 shows the Peltier heating/cooling device in detail.
  • a self-contained suction vapor heating/cooling block 500 with a thermoelectric Peltier module is wrapped around suction line 104, and a temperature sensor 502, within, is inserted into a hole 503 drilled in suction line 104, to sense the temperature of the refrigerant fluid, such as R-22. Sensor 502 is then soldered 504 into place to seal the hole to keep the R-22 refrigerant within tube 104.
  • Conductors 506-507 conduct the temperature signal to power supply 508 fig. 6, which polarizes and adjusts the current of direct current from power supply 508 across conductors 511-512 to the thermocouple 516 to heat or cool the suction tube 104, as needed to achieve an optimum 40 to 60 degrees F.
  • Heat from or to cooler 516 is conducted across thermal epoxy 518 to heat pipe 520, which is a copper conduit with acetone sealed inside. The acetone evaporates in response to heat and almost instantly transmits the heat
  • a similar or identical self-contained liquid cooling block 502A with a thermoelectric Peltier module is wrapped around expansion valve feed line 545, and a temperature sensor similarly placed within line 545, senses said fluid's temperature.
  • Power supply 508 polarizes and adjusts the current of direct current from power supply 508 across the Peltier device 502A to heat or cool the line 522 as needed to achieve an optimum 60 degrees F, into expansion valve TVX 550.
  • Fig. 8 shows how improved auxiliary heat exchanger 102 results in a dramatic efficiency improvement, in which the building heating system heat pump works at lower ambient temperatures, e.g.: 20° F., than the 35° F of a conventional heat pump, in the heating mode.
  • FIG. 8 shows the present heat pump system, generally designated 690 in its heating mode.
  • the heat pump system 690 comprises an indoor unit 704, and an outdoor unit 706.
  • Indoor unit 704 includes heat exchanger 708, and fan 711 which blows indoor air across heat exchanger 708, to heat or cool an indoor space. In this drawing it is heating.
  • motor 717 driven compressor 106 compresses a refrigerant, such as R-22, to drive the refrigerant towards 4-way- valve 719, which switches the system between heating (shown here) and cooling modes.
  • An out door heat exchanger 720 adds (in this heating mode) or removes heat from the system.
  • Auxiliary heat exchanger 102 is an improved unit as in Fig. 3.
  • Compressor 106 pumps out refrigerant as a high pressure hot gas, at perhaps 140° Fahrenheit through compressor output tube 730 through 4-way valve 19, which is switched in its heating mode to send the refrigerant through tube 732 towards indoor heat exchanger 708.
  • This 140° gas enters indoor heat exchanger 708, where it transfers its heat to the indoor air, which fan 11 blows across heat exchanger 708.
  • Refrigerant exits heat exchanger 708 through tube 734 as high-pressure mid-temperature (perhaps 75 degrees) gas and liquid. These pass through capillary tube 736, which drops their pressure and temperature to about 45 degrees F.
  • temperatures and pressures are approximate, and may vary with time. These temperatures assume an increased efficiency that occurs in this system after the compressor has been running for an interval.
  • Refrigerant is about 45° F as it enters the improved auxiliary heat exchanger 102, at inlet 200 as in Figure 3.
  • the improved heat exchanger 102 tends to more efficiently equalize the temperature, so that the gas exits output 216 at perhaps 35 0 F, and the liquid exits through outlet 250 at about 30 0 F, from whence it flows through tube 779, towards outside heat exchanger 720 .
  • Orifice 774 is a restriction in pipe 779's diameter, which restriction decompresses the liquid refrigerant and drops its pressure and temperature towards R-22's -41 0 F vaporization temperature, as it flows through heat exchanger 720.
  • heated R-22 exits heat exchanger 720 at outlet line 778, at about 15°F.
  • the R-22 flows through 4-way valve 719, which in the heating mode directs it to gas input 212 of auxiliary heat exchanger 102, shown also in Fig. 3, where in middle chamber 214 it flows around tubes 207-208 and 220-222, to cool the liquid in those tubes and absorb heat so that it exits outlet 62 at about 35°F.
  • Gas outlet 216 is the suction line of Fig. 8, leading warm mostly gas to input 104 of compressor 106. If this gas is too hot, it tends to burden the compressor 106. On warmer days, this system might prove too efficient and warm the suction line to a temperature that overpressures the suction line 104, and thus overburdens the compressor.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention porte sur un système de pompe à chaleur classique qui comprend un échangeur de chaleur d'espace, un compresseur (106) entraîné par un moteur (717), un fluide frigorigène, une conduite d'aspiration (104) pour alimenter en fluide frigorigène le compresseur, et un échangeur de chaleur résiduelle (720) pour ajouter ou enlever de la chaleur du système de pompe à chaleur, l'amélioration de ce système utilisant divers dispositifs pour optimiser une température du fluide frigorigène dans la conduite d'aspiration (104), où le fluide frigorigène entre dans le compresseur. Le dispositif préféré est un thermocouple à effet Peltier (500), qui peut être commandé par un courant, en réponse à un capteur (502) dans la conduite d'aspiration, pour chauffer ou refroidir la conduite d'aspiration pour rendre minimale la charge de liquide incompressible ou de pression de gaz élevée sur le compresseur. Un échangeur de chaleur auxiliaire amélioré peut également améliorer le rendement.
PCT/US2009/053236 2008-08-08 2009-08-08 Système de pompe à chaleur Ceased WO2010017536A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/058,178 US20110138829A1 (en) 2008-08-08 2009-08-08 Heat Pump System

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US8746708P 2008-08-08 2008-08-08
US61/087,467 2008-08-08
US10331108P 2008-10-07 2008-10-07
US61/103,311 2008-10-07

Publications (3)

Publication Number Publication Date
WO2010017536A2 true WO2010017536A2 (fr) 2010-02-11
WO2010017536A3 WO2010017536A3 (fr) 2010-04-01
WO2010017536A4 WO2010017536A4 (fr) 2010-05-27

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US (1) US20110138829A1 (fr)
WO (1) WO2010017536A2 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8783052B2 (en) 2010-11-04 2014-07-22 International Business Machines Corporation Coolant-buffered, vapor-compression refrigeration with thermal storage and compressor cycling
US8789385B2 (en) 2010-11-04 2014-07-29 International Business Machines Corporation Thermoelectric-enhanced, vapor-compression refrigeration method facilitating cooling of an electronic component
US8833096B2 (en) 2010-11-04 2014-09-16 International Business Machines Corporation Heat exchange assembly with integrated heater
US8899052B2 (en) 2010-11-04 2014-12-02 International Business Machines Corporation Thermoelectric-enhanced, refrigeration cooling of an electronic component
US8955346B2 (en) 2010-11-04 2015-02-17 International Business Machines Corporation Coolant-buffered, vapor-compression refrigeration apparatus and method with controlled coolant heat load
US9207002B2 (en) 2011-10-12 2015-12-08 International Business Machines Corporation Contaminant separator for a vapor-compression refrigeration apparatus
US9301433B2 (en) 2010-11-04 2016-03-29 International Business Machines Corporation Vapor-compression refrigeration apparatus with backup air-cooled heat sink and auxiliary refrigerant heater

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014097439A1 (fr) * 2012-12-20 2014-06-26 三菱電機株式会社 Dispositif de climatisation
CN103090580B (zh) * 2013-01-31 2015-06-10 南京瑞柯徕姆环保科技有限公司 一种热泵型空调装置
KR101637745B1 (ko) * 2014-11-25 2016-07-07 현대자동차주식회사 열해를 방지하는 에어가이드를 구비한 라디에이터
KR102382161B1 (ko) 2017-12-27 2022-04-01 주식회사 엘지에너지솔루션 이중 직병렬 패스를 이용한 셀 밸런싱 회로

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4065938A (en) * 1976-01-05 1978-01-03 Sun-Econ, Inc. Air-conditioning apparatus with booster heat exchanger
US6321543B1 (en) * 2000-03-15 2001-11-27 Carrier Corporation Method for protecting compressors used in chillers and/or heat pumps
KR100428064B1 (ko) * 2001-07-04 2004-04-28 김강영 냉매 저장용 보조 탱크가 구비된 냉동기/히트펌프 장치

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8783052B2 (en) 2010-11-04 2014-07-22 International Business Machines Corporation Coolant-buffered, vapor-compression refrigeration with thermal storage and compressor cycling
US8789385B2 (en) 2010-11-04 2014-07-29 International Business Machines Corporation Thermoelectric-enhanced, vapor-compression refrigeration method facilitating cooling of an electronic component
US8813515B2 (en) 2010-11-04 2014-08-26 International Business Machines Corporation Thermoelectric-enhanced, vapor-compression refrigeration apparatus facilitating cooling of an electronic component
US8833096B2 (en) 2010-11-04 2014-09-16 International Business Machines Corporation Heat exchange assembly with integrated heater
US8899052B2 (en) 2010-11-04 2014-12-02 International Business Machines Corporation Thermoelectric-enhanced, refrigeration cooling of an electronic component
US8955346B2 (en) 2010-11-04 2015-02-17 International Business Machines Corporation Coolant-buffered, vapor-compression refrigeration apparatus and method with controlled coolant heat load
US9301433B2 (en) 2010-11-04 2016-03-29 International Business Machines Corporation Vapor-compression refrigeration apparatus with backup air-cooled heat sink and auxiliary refrigerant heater
US9207002B2 (en) 2011-10-12 2015-12-08 International Business Machines Corporation Contaminant separator for a vapor-compression refrigeration apparatus
US9470439B2 (en) 2011-10-12 2016-10-18 International Business Machines Corporation Contaminant separator for a vapor-compression refrigeration apparatus

Also Published As

Publication number Publication date
WO2010017536A4 (fr) 2010-05-27
WO2010017536A3 (fr) 2010-04-01
US20110138829A1 (en) 2011-06-16

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