WO1988007162A1 - Systeme servant a chauffer et a refroidir des liquides - Google Patents

Systeme servant a chauffer et a refroidir des liquides Download PDF

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Publication number
WO1988007162A1
WO1988007162A1 PCT/US1987/000590 US8700590W WO8807162A1 WO 1988007162 A1 WO1988007162 A1 WO 1988007162A1 US 8700590 W US8700590 W US 8700590W WO 8807162 A1 WO8807162 A1 WO 8807162A1
Authority
WO
WIPO (PCT)
Prior art keywords
passage
refrigerant
liquid
coil
outlet
Prior art date
Application number
PCT/US1987/000590
Other languages
English (en)
Inventor
James B. Martin, Jr.
Original Assignee
Martin James B Jr
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
Priority to US06/787,142 priority Critical patent/US4653287A/en
Application filed by Martin James B Jr filed Critical Martin James B Jr
Publication of WO1988007162A1 publication Critical patent/WO1988007162A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B2313/002—Compression machines, plants or systems with reversible cycle not otherwise provided for geothermal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost

Definitions

  • This invention relates generally to the heating and cooling of liquids / and more particularly, to the improvements in a compression-type refrigeration system for heating and cooling liquids such as water in a swimming pool.
  • the present invention contemplates improvements over the above-disclosed U.S. Patent.
  • One aspect of these improvements includes the elimination of the second or ground liquid source.
  • Another aspect of these improvements comprises liquid and/or refrigerant flow reversal or re- routing to conveniently heat or cool one liquid source.
  • this invention discloses select use of external fluid flow over condenser or evaporator coils to enhance the coefficient of performance.
  • the present invention discloses and claims certain improvements in a system for heating a first liquid source which utilizes a ref igeration compressor, a condenser coil, an evaporator coil, a refrigerant, and means for expansion of the compressed refrigerant, all in their well-known interconnected manner, and which also includes a second liquid source.
  • These improvements may be incorporated separately, or in combination, to provide novel benefits in relation to the situational and/or economic restraints.
  • One such improvement broadly deals with the elimination of the second liquid energy source, which has typically been a ground water well. In areas of the country where ground water is scarce or where there is no other convenient source of heat, this improvements, then, provides liquid source heating or cooling at higher operational efficiencies than previously available.
  • Liquid source heating occurs by extracting heat from the source liquid flow as needed at one point in the refrigerant cycle, then adding substantially greater amounts of heat at another point in the refrigerant cycle. By this means, the liquid source acts as a net resultant heat sink, becoming progressively warmer.
  • Another broad aspect of the present invention is to optionally alter the path of both first and second liquid source flows in segregated heat exchange fashion through the . condenser and evaporator coils. This reversal provides easily controlled and varied heating or cooling of either liquid source.
  • Still another broad aspect of the present inventive improvement is to provide a source of external fluid flow over either condenser or evaporatoi coil to achieve increased efficiency of either heating or cooling of either or both liquid sources. It is therefore an object of this invention to provide improvements in the system for heating and cooling liquids disclosed in U.S. Patent 3,513,663.
  • Figure 1 is a schematic vie * of the first embodiment of the invention.
  • Figure 2 is a section view through arrows 2-2 in Figure 201.
  • Figure 3 is a schematic view of another embodiment of the present invention.
  • Figure 4 is a schematic view of yet another embodiment of the present invention.
  • Figure 5 is a schematic view of still another embodiment of the present invention.
  • Figure 6 is a schematic view of yet another embodiment of the present invention.
  • Figure 7 is a schematic view of still another 0 embodiment of the present invention.
  • Figure 8 is a schematic view of yet another embodiment of the present invention.
  • one embodiment of the improved system is shown generally at 10, and includes a efrigera ion compressor 12, a condenser coil 14, and an evaporator coil 16 in their normal refrigeration cycle relationship. Heated, compressed refrigerant passes out of the compressor 12 into the condenser 14, where it is to be cooled. Thereafter, the refrigerant is passed through means for refrigerant expansion 24 and into the evaporator coil 16, where heat is absorbed during vaporization change of state. This vapor is then suctioned back into the compressor 12, the cycle continuously repeated. Sight glass 26 provides visual indication of adequate refrigerant charge.
  • thermostat control 20, and high/low pressure control switch 22 are interconnected between compressor and a power source (not shown) to regulate operation in a well-known manner.
  • a power source not shown
  • Figure 2 is shown a coaxial coil conduit, preferred and typical of both compressor coil 14 and evaporator coil 16, which preferably are of similar construction and design. Note that any other convenient conduit design for coil and evaporator may be incorporated which allows liquid and refrigerant to flow in a side-by-side heat exchange manner. Refrigerant flows in passage 56 within outer conduit 50 and around inner conduit 54.
  • the first liquid reservoir _42 and pump 44 are eliminated and liquid flowing from evaporator coil 16 discharge conduit 36 is re-routed via transfer conduit 38 also through the condensor coil 14 and back to the second reservoir 30 via return conduit 40.
  • the net result of the arrangement shown in Figure 1 is to heat the liquid in liquid reservoir 30, which may be a swimming pool, hot water storage tank or any other source of liquid which is intended to be heated.
  • liquid reservoir 30 which may be a swimming pool, hot water storage tank or any other source of liquid which is intended to be heated.
  • the vaporizing refrigerant absorbs heat from the liquid, which discharges through conduit 36 at a temperature Y degrees cooler than its inlet temperature X degrees.
  • the liquid then passes through condenser coil 14, during which time it absorbs heat from the just-compressed refrigerant.
  • the liquid discharges from the condenser coil 14 at a temperature approximately 2Y degrees warmer than its condenser inlet temperature, X degrees minus Y degrees.
  • the liquid returning to the second liquid reservoir 30 is therefore at a temperature of X degrees plus Y degrees, or Y degrees warmer than when it was pumped out in the direction of arrow A.
  • This net heating effect may be explained by virtue of the compressor 12 converting electrical power into heat by compression of the refrigerant, the converted source of energy for this system. This energy conversion and absorption is at a considerably higher level of efficiency than either resistive heating elements or fuel combustion. And the need for first liquid reservoir 42, typically ground water, is eliminated in geographic areas where it is unavailable.
  • a portion 38' of the transfer conduit 38 may be routed through any convenient additional heat source, preferably partially embedded in the ground 60 sufficiently deep to be warmer than the liquid discharging from the evaporator coil, X degrees minus Y degrees. Alternately, this section of conduit 38' may be routed through a solar panel for passive heat absorption.
  • the boxed portion 70 remains the same as that previously described, as does the construction of the evaporator coil 16. Likewise, only the second liquid reservoir 30 is utilized. However, in this embodiment the output liquid flow A may be partially or totally diverted in the direction of arrow F through bypass conduit 51 by a 0% to 100% proportional three-way regulating valve 46.
  • the evaporator coil 16 requires a certain amount of heat to prevent "icing", but as the liquid and/or the ambient air temperature rises, the liquid flow requirement decreases to provide that heat.
  • either all, or a portion E of the pump 32 total output flow passes through the evaporator coil 16, or all or a portion F of the total flow bypasses the evaporator coil 16.
  • regulating valve 46 The position of regulating valve 46 is regulated by the sensed pressure within the evaporator coil 16 and associated electrical controls (not shown).
  • Check valve 48 prevents backflow in bypass conduit 51. All liquid flow is returned to the second reservoir 30 via conduit 40. By this means, the heating effect upon the second liquid reservoir 30, flowing through transfer conduit 47 in the direction of arrow G, is maximized by minimizing the degree to which the liquid flow is passed through, and cooled by, the evaporator coil 16.
  • a fan 58 may also, or alternatively to liquid bypass, be provided which forces ambient air over the evaporator coil 16.
  • the operation of this fan 58 is regulated by both an ambient temperature sensor control 62 as well as an electrical signal connection 64 to the refrigerant low pressure sensor within the evaporator coil 16.
  • dual or separate evaporator coil 16 heating may be provided by controlled proportional liquid flow bypass and/or external fluid flow over the evaporator coil 16, which external fluid may be ambient air or, as will be described below, a second, separate external liquid flow.
  • the boxed portion 80 remains the same as in Figure 1, a does the construction of the evaporator coil 16.
  • the flow of the refrigerant through both evaporator and condenser coils 14 and 16 is opposite to that of the liquid flow. This is so to maximize the heat exchange relationship within the coaxial coil conduit best previously shown in Figure 2.
  • the flow of refrigerant and liquid optionally is in the same direction.
  • liquid flow reversal either the liquid flow is reversed, shown by dotted arrows, or the refrigerant flow is reversed, shown by dotted arrows.
  • the liquid flow reversal is accomplished by three-way valve 66 first diverting the flow to three-way valve 72, then into, through, and out of, the evaporator coil 16 via conduit 88 to three-way valve 68, through check valve 74, and into transfer conduit 100.
  • the refrigerant flow reversal is accomplished by three-way valve 76, first diverting the expanding, vaporizing refrigerant through conduit 82 into the opposite end 88 of the evaporator coil 16, and back out to three-way valve 78, where the refrigerant is carried via conduit 98 through check valve 86 into the compressor.
  • Shut-off valve 84 prevents refrigerant from either flowing from conduit 82 directly back into the compressor or flowing from conduit 98 back into the evaporator coil 16 at 88.
  • Either flow reversal is controlled and made intermittent, and is reversed back, when the low pressure sensor within the evaporator coil signals insufficient refrigerant vapor pressure.
  • the condenser cooling fluid may be ambient air and/or another fluid such as water.
  • both liquid reservoir 30 and 42 are intended to be utilized, wherein either reservoir may be either heated or cooled, the temperature of the other reservoir being changed oppositely.
  • the liquid flow from the pumps ' 32 and 44 are made reversible within each coil 14 and 16 simultaneously with refrigerant flow reversal coil to coil.
  • Patent 3,513,663 liquid flow from the first liquid reservoir 42, typically a swimming pool, via pump 44 (shown in solid arrows) is directed through condenser coil 14 and returned to the reservoir 42 somewhat heated, while liquid flow from a second reservoir 30, typically ground water, via pump 32 (shown in solid arrows) is directed through evaporator coil 16 and returned to the second reservoir 30 somewhat cooled while refrigerant routing is as in Figure 1, including the dotted portion.
  • liquid flow from pump 44 is diverted at three-way valves 142 and 144 and thus made to flow oppositely through condenser coil 14 in the direction of the dotted arrows through crossover conduits 146 and 148.
  • liquid flow from pump 32 is diverted at three-way valves 110 and 112, and thus made to flow oppositely through evaporator coil 16 in the direction of the dotted arrows through crossover conduits 114 and 116.
  • refrigerant reversing valve 130 such as that available from
  • the evaporator coil 16 acts as a condenser and the condenser coil 14 acts as an evaporator, heating the second reservoir 30 and cooling first reservoir 42.
  • Bypass check valve 118 and bypass expansion valve 120 facilitates refrigerant flow only in the direction of the dotted arrows, check valve 122 and expansion valve 124 only allowing refrigerant flow in the direction of the solid arrows.
  • Refrigerant return flow to the compressor 12 is through conduit 140, fed by normal refrigerant flow from conduit 138 into valve port 136 and exiting valve port 134, and in reverse mode, fed by conduit 145 into valve portion 132 and exiting valve port 134. Note that the selective heating or cooling is achieved without co-mingling the two liquid reservoirs 30 and 42, a very desirable situation.
  • the overall system 10' is similar to that in Figure 1, except also having a first liquid reservoir 42 in said fluid communication with the condenser coil 14.
  • the point of novelty in this embodiment ⁇ o• is the selective addition of a second external source of liquid for heating the evaporator coil 16 or cooling the condenser coil 14.
  • This external fluid flow may be provided over the coils 14 and 16 by fans 152 and 58 respec ively, forcing air flow shown by the arrows, or by fluid flow discharge from apertured conduits 164 and 166 supplied by pumps 158 and 154 respectively, in fluid communication with reservoirs 160 and 156 respec ively. Return drainage (not shown) to these reservoirs 156 and 160 may also be provided or the fluids may be wasted.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

Les systèmes améliorés décrits, qui servent à chauffer et à refroidir des liquides, comprennent les éléments de la réfrigération, tels qu'un compresseur, un serpentin de condensation, un serpentin d'évaporation, un agent réfrigérant et une soupape d'expansion placés les uns par rapport aux autres dans leur position bien connue et une première et une seconde source de liquide, qui sont pompées en échange thermique à travers les serpentins de condensation et d'évaporation séparés en simultanéité avec l'agent réfrigérant et dans la direction opposée par rapport à ce dernier. Une amélioration générale (10) de la présente invention consiste à éliminer la seconde source de liquide (42), constituée habituellement par un puits d'eau souterraine, et à modifier l'écoulement normal du liquide afin d'obtenir le chauffage ou le refroidissement désirés. Un autre aspect général de la présente invention consiste à modifier éventuellement le trajet des écoulements de la première et de la seconde sources de liquide (30 et 42) en échange thermique séparé à travers les serpentins de condensation et d'évaporation (14 et 16), afin de pouvoir obtenir une sélection et une régulation aisées du chauffage ou du refroidissement de l'une ou de l'autre source de liquide (30 ou 42). L'écoulement de l'agent réfrigérant peut également être modifié.
PCT/US1987/000590 1985-01-28 1987-03-20 Systeme servant a chauffer et a refroidir des liquides WO1988007162A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US06/787,142 US4653287A (en) 1985-01-28 1985-10-15 System for heating and cooling liquids

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US69554185A 1985-01-28 1985-01-28

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WO1988007162A1 true WO1988007162A1 (fr) 1988-09-22

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2327748A (en) * 1997-07-25 1999-02-03 Scottish & Newcastle Plc Cooling apparatus
WO2001002783A1 (fr) * 1999-07-02 2001-01-11 Hongsun Hua Equipement thermodynamique multifonctions
EP1640675A2 (fr) * 2004-09-22 2006-03-29 aqua signal Aktiengesellschaft Dispositif pour la transmission de l'énergie thermique
EP1676080A1 (fr) * 2003-09-18 2006-07-05 Enotion Co., Ltd. Systeme de production d'eau chaude de type pompe a chaleur
CN102721234A (zh) * 2012-05-31 2012-10-10 浙江陆特能源科技有限公司 适用于室内泳池的地源热泵系统
FR2979977A1 (fr) * 2011-09-14 2013-03-15 Zodiac Pool Care Europe Dispositif et procede de chauffage d'une eau de bassin

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3513663A (en) * 1968-05-08 1970-05-26 James B Martin Jr Apparatus for heating and cooling liquids
US3992896A (en) * 1973-08-22 1976-11-23 August Janson Air conditioning system
US4248056A (en) * 1978-05-18 1981-02-03 379235 Ontario Ltd. Heat reclaimer for a heat pump
US4249390A (en) * 1979-08-23 1981-02-10 Jones William M Air conditioning system
US4254630A (en) * 1979-06-01 1981-03-10 Carrier Corporation Heat reclaiming method and apparatus
US4327561A (en) * 1980-06-20 1982-05-04 Mcneal G Russell High coefficient of performance heat pump
US4363218A (en) * 1981-04-10 1982-12-14 Halstead Industries, Inc. Heat pump using solar and outdoor air heat sources
US4479365A (en) * 1983-08-08 1984-10-30 Holmes Alan G Water cooled air conditioning and heating accessory transfer coil kit
US4492091A (en) * 1983-01-20 1985-01-08 Carrier Corporation Apparatus and method for controlling a heat pump water heater

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3513663A (en) * 1968-05-08 1970-05-26 James B Martin Jr Apparatus for heating and cooling liquids
US3992896A (en) * 1973-08-22 1976-11-23 August Janson Air conditioning system
US4248056A (en) * 1978-05-18 1981-02-03 379235 Ontario Ltd. Heat reclaimer for a heat pump
US4254630A (en) * 1979-06-01 1981-03-10 Carrier Corporation Heat reclaiming method and apparatus
US4249390A (en) * 1979-08-23 1981-02-10 Jones William M Air conditioning system
US4327561A (en) * 1980-06-20 1982-05-04 Mcneal G Russell High coefficient of performance heat pump
US4363218A (en) * 1981-04-10 1982-12-14 Halstead Industries, Inc. Heat pump using solar and outdoor air heat sources
US4492091A (en) * 1983-01-20 1985-01-08 Carrier Corporation Apparatus and method for controlling a heat pump water heater
US4479365A (en) * 1983-08-08 1984-10-30 Holmes Alan G Water cooled air conditioning and heating accessory transfer coil kit

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2327748A (en) * 1997-07-25 1999-02-03 Scottish & Newcastle Plc Cooling apparatus
WO2001002783A1 (fr) * 1999-07-02 2001-01-11 Hongsun Hua Equipement thermodynamique multifonctions
JP2003503673A (ja) * 1999-07-02 2003-01-28 ▲ほあ▼宏▲すん▼ 多機能熱設備
EP1676080A1 (fr) * 2003-09-18 2006-07-05 Enotion Co., Ltd. Systeme de production d'eau chaude de type pompe a chaleur
EP1676080A4 (fr) * 2003-09-18 2007-11-28 Enotion Co Ltd Systeme de production d'eau chaude de type pompe a chaleur
EP1640675A2 (fr) * 2004-09-22 2006-03-29 aqua signal Aktiengesellschaft Dispositif pour la transmission de l'énergie thermique
EP1640675A3 (fr) * 2004-09-22 2008-04-23 aqua signal Aktiengesellschaft Dispositif pour la transmission de l'énergie thermique
FR2979977A1 (fr) * 2011-09-14 2013-03-15 Zodiac Pool Care Europe Dispositif et procede de chauffage d'une eau de bassin
WO2013038114A1 (fr) * 2011-09-14 2013-03-21 Zodiac Pool Care Europe Dispositif et procédé de chauffage d'une eau de bassin
CN102721234A (zh) * 2012-05-31 2012-10-10 浙江陆特能源科技有限公司 适用于室内泳池的地源热泵系统

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