WO2006036121A1 - Echangeur thermique - Google Patents

Echangeur thermique Download PDF

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Publication number
WO2006036121A1
WO2006036121A1 PCT/SE2005/001442 SE2005001442W WO2006036121A1 WO 2006036121 A1 WO2006036121 A1 WO 2006036121A1 SE 2005001442 W SE2005001442 W SE 2005001442W WO 2006036121 A1 WO2006036121 A1 WO 2006036121A1
Authority
WO
WIPO (PCT)
Prior art keywords
coil
water
container
hot fluid
heat exchanger
Prior art date
Application number
PCT/SE2005/001442
Other languages
English (en)
Inventor
Adam Fjaestad
Christer Persson
Kåre CARLSSON
Lars Ivarsson
Leif Olsson
Robert Nord
Original Assignee
Thermia Värme Ab
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 Thermia Värme Ab filed Critical Thermia Värme Ab
Priority to EP05788736A priority Critical patent/EP1794532A1/fr
Publication of WO2006036121A1 publication Critical patent/WO2006036121A1/fr
Priority to NO20071639A priority patent/NO20071639L/no

Links

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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply
    • F24D3/082—Hot water storage tanks specially adapted therefor
    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F24H1/186—Water-storage heaters using fluid fuel
    • 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
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/18—Water-storage heaters
    • F24H1/20—Water-storage heaters with immersed heating elements, e.g. electric elements or furnace tubes
    • F24H1/208—Water-storage heaters with immersed heating elements, e.g. electric elements or furnace tubes with tubes filled with heat transfer fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0132—Auxiliary supports for elements for tubes or tube-assemblies formed by slats, tie-rods, articulated or expandable rods

Definitions

  • the present invention relates to heating systems, and in particular to a system including a heat exchanger apparatus for heating water according to the preamble of claim 1 and 5, respectively.
  • the present invention also relates to a coil support device according to the preamble of claim 13 and a heat exchanger device comprising a coil support device according to the preamble of claim 20.
  • These heating systems may consist of, e.g. oilfired boilers, bioenergy boilers, which e.g. are intended for firing with chips or pellets, and heat pumps.
  • the heating systems often comprise a water heater, which, in principle, consists of a water container in which hot water is heated and stored to enable a momentary consumption of water that is larger than what the heating system momentarily can produce.
  • the hot water may be heated during the night to enable a large hot water consumption during the day.
  • the water in the water heater may, in principle, be heated to an arbitrary temperature, ⁇ which enables consumption of a large number of litres- of ready-mixed hot water when the water heater is fully heated.
  • heat pumps on the other hand, water heating is performed more often.
  • heating of the hot water in the water heater, the so called secondary water or hot water is performed by the so called primary water, heated by the heat pump loop.
  • the available water heating temperature is limited by the temperature to which the heat pump is capable of heating the primary water, there is a limitation in the temperature to which the secondary water may be heated.
  • the water heating method often used today involves use of a double-walled water container, wherein the clean water is contained in the inner container, and is heated by hot water in the double-wall through the container wall.
  • a problem when using this kind of water heating is that heat pumps with high output power, e.g. more than 6 kW, tends to, during heating of hot water, and in particular during summer operation, turn off and on a number of times during heating, charging, of the hot water, which results in poor usage of the heat pump.
  • the object of the present invention is to provide a system for heating water that solves the above mentioned problem.
  • the heat exchanger arrangement includes a water container having an inlet for supplying water to be heated and an outlet for discharging heated water.
  • the heat exchanger arrangement further includes means for carrying a hot fluid through said container, wherein heat from the hot fluid is emitted to the water in the container when hot fluid passages through the means, wherein the system further comprises means for heating the hot fluid using a heat pump, wherein the hot fluid is circulated through the container using a circulation pump, and wherein the system comprises means for controlling the circulation pump continuously or in relation to predetermined start and stop conditions.
  • the circulation pump may be controlled such that the circulation pump is turned on at a first predetermined cooling medium condensation pressure, and turned off at a second predetermined cooling medium condensation pressure, which is lower than said first cooling medium condensation pressure.
  • the circulation pump may be controlled such that the cooling medium condensation pressure is kept at a predetermined cooling medium condensation pressure.
  • Controlling the circulation pump towards a certain working point may allow a higher temperature in the water container, which in turn has as result that a consumer of large amounts of water may achieve a larger amount of ready-mixed hot water (ready-mixed hot water means the total volume of the hot water in the container and the volume of the cold water that the hot water is mixed together with) but at a higher cost due to lower efficiency.
  • ready-mixed hot water means the total volume of the hot water in the container and the volume of the cold water that the hot water is mixed together with
  • Said means for carrying hot fluid through said water container may consist of a tubular coil arranged in said water container, wherein said tubular coil includes an inlet for receiving hot fluid and an outlet for discharging said hot fluid after passage through the coil, wherein the coil is made from a material admitting heat from the hot fluid to be emitted to water in the container when passaging through the coil.
  • the outlet of the coil may be arranged in the lower end of the tubular coil.
  • the tubular coil solution has the advantage that a considerably higher hot water velocity may be achieved as compared to what is possible when using the double-wall solution, which further increases heat transfer. Even further, the solution according to the present invention allows that the heat transferring surface may be positioned more freely than when using a double-wall, which has the advantage that a larger temperature gradient may be achieved in the container.
  • the pitch of the tubular coil may be evenly distributed over its length, or, alternatively, the pitch of the tubular coil may vary over its length.
  • the pitch may be lower in the top and bottom as compared to the pitch in the middle of the coil. This has the advantage that the water transferring surface may be adapted to achieve a best possible temperature stratification in the container.
  • the heat exchanger arrangement may further comprise a double- wall, which may be used as an accumulator container, e.g. for defrosting water.
  • a double- wall which may be used as an accumulator container, e.g. for defrosting water.
  • the heat exchanger arrangement may further be provided with a coil support device for keeping the tubular coil in position.
  • the tubular coil may be assembled in the container in a manufacturing plant and then transported to an installation location without having to risk the coil collapsing and becoming damaged, which otherwise could be the case, e.g. if the tubular coil is made from copper.
  • a further advantage is that the tubular coil may easily be positioned in an optimal way in the container, both regarding the position relative to the container wall and the positioning of the individual turns of the coil.
  • a heat pump 10 installed in a real estate such as a private house.
  • the heat pump is provided with a control computer 12, which controls and monitors various functions in the heat pump. Such functions may be, e.g. setting and/or monitoring operating temperatures of the heat pump compressor, indoor and outdoor temperatures, heating function settings, room temperature control depending on time- of-day or holiday absence etc.
  • a user may communicate with the control computer 12 via a display 29 and keypad 29 arranged on the heat pump.
  • the heat pump 10 further comprises a heat pump circuit 20 and a water container 11 having an inlet 13 in the bottom part of the container for supplying water to be heated and an outlet 14 in the upper part of the container for discharging heated water.
  • the heat pump circuit 20 comprises a circulating cooling medium, refrigerant, wherein liquid cooling medium absorbs heat from a heat source such as heat loop in rock 22, having a temperature of about -5° - +5° and is evaporated in an evaporator.
  • the evaporation temperature may be, e.g. -3°.
  • the gaseous cooling medium is then compressed using a compressor 23 to a higher pressure, which, due to the smaller volume of the gas, results in an increased gas temperature.
  • the compressed, hot gas then delivers its heat via a condenser 24 and sub-cooler 25 to the so called primary water, or radiator water 26.
  • the sub-cooler has as result that more heat may be extracted, which consequently yields a more economic heat pump.
  • the pressure of the, at this stage liquid, cooling medium is then considerably lowered in an expansion valve 27, whereupon the temperature of the cooling medium is rapidly lowered, whereupon the cooling medium again absorbs heat from the heat loop 22.
  • the heat loop may also absorb heat from earth, air and/or water.
  • the primary water is then alternately used for heating hot water or the estates radiator and/or underfloor heating system.
  • the efficiency of the heat pump is controlled by the temperature of the cooling medium when it reaches the condenser. The lower the temperature, i.e. the lower the pressure, the higher efficiency.
  • the coefficient of performance, COP, of the heat pump i.e. the ratio of delivered power and supplied power, may be 4,4; at 50° it may be 3,3 and at 60° it may be 2,7.
  • the heat pump can not heat the primary water to an arbitrary high temperature, which leads to restrictions in the temperature to which the secondary water, hot water, may be heated by the primary water.
  • FIG. 1 In fig. 1 is shown the method for heating the secondary water that is commonly used today.
  • the water container 11 is double- walled with an outer wall 15 surrounding the container 11.
  • the primary water is, by means of a valve, alternately circulated through the estate's heating system (not shown) and the volume 16 between the container 11 and the wall 15.
  • the hot primary water passes through the volume 16, the water in the container 11 is heated through the container wall surface 17.
  • the primary water reaches the bottom of the double-wall it is led by means of outlet 18 back towards the heat pump portion for reheating.
  • a heat exchanger arrangement according to the present invention, which allows a larger heat transfer to the water in the container and also larger hot water consumption.
  • a tubular coil 31 extending substantially through the entire portion of the water container 30 that is filled with water, is arranged in the water container 30.
  • the primary water, heated by the heat pump portion is let into the tubular coil from above and circulates through the coil, which is ended by an outlet in the container bottom, after which the primary water is re- circulated to the heat pump portion for reheating prior to circulating the coil again.
  • the tubular coil has the advantage that, as compared to the container wall, a considerably larger heat transfer surface is obtained, which results in transfer of a larger amount of energy during passage through the coil.
  • the coil is shown as having an essentially square section, this section, however, may, of course, also be circular, triangular or of any other polygon shape.
  • the tubular coil and the water container are coaxially aligned in this example.
  • the coil extends through all or substantially all of the water carrying portion of the container, a greater temperature gradient as compared to the double-wall solution is achieved. I.e., even if the total energy contained in the container is the same, the temperature difference between the top and bottom will be greater using the tubular coil, which results in a higher temperature in the upper part as compared to using a double-wall.
  • each additional degree of higher temperature in the hot water is important since this means that a larger amount of ready-mixed water with a temperature suitable for consumption can be obtained.
  • the present invention thus facilitates the often present regulations regarding how much hot water a water heater must be able to deliver during a continuous discharge, and then again at a new discharge after a certain amount of time, e.g. one hour.
  • a top temperature 5° higher than when using a double-wall solution is obtained. Further, recharging is much quicker since the heat pump does not turn off in the same manner as when using the double-wall.
  • the present invention further has the advantage that the weight of the total appliance is lighter and the heat pump is thus easier to transport and install.
  • the double-wall may be kept.
  • a defrosting container containing hot water is normally required, wherein the hot water is circulated through an air heat exchanger having a flange battery to defrost ice precipitated on the flange battery.
  • This defrosting container normally constitutes a separate unit, positioned next to the heat pump.
  • the present invention allows that the freed volume in the double-wall is used as a defrosting container. Water that has been cooled during heating of the flange battery may then be reheated by the hot water through the wall of the water container, and then be shunted to the flange battery when necessary.
  • the limited ability of the wall to transfer heat has as result that the temperature of the hot water is only slightly affected.
  • the invention thus has the advantage that the extra container is unnecessary, with following savings in cost and space.
  • the water is circulated through the tubular coil using a circulation pump. Normally, no control of the circulation pump is performed, the water is circulated continuously.
  • a control of the circulation pump may be performed. For example, a very simple control principle may be used, wherein the circulation pump is started when the condensation pressure in the heat pump has reached, e.g. 25,5 bar, which means that the cooling medium has a high temperature and that the primary water thus will be heated to a high temperature when the circulation starts . When the condensation pressure then has dropped, e.g. to 20 bar, due to heat transfer to the primary water the circulation pump is turned of until the condensation pressure again has risen to 25,5 bar.
  • this control method is very simple and may be implemented in a simple manner.
  • the advantage of this control method is that even more hot water may be drawn from the container, in particular when using hot water of higher temperatures, such as 50° hot water.
  • This control method also results in an even greater temperature difference in the container, and thereby higher top temperature.
  • the disadvantage of this control is that the COP of the heat pump is lower than when using an uncontrolled circulation pump due to the higher condensation temperature.
  • Another alternative regulation possibility is to turn on the circulation pump during a certain fraction of the time, e.g. 1 second every 4 seconds.
  • a continuous control of the circulation pump may be applied.
  • the working point of the heat pump compressor may be kept about a predetermined point, e.g. 26 bar, which allows that an even larger volume of high temperature hot water maybe drawn, which may be advantageous for large families or at occasions with guests staying overnight.
  • the lower COP factor raises the costs for heating.
  • the circulation pump may advantageously be variable-speed controlled to enable an accurate and continuous control.
  • circulation pump start and stop pressures merely constitutes an example, and should be chosen lower than the condensation pressure at which the heat pump turns off.
  • the water container may also be provided with a sensor in the top of the water container in order to allow display of a real water temperature.
  • This sensor may also be used in control of hot water production.
  • the heat pump may turn off when the top temperature has reached a certain temperature. This has the ' advantage that a customer may choose at which temperature the heat pump turns off. If the household is not a large consumer of hot water, maybe 45° or 50° is enough to provide the household with a sufficient amount of ready-mixed water from the water in the water container.
  • the sensor may also be used to start the heat pump when the top temperature falls below a certain value, e.g. when the top temperature has fallen due to hot water consumption or heat transfer by radiation, e.g. when the container has been left unused for some time.
  • fig. 3a In fig. 3a is shown a solution to keep the tubular coil in position.
  • a coil support device may be used to keep the coil in position.
  • two diametrically opposed coil support devices 41, 42 that are used to support a coil in a container 43.
  • the coil support devices 41, 42 each consists of two separate parts wherein one 44 constitutes the coil support element and the other part 45 constitutes a coil support locking element.
  • the coil supports are preferably made from thermoplastic such as polyethylene or polyoximethylene and consist of, e.g. a 2 mm thick plate with cut-outs 46 for the coil support.
  • the coil support is bent approximately 90 degrees using a tool and is applied onto the corner of the coil.
  • a coil support locking element in the shape of a stiff rod is inserted into the space arisen between the coil and the coil support from one end.
  • the coil support is shown both in a bent shape and in a planar shape.
  • the coil support may be arranged such that it remains in a bent shape after bending, but may also be arranged such that when the tool releases the coil support this may, as much as possible, tend to again become straight, i.e. until the coil support locking element is stopped by the coil and thereby prohibits the coil support from fully straightening out.
  • the coil support locking element consists of, e.g., a round bar made from polyethylene or polyoxymethylene.
  • the locking element may have a diameter of about 8 mm and be about 900 mm in length.
  • both coil supports are mounted in this manner on each coil and in two opposite corners of the coil.
  • both coil supports may be identical, but shaped such that a compensation for the pitch of the coil is accomplished by turning one support upside down.
  • the lower portions of the coil support rests on the bottom portion of the container and, in this manner, keeps the coil in position and prohibits it from collapsing during transport.
  • the coil support also ensures that a correct positioning of the coil is maintained during the heat exchanger lifetime.
  • the coil support may be completely flat but shaped such that it still may be applied on to a corner of the coil.
  • the corner of the coil may, e.g., be relatively sharp, as may be the case, e.g. when an axial section of the coil is triangular, quadrangular, pentagonal or of another polygon shape.
  • water has been used as heat transfer medium.
  • some other liquid may be used, or fluids such as gas or gas/liquid mixtures.

Abstract

L'invention porte sur un échangeur thermique qui s'utilise avec une pompe thermique, un brûleur à mazout ou similaire, cet échangeur thermique comprenant un contenant d'eau doté d'une entrée permettant de fournir de l'eau à chauffer et d'une sortie afin d'évacuer l'eau chauffée. Cet échangeur thermique comporte aussi : une bobine tubulaire disposée dans le contenant d'eau, cette bobine tubulaire comprenant une entrée pour recevoir des fluides chauds et une sortie pour évacuer ces fluides chauds après être passés à travers la bobine, cette bobine étant constituée d'un matériau qui supporte la chaleur des fluides chauds à diffuser dans l'eau du contenant lors du passage à travers la bobine. Cette invention se rapporte aussi à un système et à un dispositif de support de bobine.
PCT/SE2005/001442 2004-09-29 2005-09-29 Echangeur thermique WO2006036121A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05788736A EP1794532A1 (fr) 2004-09-29 2005-09-29 Echangeur thermique
NO20071639A NO20071639L (no) 2004-09-29 2007-03-28 System som omfatter et varmevekslerarrangement, en kveilholderanordning og et varmevekslerarrangement

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0402355A SE528862C2 (sv) 2004-09-29 2004-09-29 Värmeväxlaranordning
SE0402355-2 2004-09-29

Publications (1)

Publication Number Publication Date
WO2006036121A1 true WO2006036121A1 (fr) 2006-04-06

Family

ID=33414856

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE2005/001442 WO2006036121A1 (fr) 2004-09-29 2005-09-29 Echangeur thermique

Country Status (5)

Country Link
EP (3) EP1983287B1 (fr)
AT (2) ATE524702T1 (fr)
NO (1) NO20071639L (fr)
SE (1) SE528862C2 (fr)
WO (1) WO2006036121A1 (fr)

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CN101586877B (zh) * 2009-07-06 2011-08-10 徐生恒 热平衡式热水器
CN103344043A (zh) * 2013-07-16 2013-10-09 英特换热设备(浙江)有限公司 储热蓄水式热泵热水器及其室内机
EP2136151A4 (fr) * 2007-03-27 2015-11-25 Daikin Ind Ltd Installation de fourniture d'eau chaude de type pompe à chaleur et appareil de fourniture d'eau chaude pour le chauffage

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JP5226576B2 (ja) * 2009-03-26 2013-07-03 株式会社コロナ 貯湯式給湯器
AU2010346932B8 (en) * 2010-02-26 2013-10-17 Daikin Europe N.V. Coil support member
US8795561B2 (en) 2010-09-29 2014-08-05 Milliken & Company Process of forming a nanofiber non-woven containing particles
US8889572B2 (en) 2010-09-29 2014-11-18 Milliken & Company Gradient nanofiber non-woven
TW201417702A (zh) * 2012-11-01 2014-05-16 Zhong-Xiong Que 水中保溫透氣帳蓬
CN104501417B (zh) * 2014-12-01 2017-02-22 江门市君盛实业有限公司 一种盘管固定装置
CN106123097A (zh) * 2016-06-30 2016-11-16 珠海格力电器股份有限公司 基于热水器的取暖装置

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US2865612A (en) * 1956-04-02 1958-12-23 Hall Robert M Vehicular water heaters for field use
GB1029468A (en) * 1963-08-16 1966-05-11 Beteiligungs & Patentverw Gmbh Combined hot water space heating and hot water supply system
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DE1454702A1 (de) * 1962-10-08 1969-03-27 Omnical Ges Fuer Kessel Und Ap Lagerung und Halterung von Rohrspiralen in Warmwasser-Durchflussboilern
DE1679730A1 (de) * 1967-09-22 1971-03-25 Richard Gruchol Brauchwassererwaermer
US3828847A (en) * 1973-02-14 1974-08-13 Glass Lined Water Heater Co Hot water heater
JPS52124262A (en) * 1976-04-12 1977-10-19 Kawasaki Heavy Ind Ltd Heat pipe supporting parts for helical coil typehet exchanger
US4201264A (en) * 1978-07-31 1980-05-06 Owens-Illinois, Inc. Solar water tank
GB2069667A (en) * 1980-02-18 1981-08-26 Hawkhead Bray & Son Ltd A hot water system
US4350024A (en) * 1979-10-15 1982-09-21 Cinderella Ab Heating system
DE3403337A1 (de) * 1983-02-26 1984-08-30 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Vorrichtung zum erwaermen von wasser
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US4667482A (en) * 1984-08-29 1987-05-26 Anstalt f/u/ r Metallbau Heat exchanger device
US5165472A (en) * 1991-03-18 1992-11-24 Louis Cloutier Heat exchanger with fluid injectors
EP0663569A1 (fr) * 1994-01-14 1995-07-19 Martin Mag. Ing. Bergmayr Installation de chauffage, en particulier de chauffage solaire
EP0676592A2 (fr) * 1994-04-08 1995-10-11 Bradford-White Corporation Déchauffeur d'eau et échangeur de chaleur combiné
EP1371908A1 (fr) * 2002-06-12 2003-12-17 Justo Comadira Gonzalez Chauffe-eau avec échangeur de chaleur à haute performance

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB603315A (en) * 1945-10-18 1948-06-14 Ewart & Son Ltd Improvements in water heaters
US2865612A (en) * 1956-04-02 1958-12-23 Hall Robert M Vehicular water heaters for field use
DE1454702A1 (de) * 1962-10-08 1969-03-27 Omnical Ges Fuer Kessel Und Ap Lagerung und Halterung von Rohrspiralen in Warmwasser-Durchflussboilern
GB1029468A (en) * 1963-08-16 1966-05-11 Beteiligungs & Patentverw Gmbh Combined hot water space heating and hot water supply system
GB1070513A (en) * 1965-02-22 1967-06-01 Maurice Vidalenq Combined central heating and hot water supply boiler
DE1679730A1 (de) * 1967-09-22 1971-03-25 Richard Gruchol Brauchwassererwaermer
US3828847A (en) * 1973-02-14 1974-08-13 Glass Lined Water Heater Co Hot water heater
JPS52124262A (en) * 1976-04-12 1977-10-19 Kawasaki Heavy Ind Ltd Heat pipe supporting parts for helical coil typehet exchanger
US4201264A (en) * 1978-07-31 1980-05-06 Owens-Illinois, Inc. Solar water tank
US4350024A (en) * 1979-10-15 1982-09-21 Cinderella Ab Heating system
GB2069667A (en) * 1980-02-18 1981-08-26 Hawkhead Bray & Son Ltd A hot water system
DE3403337A1 (de) * 1983-02-26 1984-08-30 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Vorrichtung zum erwaermen von wasser
US4667482A (en) * 1984-08-29 1987-05-26 Anstalt f/u/ r Metallbau Heat exchanger device
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EP2136151A4 (fr) * 2007-03-27 2015-11-25 Daikin Ind Ltd Installation de fourniture d'eau chaude de type pompe à chaleur et appareil de fourniture d'eau chaude pour le chauffage
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CN103344043A (zh) * 2013-07-16 2013-10-09 英特换热设备(浙江)有限公司 储热蓄水式热泵热水器及其室内机
CN103344043B (zh) * 2013-07-16 2015-08-12 英特换热设备(浙江)有限公司 储热蓄水式热泵热水器及其室内机

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ATE524702T1 (de) 2011-09-15
EP1983286A1 (fr) 2008-10-22
EP1794532A1 (fr) 2007-06-13
ATE524701T1 (de) 2011-09-15
EP1983287A1 (fr) 2008-10-22
NO20071639L (no) 2007-05-07
SE0402355D0 (sv) 2004-09-29
EP1983286B1 (fr) 2011-09-14
EP1983287B1 (fr) 2011-09-14
SE0402355L (sv) 2006-03-30
SE528862C2 (sv) 2007-02-27

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