US2696085A - Heat pump water heater - Google Patents
Heat pump water heater Download PDFInfo
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- US2696085A US2696085A US279703A US27970352A US2696085A US 2696085 A US2696085 A US 2696085A US 279703 A US279703 A US 279703A US 27970352 A US27970352 A US 27970352A US 2696085 A US2696085 A US 2696085A
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- 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
Definitions
- This invention relates to heat pumps and more particularly to water heaters of the domestic type which operate on the heat pump principle.
- Apparatus of this general type embodies basically, a hot water storage tank and a heat pump of the type in which a refrigerant is used as the working fluid.
- the heat pump itself includes a motor driven compressor, an evaporator and a condenser.
- the evaporator is placed in a convenient location where it is exposed to a source of heat and the condenser is disposed within the hot water storage tank.
- the compressor serves to withdraw gaseous refrigerant from the evaporator and compress the gaseous refrigerant thereby further raising its heat content.
- the hot gaseous refrigerant is then pumped through the condenser where it is changed back to liquid phase giving up its superheat, if any, plus its latent heat of condensation to the water in the tank. From this point the liquefied refrigerant is led through an expansion device to the evaporator and the cycle is repeated.
- the apparatus described herein embodies several improvements over known devices of this type.
- the objects of this invention are to provide a heat pump water heater of improved design and operating efficiency.
- the basic improvement to be described in detail herein involves a novel refrigerant circuit for the heat pump, in which a motor compressor unit having both a high discharge pressure and low discharge pressure outlet is used.
- the heat exchanger condenser is divided in three sections. One section is positioned in the upper portion of the hot water storage tank, a second is positioned substantially in the mid-section of the tank, and the third is located in the lower portion of the tank.
- the singl vfigure shows in diagrammatic form the basic refrigerant circuit, and arrangement of the apparatus.
- the apparatus comprises essentially a refrigerant evaporator unit 10, a hot water storage tank 11, a motor compressor unit 12, and a con denser type heat exchanger.
- the evaporator may be mounted on the tank as shown, or it may be placed in any convenient location where it is in heat exchange relation with a source of heat.
- the source of heat may be a source otherwise wasted, such as waste heat from a cooking stove or chimney flue.
- the evaporator serves to cool and dehumidify the kitchen and in the latter case, the dehumidifying action is a desirable one in an otherwise damp basement.
- the heat exchanger includes a desuperheating coil 13 arranged in the upper part of the storage tank 11, a high temperature condenser 14 arranged at about the mid portion of the tank, and a low temperature condenser 15 located in the lower portion of the tank.
- the bottom of the low temperature condensing coil is connected to the evaporator unit by a conventional liquid line 16 in which is interposed an expansion valve 17.
- the latter may be of any of several well known types, such as, for example, a thermally controlled expansion valve.
- a suction line 18 connects the other side of the evaporator unit 10 to a suction inlet on the motor compressor unit WhlCl'l inlet is common to both cylinders.
- the compressor unit itself in accordance with the present invention comprises a pair of cylinders 19 and 20, the former being a high discharge pressure cylinder, and
- a line 21 connects the high discharge pressure cylinder 19 to the input side of the desuperheating coil 13 and a similar line 22 connects the output of the low discharge pressure cylinder 20 to the input side of the low temperature condensing coil 15.
- the low temperature condenser is therefore fed jointly by the discharge from the high temperature condenser coil and the discharge from the low discharge pressure cylinder 20.
- a pressure reducing device 23 is interposed between the high and low temperature condensing coils above the point where the line 22 connects the low discharge pressure cylinder to the low temperature condenser. This serves to maintain a pressure differential between the high and low temperature condensing stages.
- the pressure reducing device may assume any one of several well known forms. For example, it may be a capillary tube, a spring loaded relief valve, or even a hand adjustable throttle valve.
- a thermostat 24 may be located substantially at the mid-section of the storage tank in heat exchange relation to the water in the tank at that point, and is connected in series with the source of electrical supply to the motor compressor unit.
- a fan 25 driven by an electric motor 26 maintains a fiow of air over the evaporator unit 10, and the motor 26 is connected in parallel with the motor of the motor compressor unit so that it also will be controlled by the thermostat 24-.
- the thermostat 24 In operation, therefore, inresponse to a demand for heat in the storage tank, the thermostat 24 operates to close the circuit to the motor compressor unit 12 and the fan motor 26.
- the motor compressor unit then supplies superheated refrigerant to coil 13 and simultaneously supplies heated gaseous refrigerant at a relatively lower temperature and pressure to the heat exchange coil 15.
- the refrigerant in coil 13 loses its superheatto the water in the upper portion of the tank and then flows, as a saturated gas, down to the high temperature condenser where it is partially condensed, and part of the latent heat of condensation is transferred to the water in the mid-section of the tank.
- the mixture of gas and liquid after passing through the pressure reducing device then joins the heated gas from the low pressure cylinder.
- the resulting mixture is then circulated through the low temperature condenser coil 15 to give up the remainder of its latent heat of condensation to the water in the lower portion of the tank.
- the cooled and liquefied refrigerant passes through the liquid line 16, the expansion valve 17 and into the evaporator unit 10. There, in changing back from liquid to gaseous state, it picks up heat from the ambient air being circulated through the evaporator coils by the fan 25.
- the heat laden refrigerant is then returned to a common intake of the motor compressor unit through the suction line 18, where it is recompressed and the cycle is repeated.
- the storage tank 11 is provided with a depression or pocket 27 in a side wall of the tank adjacent the upper end thereof.
- the motor compressor unit will be of the well known hermetically sealed type, but it in turn will be wholly received within the pocket 27 and also sealed therein.
- the space intermediate the motor compressor unit and the pocket is then filled with a non inflammable liquid having good heat transfer characteristics in order to increase the rate of transfer of the waste heat from the motor compressor to the warmest Water in the upper portion of the tank by conduction.
- a liquid Well adapted to this purpose is Pyranol, which is a well known oil, in common use, in oilimmersed electrical transformer apparatus. it also has high dielectric constant which is desirable to prevent short circuiting the electrical leads which carry current to the motor compressor unit.
- the water in the storage tank of heaters of this type tends to stratify in definite temperature levels.
- the hottest water will be in the upper portion of the tank surrounding the desuperheating coil, while the water in the bottom portion of the tank surrounding the low temperature condenser coil may be only a few degrees warmer than the make up water.
- the water in the mid-section of the tank, surrounding the high temperature condenser will be at an intermediate temperature and these temperature strata remain fairly constant in normal operation of the apparatus. For this reason, the operating characteristics of the heat exchanger, that is, its temperature and pressure in the three sections, also remain substantially constant.
- a water heater of the heat pump type comprising in combination: a hot water storage tank; a refrigerant evaporator adapted to absorb heat from the atmosphere; heat transfer means of the type in which refrigerant is circulated, said means being disposed in heat exchange relation to the water in said tank, extending substantially from top to bottom thereof and including during normal operating conditions, a desuperheating stage located adjacent the upper part of said tank, a high temperature condensing stage located substantially at the mid-section of said tank, and a low temperature condensing stage located adjacent the bottom part of said tank said stages being connected in series; means connected between said high and low temperature stages to maintain a controlled pressure differential therebetween; means connecting said low temperature condensing stage to said evaporator, said means including an expansion device; motor driven refrigerant compression means, said means including at least a low discharge pressure outlet and a high discharge pressure outlet; a common suction inlet for said compression means; means connecting said high discharge pressure outlet to said desuperheating stage; means connecting said low discharge pressure outlet to
- a water heater of the heat pump type comprising in combination: a hot Water storage tank; a refrigerant evaporator adapted to absorb heat from the atmosphere; heat transfer means of the type in which refrigerant is circulated, said means being disposed in heat exchange relation to the water in said tank, extending substantially from top to bottom thereof and including during normal operating conditions, a desuperheating stage located adjacent the upper part of said tank, a high temperature condensing stage located substantially at the mid-section of said tank, and a low temperature condensing stage located adjacent the bottom part of said tank said stages being connected in series; means connected between said high and low temperature stages to maintain a controlled pressure differential therebetween; means connecting said low temperature condensing stage to said evaporator, said means including an expansion device; a motor compressor unit, said compressor including a low discharge pressure cylinder and a high discharge pressure cylinder; a suction inlet to said compressor common to both said cylinders; means connecting said high discharge pressure cylinder to said desuperheating stage; means connecting said low discharge
- a water heater as defined by claim 1 in which the motor compressor unit is mounted on and in heat exchange relation to said storage tank.
- a water heater as defined by claim 1 in which said storage tank is formed with a depressed pocket in the side wall thereof adjacent the upper portion thereof; means sealing said motor compressor unit within said pocket; and a noninfiammable liquid having a high dielectric constant interposed in the space intermediate said compressor unit and said storage tank to increase the rate of heat transfer from said motor compressor to the water in said tank.
- a heat pump comprising: a motor compressor unit, said compressor including a low discharge pressure cylinder and a high discharge pressure cylinder; a suction inlet to said compressor common to both said cylinders; an evaporator; a condenser type heat exchanger; conduit means connecting the high discharge pressure cylinder of said motor compressor unit to one end of said heat exchanger; conduit means including an expansion device connecting the opposite end of said heat exchanger to said evaporator; conduit means connecting the low discharge pressure cylinder of said motor compressor unit to an intermediate point on said heat exchanger; means connected to said heat exchanger for maintaining a controlled pressure differential between that portion of the heat exchanger to which the high discharge pressure cylinder is connected and that portion to which the low discharge pressure cylinder is connected; and further conduit means connecting said evaporator to the suction inlet of said motor compressor.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Description
Dec. 7, 1954 w RUFF HEAT PUMP WATER HEATER Filed March 51, 1952 g] iv PRESSURE REDl/G /NG DEV/CE HOT WATER COLD WA TER INVENTOR A L ONZ o W. RUFF ATTORNEY United States Patent HEAT PUMP WATER HEATER Alonzo W. Ruff, York, Pa., assignor to V. C. Patterson & Associates, Inc., York, Pa., a corporation of Pennsylvania Application March 31, 1952, Serial No. 279,703
5 Claims. (Cl. 62-4) This invention relates to heat pumps and more particularly to water heaters of the domestic type which operate on the heat pump principle.
Apparatus of this general type embodies basically, a hot water storage tank and a heat pump of the type in which a refrigerant is used as the working fluid. The heat pump itself includes a motor driven compressor, an evaporator and a condenser. The evaporator is placed in a convenient location where it is exposed to a source of heat and the condenser is disposed within the hot water storage tank. In operation, the compressor serves to withdraw gaseous refrigerant from the evaporator and compress the gaseous refrigerant thereby further raising its heat content. The hot gaseous refrigerant is then pumped through the condenser where it is changed back to liquid phase giving up its superheat, if any, plus its latent heat of condensation to the water in the tank. From this point the liquefied refrigerant is led through an expansion device to the evaporator and the cycle is repeated.
The apparatus described herein embodies several improvements over known devices of this type.
In general, the objects of this invention are to provide a heat pump water heater of improved design and operating efficiency.
The basic improvement to be described in detail herein involves a novel refrigerant circuit for the heat pump, in which a motor compressor unit having both a high discharge pressure and low discharge pressure outlet is used. The heat exchanger condenser is divided in three sections. One section is positioned in the upper portion of the hot water storage tank, a second is positioned substantially in the mid-section of the tank, and the third is located in the lower portion of the tank.
The invention may be readily understood from the following description read in conjunction with the accompanying sheet of drawings, in which:
The singl vfigure shows in diagrammatic form the basic refrigerant circuit, and arrangement of the apparatus.
Referring now to the drawing, the apparatus comprises essentially a refrigerant evaporator unit 10, a hot water storage tank 11, a motor compressor unit 12, and a con denser type heat exchanger. The evaporator may be mounted on the tank as shown, or it may be placed in any convenient location where it is in heat exchange relation with a source of heat. Conveniently, the source of heat may be a source otherwise wasted, such as waste heat from a cooking stove or chimney flue. In case of the former, the evaporator serves to cool and dehumidify the kitchen and in the latter case, the dehumidifying action is a desirable one in an otherwise damp basement. The heat exchanger includes a desuperheating coil 13 arranged in the upper part of the storage tank 11, a high temperature condenser 14 arranged at about the mid portion of the tank, and a low temperature condenser 15 located in the lower portion of the tank. The bottom of the low temperature condensing coil is connected to the evaporator unit by a conventional liquid line 16 in which is interposed an expansion valve 17. The latter may be of any of several well known types, such as, for example, a thermally controlled expansion valve. A suction line 18 connects the other side of the evaporator unit 10 to a suction inlet on the motor compressor unit WhlCl'l inlet is common to both cylinders.
The compressor unit itself in accordance with the present invention, comprises a pair of cylinders 19 and 20, the former being a high discharge pressure cylinder, and
the latter being a relatively low discharge pressure cylinder. A line 21 connects the high discharge pressure cylinder 19 to the input side of the desuperheating coil 13 and a similar line 22 connects the output of the low discharge pressure cylinder 20 to the input side of the low temperature condensing coil 15. The low temperature condenser is therefore fed jointly by the discharge from the high temperature condenser coil and the discharge from the low discharge pressure cylinder 20. A pressure reducing device 23 is interposed between the high and low temperature condensing coils above the point where the line 22 connects the low discharge pressure cylinder to the low temperature condenser. This serves to maintain a pressure differential between the high and low temperature condensing stages. In practice, the pressure reducing device may assume any one of several well known forms. For example, it may be a capillary tube, a spring loaded relief valve, or even a hand adjustable throttle valve.
In order to control the rate of transfer of heat to the water in the tank, a thermostat 24 may be located substantially at the mid-section of the storage tank in heat exchange relation to the water in the tank at that point, and is connected in series with the source of electrical supply to the motor compressor unit. A fan 25 driven by an electric motor 26 maintains a fiow of air over the evaporator unit 10, and the motor 26 is connected in parallel with the motor of the motor compressor unit so that it also will be controlled by the thermostat 24-.
In operation, therefore, inresponse to a demand for heat in the storage tank, the thermostat 24 operates to close the circuit to the motor compressor unit 12 and the fan motor 26. The motor compressor unit then supplies superheated refrigerant to coil 13 and simultaneously supplies heated gaseous refrigerant at a relatively lower temperature and pressure to the heat exchange coil 15. The refrigerant in coil 13 loses its superheatto the water in the upper portion of the tank and then flows, as a saturated gas, down to the high temperature condenser where it is partially condensed, and part of the latent heat of condensation is transferred to the water in the mid-section of the tank. The mixture of gas and liquid after passing through the pressure reducing device, then joins the heated gas from the low pressure cylinder. The resulting mixture is then circulated through the low temperature condenser coil 15 to give up the remainder of its latent heat of condensation to the water in the lower portion of the tank. From there, the cooled and liquefied refrigerant passes through the liquid line 16, the expansion valve 17 and into the evaporator unit 10. There, in changing back from liquid to gaseous state, it picks up heat from the ambient air being circulated through the evaporator coils by the fan 25. The heat laden refrigerant is then returned to a common intake of the motor compressor unit through the suction line 18, where it is recompressed and the cycle is repeated.
It has been discovered that the basic refrigerant circuit as described above yields superior results, as to operating eificiency. While the compressor shown on the attached drawing is of the piston type, it will be apparent to those skilled in the art that other well known types, such for example as rotary compressors, are readily adaptable to the apparatus herein shown and described. Also, a compressor having more than two difierent discharge pressure outlets could be used. For example, a compressor having three diiferent discharge pressure outlets could be used to feed separately, the three stages of the heat exchanger.
In addition, however, to the above described refinements in the refrigerant circuit, it has also been discovered that the waste heat of the motor compressor unit may be more effectively utilized by increasing its rate of transfer to the water in the tank. This is accomplished by certain structural modifications, a description of which follows.
Referring again to the drawing, it will be seen that the storage tank 11 is provided with a depression or pocket 27 in a side wall of the tank adjacent the upper end thereof. In practice, the motor compressor unit will be of the well known hermetically sealed type, but it in turn will be wholly received within the pocket 27 and also sealed therein. The space intermediate the motor compressor unit and the pocket is then filled with a non inflammable liquid having good heat transfer characteristics in order to increase the rate of transfer of the waste heat from the motor compressor to the warmest Water in the upper portion of the tank by conduction. One ex ample of a liquid Well adapted to this purpose is Pyranol, which is a well known oil, in common use, in oilimmersed electrical transformer apparatus. it also has high dielectric constant which is desirable to prevent short circuiting the electrical leads which carry current to the motor compressor unit.
The water in the storage tank of heaters of this type tends to stratify in definite temperature levels. The hottest water will be in the upper portion of the tank surrounding the desuperheating coil, while the water in the bottom portion of the tank surrounding the low temperature condenser coil may be only a few degrees warmer than the make up water. The water in the mid-section of the tank, surrounding the high temperature condenser will be at an intermediate temperature and these temperature strata remain fairly constant in normal operation of the apparatus. For this reason, the operating characteristics of the heat exchanger, that is, its temperature and pressure in the three sections, also remain substantially constant.
The foregoing will enable one skilled in the art to fully understand the invention and the novelty thereof which is defined by the following claims.
I claim:
1. A water heater of the heat pump type, comprising in combination: a hot water storage tank; a refrigerant evaporator adapted to absorb heat from the atmosphere; heat transfer means of the type in which refrigerant is circulated, said means being disposed in heat exchange relation to the water in said tank, extending substantially from top to bottom thereof and including during normal operating conditions, a desuperheating stage located adjacent the upper part of said tank, a high temperature condensing stage located substantially at the mid-section of said tank, and a low temperature condensing stage located adjacent the bottom part of said tank said stages being connected in series; means connected between said high and low temperature stages to maintain a controlled pressure differential therebetween; means connecting said low temperature condensing stage to said evaporator, said means including an expansion device; motor driven refrigerant compression means, said means including at least a low discharge pressure outlet and a high discharge pressure outlet; a common suction inlet for said compression means; means connecting said high discharge pressure outlet to said desuperheating stage; means connecting said low discharge pressure outlet to said low temperature condensing stage; means connecting said evaporator to the suction inlet of said compressor; and means responsive to the temperature of the water in said tank to control the transfer of heat thereto.
2. A water heater of the heat pump type, comprising in combination: a hot Water storage tank; a refrigerant evaporator adapted to absorb heat from the atmosphere; heat transfer means of the type in which refrigerant is circulated, said means being disposed in heat exchange relation to the water in said tank, extending substantially from top to bottom thereof and including during normal operating conditions, a desuperheating stage located adjacent the upper part of said tank, a high temperature condensing stage located substantially at the mid-section of said tank, and a low temperature condensing stage located adjacent the bottom part of said tank said stages being connected in series; means connected between said high and low temperature stages to maintain a controlled pressure differential therebetween; means connecting said low temperature condensing stage to said evaporator, said means including an expansion device; a motor compressor unit, said compressor including a low discharge pressure cylinder and a high discharge pressure cylinder; a suction inlet to said compressor common to both said cylinders; means connecting said high discharge pressure cylinder to said desuperheating stage; means connecting said low discharge pressure cylinder to said low temperature condensing stage; means connecting said evaporator to the suction inlet of said compressor; and means responsive to the temperature of the water in said tank to control the transfer of heat thereto.
3. A water heater as defined by claim 1 in which the motor compressor unit is mounted on and in heat exchange relation to said storage tank.
4. A water heater as defined by claim 1 in which said storage tank is formed with a depressed pocket in the side wall thereof adjacent the upper portion thereof; means sealing said motor compressor unit within said pocket; and a noninfiammable liquid having a high dielectric constant interposed in the space intermediate said compressor unit and said storage tank to increase the rate of heat transfer from said motor compressor to the water in said tank.
5. In a water heater of the heat pump type, a heat pump comprising: a motor compressor unit, said compressor including a low discharge pressure cylinder and a high discharge pressure cylinder; a suction inlet to said compressor common to both said cylinders; an evaporator; a condenser type heat exchanger; conduit means connecting the high discharge pressure cylinder of said motor compressor unit to one end of said heat exchanger; conduit means including an expansion device connecting the opposite end of said heat exchanger to said evaporator; conduit means connecting the low discharge pressure cylinder of said motor compressor unit to an intermediate point on said heat exchanger; means connected to said heat exchanger for maintaining a controlled pressure differential between that portion of the heat exchanger to which the high discharge pressure cylinder is connected and that portion to which the low discharge pressure cylinder is connected; and further conduit means connecting said evaporator to the suction inlet of said motor compressor.
References Cited in the file of this patent UNITED STATES PATENTS
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US279703A US2696085A (en) | 1952-03-31 | 1952-03-31 | Heat pump water heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US279703A US2696085A (en) | 1952-03-31 | 1952-03-31 | Heat pump water heater |
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| Publication Number | Publication Date |
|---|---|
| US2696085A true US2696085A (en) | 1954-12-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| US279703A Expired - Lifetime US2696085A (en) | 1952-03-31 | 1952-03-31 | Heat pump water heater |
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Cited By (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2802342A (en) * | 1957-08-13 | Heat pumps | ||
| DE1027216B (en) * | 1955-04-04 | 1958-04-03 | Borsig Ag | Method and device for operating a heat pump |
| US2968934A (en) * | 1957-03-05 | 1961-01-24 | Heat Pump & Refrigeration Ltd | Heat pump systems |
| DE1107682B (en) * | 1959-04-21 | 1961-05-31 | Minnesota Mining & Mfg | Container for storing, heating and cooling liquids by means of a thermoelectric heat pump |
| DE1174339B (en) * | 1959-10-27 | 1964-07-23 | Schiff & Stern Ges M B H | Motor unit for cooling machines for refrigerators that work according to the heat pump principle |
| US3244010A (en) * | 1962-11-23 | 1966-04-05 | William F Martin | Temperature dependent density gradient |
| US4146089A (en) * | 1976-03-29 | 1979-03-27 | Paul Mueller Company | Hot water system and condensing unit therefor |
| US4173872A (en) * | 1978-02-01 | 1979-11-13 | Energy Utilization Systems, Inc. | Water heater apparatus |
| US4216660A (en) * | 1978-05-04 | 1980-08-12 | T.E.S., Inc. | Heat generator |
| WO1981000616A1 (en) * | 1979-08-21 | 1981-03-05 | Genvex Energiteknik As | Heat exchanger |
| US4448347A (en) * | 1981-12-09 | 1984-05-15 | Dunstan Phillip E | Heat pump system using wastewater heat |
| US4474018A (en) * | 1982-05-06 | 1984-10-02 | Arthur D. Little, Inc. | Heat pump system for production of domestic hot water |
| US4517799A (en) * | 1983-03-09 | 1985-05-21 | Misawa Home Co., Ltd. | Heat utilizing system using internal combustion engine |
| US4747273A (en) * | 1987-03-05 | 1988-05-31 | Artesian Building Systems | Heating and cooling system |
| US4798240A (en) * | 1985-03-18 | 1989-01-17 | Gas Research Institute | Integrated space heating, air conditioning and potable water heating appliance |
| US4959975A (en) * | 1987-05-14 | 1990-10-02 | Conserve, Inc. | Heat pump system |
| US5906109A (en) * | 1998-04-14 | 1999-05-25 | Arthur D. Little, Inc. | Heat pump water heater and storage tank assembly |
| US6290142B1 (en) * | 1999-04-14 | 2001-09-18 | Honda Giken Kogyo Kabushiki Kaisha | Cogeneration apparatus |
| US6595011B1 (en) | 2002-05-02 | 2003-07-22 | Linda Forgy Chaney | Water cooled air conditioner |
| US20060191495A1 (en) * | 2003-10-21 | 2006-08-31 | Ting Sun | Air heat pump type hot water stove |
| US20070039341A1 (en) * | 2005-08-17 | 2007-02-22 | Bradford White Corporation | Heat pump water heater |
| US20070214816A1 (en) * | 2004-09-16 | 2007-09-20 | Matsushita Electric Industrial Co., Ltd. | Heat-pump-type hot water supply apparatus |
| WO2008094152A1 (en) * | 2007-02-01 | 2008-08-07 | Cotherm Of America Corporation | Heat transfer system and associated methods |
| WO2009049612A2 (en) * | 2007-10-20 | 2009-04-23 | Solarhybrid Ag | Heat accumulator for storing thermal energy and method for shifting thermal energy in a heat accumulator |
| AU2005202057B2 (en) * | 2004-05-14 | 2010-10-28 | Rheem Australia Pty Limited | An improved evaporator for a heat pump water heater |
| US20110061418A1 (en) * | 2009-09-17 | 2011-03-17 | Panasonic Corporation | Heat pump type hot-water heater |
| US8385729B2 (en) | 2009-09-08 | 2013-02-26 | Rheem Manufacturing Company | Heat pump water heater and associated control system |
| AT516383B1 (en) * | 2015-02-03 | 2016-05-15 | Forstner Maximilian | fluid reservoir |
| US9488384B2 (en) | 2013-03-22 | 2016-11-08 | Carrier Corporation | Heat pump water module with condensing coil in water storage tank |
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| US2463881A (en) * | 1946-07-06 | 1949-03-08 | Muncie Gear Works Inc | Heat pump |
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| US2516094A (en) * | 1949-05-17 | 1950-07-18 | V C Patterson & Associates Inc | Heat pump water heater |
| US2597745A (en) * | 1948-09-29 | 1952-05-20 | Sunroc Refrigeration Company | Refrigerator and stove |
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1952
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| US2104974A (en) * | 1936-06-15 | 1938-01-11 | Bailey P Dawes | Fuel heater for internal combustion engines |
| US2463881A (en) * | 1946-07-06 | 1949-03-08 | Muncie Gear Works Inc | Heat pump |
| US2500688A (en) * | 1948-08-24 | 1950-03-14 | Edward P Kellie | Refrigerating apparatus |
| US2597745A (en) * | 1948-09-29 | 1952-05-20 | Sunroc Refrigeration Company | Refrigerator and stove |
| US2516093A (en) * | 1949-05-05 | 1950-07-18 | V C Patterson & Associates Inc | Heat pump water heater and method of heat exchange |
| US2516094A (en) * | 1949-05-17 | 1950-07-18 | V C Patterson & Associates Inc | Heat pump water heater |
Cited By (40)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2802342A (en) * | 1957-08-13 | Heat pumps | ||
| DE1027216B (en) * | 1955-04-04 | 1958-04-03 | Borsig Ag | Method and device for operating a heat pump |
| US2968934A (en) * | 1957-03-05 | 1961-01-24 | Heat Pump & Refrigeration Ltd | Heat pump systems |
| DE1102187B (en) * | 1957-03-05 | 1961-03-16 | Heat Pump & Refrigeration Ltd | Heat pump system |
| DE1107682B (en) * | 1959-04-21 | 1961-05-31 | Minnesota Mining & Mfg | Container for storing, heating and cooling liquids by means of a thermoelectric heat pump |
| DE1174339B (en) * | 1959-10-27 | 1964-07-23 | Schiff & Stern Ges M B H | Motor unit for cooling machines for refrigerators that work according to the heat pump principle |
| US3244010A (en) * | 1962-11-23 | 1966-04-05 | William F Martin | Temperature dependent density gradient |
| US4146089A (en) * | 1976-03-29 | 1979-03-27 | Paul Mueller Company | Hot water system and condensing unit therefor |
| US4173872A (en) * | 1978-02-01 | 1979-11-13 | Energy Utilization Systems, Inc. | Water heater apparatus |
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