CA1167653A - Heat pump - Google Patents
Heat pumpInfo
- Publication number
- CA1167653A CA1167653A CA000382456A CA382456A CA1167653A CA 1167653 A CA1167653 A CA 1167653A CA 000382456 A CA000382456 A CA 000382456A CA 382456 A CA382456 A CA 382456A CA 1167653 A CA1167653 A CA 1167653A
- Authority
- CA
- Canada
- Prior art keywords
- tube
- evaporator
- heat pump
- external fluid
- heat
- 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.)
- Expired
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
- F24D3/00—Hot-water central heating systems
- F24D3/12—Tube and panel arrangements for ceiling, wall, or underfloor heating
- F24D3/14—Tube and panel arrangements for ceiling, wall, or underfloor heating incorporated in a ceiling, wall or floor
- F24D3/146—Tubes specially adapted for underfloor heating
-
- 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
- F24D3/18—Hot-water central heating systems using heat pumps
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
- F28D7/06—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 having a single U-bend
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/12—Hot water central heating systems using heat pumps
Landscapes
- 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)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Central Heating Systems (AREA)
- Control Of The Air-Fuel Ratio Of Carburetors (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A heat pump comprising a compressor, an evaporator and a condensor. The evaporator comprises a first tube to be contacted by an external fluid, which is closed at the ends, and a second tube inside the first tube and substantially coaxial therewith, which extends from one end of the first tube and opens at some distance from the other end of this tube. At said one end said first tube is connected to the suction side of the compressor, while said second tube at said one end is connected to the pressure side of the compressor to form the throttling means of the evaporator.
A heat pump comprising a compressor, an evaporator and a condensor. The evaporator comprises a first tube to be contacted by an external fluid, which is closed at the ends, and a second tube inside the first tube and substantially coaxial therewith, which extends from one end of the first tube and opens at some distance from the other end of this tube. At said one end said first tube is connected to the suction side of the compressor, while said second tube at said one end is connected to the pressure side of the compressor to form the throttling means of the evaporator.
Description
I i 6 7 6 5 3 HEAT PUMP
The in~ention relates to a h'eat pump comprising a compressor fQr circulating a refrigerant, an evaporator for thé evapQration of li'quid refrigerant, in heat exchange relationship with an external fluid, and a condensor for the condensation of the evaporated re- i~
frigerant.
According to the invention a heat pump of this type is characterized in that the evaporator comprises a first tube to be contacted by the external fluid at the outside thereof, which is connected at one end to the suction side of the compressor and is closed at the other end, and a second tube connected to the condensor, 1~ which extends substantially coaxially into said first tube,'from said one end thereof and opens at some distance from the other, closed end of the first tube to form the throttling means of the evaporator.
By this arrangement there is achieved not only a very simple construction of the evaporator but also an automatic adjustment of the supply of liquid refrigerant to the evaporator in dependance of the amount of heat supplied: when a small amount of heat is supplied to the e~aporator from the external fluid, a lower vapor-ization temperature is required in the evaporator, andthis is automatically achieved in the evaporator accord-ing to the inYention by the flow of liquid refrigerant being automatically reduced at decreasing temperature.
It is not known for sure what causes this effect 3~ but it is supposed that it is caused by the fact that oil entrained in the circulating refrigerant and emanat-ing from the compressor of the heat pump, is becoming increasingly Yiscous the lower the temperature of the external fluid will be, whereby the flow of liquid refrigerant thr'ough said second tube will be restrained.
-S~
Preferably said first tube is surrounded by an elongated tubular outer casing forming part of a conduit for circulating the external fluid.
The invention will be explained in more detail below, reference being made to the attached drawings in which FIG 1 is a diagrammatic view of a heat pump in accordance with the invention, and FIG 2 is a transparent perspective view of the evaporator and a tube forming an outer casing there-of, which conveys the external fluid.
The heat pump disclosed in F~G 1 comprises a com-pressor 10 which pumps a refrigerant such as freon to a condensor 11 and therefrom to an evaporator 12 which lS is more clearly disclosed in FIG 2. The evaporator is arranged inside an outer casing formed by a tube 13, which is closed at one end thereof at 14 and is connec-ted to a circulation pump 15 at the other end thereof.
A number of tubes 16 of a smaller cross section than the tube 13 are connected at one end thereof to the tube 13. They extend in parallel from the tube 13 in the transverse direction thereof and then form a bow 17 of 180 to return to the tube 13 in parallel so as to be connected at the other end thereof to another tube 18 identical with the tube 13. The tube 18 is closed at one end thereof at 19 and is connected at the other end to the circulation pump 15, which circulates an external fluid such as water through the tubes 13, 16 and 18 as indicated by arrows in the drawings. Thus, it will be seen that the tubes 13 and 18 form manifolds for the tubes 16. The tubes 13, 16 and 18 preferably are , ~ made of a highly durabc~e~an;d~flexible synthetic elasto-mer such as polyvinyl clv-rt~ (PVC) in which case they may co~prise black PVC tubes of the type used for fresh water networks, or ethylene-propylene-diene-monomer ~ 1 67653 (EPDM). It is essential that the material of the tubes is impervious to corrosion, ultraviolet light and chemi-cal deterioration and eliminates freeze-up problems.
In FIG 1 the tubes 16 are arranged in a group comprising six tubes, and a desired number of such groups of tubes may be connected to the tubes 13 and 18, a further group being fragmentarily shown at 16'.
The tubes 13, 16 and 18 form a heat exchanger for supplying heat to the evaporator 12, and this heat ex-changer may be located in the ground so that the fluidcirculated therein absorbs ground heat, or may be sus-pended in stands which are located e.g. on a garage or car port roof or on a wall or a fence, so that the fluid circulated therein absorbs air heat.
In a preferred embodiment of the heat exchanger described the tubes 16 in each group consist of an ab-sorber mat which is marketed under the registered trade mark SolaRoll and is manufactured by Bio-Energy Systems, Inc., Ellenville, New York, USA. They can be arranged in the end return configuration shown in FIG I but other configur2tions known in the art may be arranged such as the butterfly type or the grid type. A balanced flow as that shown in FIG 1 wherein the circulating fluid has the same flow direction in the tubes 13 and 18 - 25 is preferred over the unbalanced flow with opposite flow directions in said tubes.
The external fluid which has absorbed heat during the passage of the heat exchanger described passes the evaporator 12 in heat exchange relationship therewith to supply the heat necessary for the evaporation of the liquid refrigerant supplied to the evaporator. The ex-ternal fluid usually would have a temperature of 6 to 8C but the temperature may be as low as 2C. Instead of being heated in the heat exchange~ described the external fluid passing through the tube 13 in heat I 1 ~7653 !
exchange relationship with the evaporator 12, such fluid may be heated in a sun collector or be supplied from a remote heating network or it may comprise subsoil water which is pumped from the ground and is re-interfiltered into the ground after having passed the evaporator in heat exchange relationship therewith.
Referring particularly to FIG 2 of the drawings the heat evaporator t2 comprises a first tube 20 which has end walls 21 and 22 and thus is completely closed against lQ the interior of the tube 13 in which the evaporator is located. A second tube 23 passes through the end wall 21 and extends into the first tube 20 substantially coaxial-ly therewith. The inner end of the second tube 23 opens at some distance from the other end wall 22. A conduit 24 connects the tube ? at the end closed by the end wall 21, to the compressor 10 at the suction side there-of, the pressure side being connected to the inlet of the condensor 11 by a conduit 25, and a conduit 26 con-nects the tube 23 to the outlet of the condensor. The condensor is arranged in heat exchange relationship with a second external fluid, such as water, which serves as a heat carrier for distributing the heat recovered in the condensor, e.g. to radiators of a central heating system in a building.
The liquid refrigerant is supplied upstreams of the external fluid passing through the tube 13 to the tube 23 and from the open end of the tube the refrigerant evaporates during absorption of heat from the external fluid and then passes through the tube 20 in the opposite 3~ flow direction to that of the liquid refrigerant in the tube 23 and the external fluid in the tube 13 to the conduit 24 in order to be sucked-in again by the compres-sor 10 and to be compressed by said compressor. The tube 23 thus forms the throttling means of the evaporator 12.
The liquid refrigerant supplied through the tube 23 is cooled by the surrounding refrigerant in the tube 20 during its flow towards the open end of the tube 23 where the refrigerant is evaporated and enters into the tube 20, and by this cooling of the refrigerant supplied the effect described above will be achieved, which means that the flow of refrigerant is adjusted to the amount of heat supplied by the external fluid in the tube 13.
In a typical embodiment of the heat pump of the invention the tube 13 has an internal diameter of about 40 mm. The said first tube 20 of the evaporator 12 has an internal diameter of about 19 mm, while the said second tube 23 has an internal diameter of 4.7 to 4.8 mm. The refrigerant is supplied to the tube 23 from the conduit 26 at a temperature of e.g. 40 to 50C and is cooled in the tube 23 to vaporizing temperature of lO to 20C.
It is not necessary that the external fluid used for supplying heat to the- evaporator 12 is a circulating fluid as in the embodiment described. A length of tube forming the outer casing of the evaporator and having a length of e.g. 15 m may be placed in the ground for heat exchange between the refrigerant and the external fluid received by the tube. In such case, the external fluid is non-circulating and consists suitably of water. When the compressor lO is operating, which may take place for some hours each 24 hours, the water in the outer casing will freeze to ice due to the fact that the refrigerant is absorbing its vaporizing heat from the water. This freezing can be admitted when the outer casing consists of a plastic tube which is flexible, thereby avoiding damage at the expansion during the freezing. During the remaining portion of the 24-hours cycle the ice will then be melted in the outer casing by the supply of ground heat from the surroundings.
Also, it is not even necessary that the evaporator ,2 is located in an outer casing. The evaporator may be submerged into the water of a sea, a lake, a river or other natural source of an external fluid suitable for the supply of evaporation heat to the evaporator. I
,
The in~ention relates to a h'eat pump comprising a compressor fQr circulating a refrigerant, an evaporator for thé evapQration of li'quid refrigerant, in heat exchange relationship with an external fluid, and a condensor for the condensation of the evaporated re- i~
frigerant.
According to the invention a heat pump of this type is characterized in that the evaporator comprises a first tube to be contacted by the external fluid at the outside thereof, which is connected at one end to the suction side of the compressor and is closed at the other end, and a second tube connected to the condensor, 1~ which extends substantially coaxially into said first tube,'from said one end thereof and opens at some distance from the other, closed end of the first tube to form the throttling means of the evaporator.
By this arrangement there is achieved not only a very simple construction of the evaporator but also an automatic adjustment of the supply of liquid refrigerant to the evaporator in dependance of the amount of heat supplied: when a small amount of heat is supplied to the e~aporator from the external fluid, a lower vapor-ization temperature is required in the evaporator, andthis is automatically achieved in the evaporator accord-ing to the inYention by the flow of liquid refrigerant being automatically reduced at decreasing temperature.
It is not known for sure what causes this effect 3~ but it is supposed that it is caused by the fact that oil entrained in the circulating refrigerant and emanat-ing from the compressor of the heat pump, is becoming increasingly Yiscous the lower the temperature of the external fluid will be, whereby the flow of liquid refrigerant thr'ough said second tube will be restrained.
-S~
Preferably said first tube is surrounded by an elongated tubular outer casing forming part of a conduit for circulating the external fluid.
The invention will be explained in more detail below, reference being made to the attached drawings in which FIG 1 is a diagrammatic view of a heat pump in accordance with the invention, and FIG 2 is a transparent perspective view of the evaporator and a tube forming an outer casing there-of, which conveys the external fluid.
The heat pump disclosed in F~G 1 comprises a com-pressor 10 which pumps a refrigerant such as freon to a condensor 11 and therefrom to an evaporator 12 which lS is more clearly disclosed in FIG 2. The evaporator is arranged inside an outer casing formed by a tube 13, which is closed at one end thereof at 14 and is connec-ted to a circulation pump 15 at the other end thereof.
A number of tubes 16 of a smaller cross section than the tube 13 are connected at one end thereof to the tube 13. They extend in parallel from the tube 13 in the transverse direction thereof and then form a bow 17 of 180 to return to the tube 13 in parallel so as to be connected at the other end thereof to another tube 18 identical with the tube 13. The tube 18 is closed at one end thereof at 19 and is connected at the other end to the circulation pump 15, which circulates an external fluid such as water through the tubes 13, 16 and 18 as indicated by arrows in the drawings. Thus, it will be seen that the tubes 13 and 18 form manifolds for the tubes 16. The tubes 13, 16 and 18 preferably are , ~ made of a highly durabc~e~an;d~flexible synthetic elasto-mer such as polyvinyl clv-rt~ (PVC) in which case they may co~prise black PVC tubes of the type used for fresh water networks, or ethylene-propylene-diene-monomer ~ 1 67653 (EPDM). It is essential that the material of the tubes is impervious to corrosion, ultraviolet light and chemi-cal deterioration and eliminates freeze-up problems.
In FIG 1 the tubes 16 are arranged in a group comprising six tubes, and a desired number of such groups of tubes may be connected to the tubes 13 and 18, a further group being fragmentarily shown at 16'.
The tubes 13, 16 and 18 form a heat exchanger for supplying heat to the evaporator 12, and this heat ex-changer may be located in the ground so that the fluidcirculated therein absorbs ground heat, or may be sus-pended in stands which are located e.g. on a garage or car port roof or on a wall or a fence, so that the fluid circulated therein absorbs air heat.
In a preferred embodiment of the heat exchanger described the tubes 16 in each group consist of an ab-sorber mat which is marketed under the registered trade mark SolaRoll and is manufactured by Bio-Energy Systems, Inc., Ellenville, New York, USA. They can be arranged in the end return configuration shown in FIG I but other configur2tions known in the art may be arranged such as the butterfly type or the grid type. A balanced flow as that shown in FIG 1 wherein the circulating fluid has the same flow direction in the tubes 13 and 18 - 25 is preferred over the unbalanced flow with opposite flow directions in said tubes.
The external fluid which has absorbed heat during the passage of the heat exchanger described passes the evaporator 12 in heat exchange relationship therewith to supply the heat necessary for the evaporation of the liquid refrigerant supplied to the evaporator. The ex-ternal fluid usually would have a temperature of 6 to 8C but the temperature may be as low as 2C. Instead of being heated in the heat exchange~ described the external fluid passing through the tube 13 in heat I 1 ~7653 !
exchange relationship with the evaporator 12, such fluid may be heated in a sun collector or be supplied from a remote heating network or it may comprise subsoil water which is pumped from the ground and is re-interfiltered into the ground after having passed the evaporator in heat exchange relationship therewith.
Referring particularly to FIG 2 of the drawings the heat evaporator t2 comprises a first tube 20 which has end walls 21 and 22 and thus is completely closed against lQ the interior of the tube 13 in which the evaporator is located. A second tube 23 passes through the end wall 21 and extends into the first tube 20 substantially coaxial-ly therewith. The inner end of the second tube 23 opens at some distance from the other end wall 22. A conduit 24 connects the tube ? at the end closed by the end wall 21, to the compressor 10 at the suction side there-of, the pressure side being connected to the inlet of the condensor 11 by a conduit 25, and a conduit 26 con-nects the tube 23 to the outlet of the condensor. The condensor is arranged in heat exchange relationship with a second external fluid, such as water, which serves as a heat carrier for distributing the heat recovered in the condensor, e.g. to radiators of a central heating system in a building.
The liquid refrigerant is supplied upstreams of the external fluid passing through the tube 13 to the tube 23 and from the open end of the tube the refrigerant evaporates during absorption of heat from the external fluid and then passes through the tube 20 in the opposite 3~ flow direction to that of the liquid refrigerant in the tube 23 and the external fluid in the tube 13 to the conduit 24 in order to be sucked-in again by the compres-sor 10 and to be compressed by said compressor. The tube 23 thus forms the throttling means of the evaporator 12.
The liquid refrigerant supplied through the tube 23 is cooled by the surrounding refrigerant in the tube 20 during its flow towards the open end of the tube 23 where the refrigerant is evaporated and enters into the tube 20, and by this cooling of the refrigerant supplied the effect described above will be achieved, which means that the flow of refrigerant is adjusted to the amount of heat supplied by the external fluid in the tube 13.
In a typical embodiment of the heat pump of the invention the tube 13 has an internal diameter of about 40 mm. The said first tube 20 of the evaporator 12 has an internal diameter of about 19 mm, while the said second tube 23 has an internal diameter of 4.7 to 4.8 mm. The refrigerant is supplied to the tube 23 from the conduit 26 at a temperature of e.g. 40 to 50C and is cooled in the tube 23 to vaporizing temperature of lO to 20C.
It is not necessary that the external fluid used for supplying heat to the- evaporator 12 is a circulating fluid as in the embodiment described. A length of tube forming the outer casing of the evaporator and having a length of e.g. 15 m may be placed in the ground for heat exchange between the refrigerant and the external fluid received by the tube. In such case, the external fluid is non-circulating and consists suitably of water. When the compressor lO is operating, which may take place for some hours each 24 hours, the water in the outer casing will freeze to ice due to the fact that the refrigerant is absorbing its vaporizing heat from the water. This freezing can be admitted when the outer casing consists of a plastic tube which is flexible, thereby avoiding damage at the expansion during the freezing. During the remaining portion of the 24-hours cycle the ice will then be melted in the outer casing by the supply of ground heat from the surroundings.
Also, it is not even necessary that the evaporator ,2 is located in an outer casing. The evaporator may be submerged into the water of a sea, a lake, a river or other natural source of an external fluid suitable for the supply of evaporation heat to the evaporator. I
,
Claims (6)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. Heat pump comprising a compressor for circulating a refrigerant, an evaporator for the evaporation of liquid refrigerant by heat exchange with an external fluid, and a condenser for the condensation of the evaporated refrigerant, wherein the evaporator comprises a first tube having two closed ends and inner and outer surfaces, the outer surface to be in contact with the external fluid, said first tube being connected generally at one end to the suction side of the compressor and being closed at the other end, and a second tube connected to the condensor, which extends substantially the length of said first tube, said second tube opening at a distance from the end of the first tube to provide the throttling means of the evaporator.
2. Heat pump as claimed in claim 1 wherein said first tube is connected to said compressor by an outlet tube attached to said first tube proximate where said second tube enters said first tube.
3. Heat pump as claimed in claim 1 wherein said first tube is surrounded by an elongated tubular outer casing receiving the external fluid.
4. Heat pump as claimed in claim 3 wherein the outer casing comprises a tube of a flexible synthetic elastomer material.
5. Heat pump as claimed in claim 1 wherein the casing is arranged as part of a conduit for circulating said external fluid therethrough.
6. Heat pump as claimed in claim 5 wherein the conduit forms a manifold for a number of tubes of a heat exchanger.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE8005384A SE424772B (en) | 1980-07-25 | 1980-07-25 | HEAT PUMP VAPOR |
| SE8005384-6 | 1980-07-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1167653A true CA1167653A (en) | 1984-05-22 |
Family
ID=20341483
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000382456A Expired CA1167653A (en) | 1980-07-25 | 1981-07-24 | Heat pump |
Country Status (15)
| Country | Link |
|---|---|
| JP (1) | JPS57501141A (en) |
| AU (1) | AU7411181A (en) |
| BE (1) | BE889732A (en) |
| CA (1) | CA1167653A (en) |
| CH (1) | CH649370A5 (en) |
| DE (1) | DE3152231A1 (en) |
| DK (1) | DK132882A (en) |
| FI (1) | FI71835C (en) |
| FR (1) | FR2487488A1 (en) |
| GB (1) | GB2102552B (en) |
| NL (1) | NL8120274A (en) |
| NO (1) | NO151869C (en) |
| SE (1) | SE424772B (en) |
| WO (1) | WO1982000511A1 (en) |
| YU (1) | YU180981A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2134236B (en) * | 1983-01-13 | 1986-03-12 | Richard William Husband | Improvements in or relating to evaporative heat exchangers |
| WO2001059385A1 (en) * | 2000-02-08 | 2001-08-16 | Hackman Wedholms Ab | A heat exchanger and use thereof |
| DE10126818A1 (en) * | 2001-06-01 | 2002-12-05 | Bsh Bosch Siemens Hausgeraete | Evaporator for refrigerator has coolant channel fed between two side walls, at least one made of flexurally weak plastic foil material, coolant channel is made from pipeline |
| JP2009257692A (en) * | 2008-04-18 | 2009-11-05 | Calsonic Kansei Corp | Double pipe heat exchanger |
| KR101387854B1 (en) | 2011-09-07 | 2014-05-07 | 엘지전자 주식회사 | An air conditioner |
| CN106969397B (en) * | 2017-05-04 | 2022-06-17 | 奥特朗电器（广州）有限公司 | Low-temperature heat pump heating unit with efficient defrosting system |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT294148B (en) * | 1967-09-06 | 1971-11-10 | Danfoss As | Forced through evaporator for a compression refrigeration system |
| FR1548499A (en) * | 1967-10-23 | 1968-12-06 | ||
| BE755566A (en) * | 1969-09-03 | 1971-02-15 | Ostro John D B | HEAT EXCHANGER |
| FR2296828A2 (en) * | 1974-12-31 | 1976-07-30 | Vignal Maurice | Heat pump using ground as source - has vapouriser vessel separating gaseous and liquid phases of expanded medium |
| SE394025B (en) * | 1975-09-30 | 1977-05-31 | Alfa Laval Ab | BAPTISM COOLER |
| DE7712095U1 (en) * | 1977-04-19 | 1977-10-13 | Hutzelmeier, Franz, 6231 Schwalbach | LIQUID COOLER FOR CONNECTION TO A COOLING MACHINE |
-
1980
- 1980-07-25 SE SE8005384A patent/SE424772B/en not_active IP Right Cessation
-
1981
- 1981-07-17 JP JP56502433A patent/JPS57501141A/ja active Pending
- 1981-07-17 DE DE813152231T patent/DE3152231A1/en not_active Withdrawn
- 1981-07-17 AU AU74111/81A patent/AU7411181A/en not_active Abandoned
- 1981-07-17 GB GB08223843A patent/GB2102552B/en not_active Expired
- 1981-07-17 CH CH1789/82A patent/CH649370A5/en not_active IP Right Cessation
- 1981-07-17 NL NL8120274A patent/NL8120274A/nl unknown
- 1981-07-17 WO PCT/SE1981/000219 patent/WO1982000511A1/en active IP Right Grant
- 1981-07-22 YU YU01809/81A patent/YU180981A/en unknown
- 1981-07-24 BE BE2/59279A patent/BE889732A/en not_active IP Right Cessation
- 1981-07-24 FR FR8114445A patent/FR2487488A1/en active Granted
- 1981-07-24 CA CA000382456A patent/CA1167653A/en not_active Expired
-
1982
- 1982-03-19 FI FI820972A patent/FI71835C/en not_active IP Right Cessation
- 1982-03-24 NO NO820978A patent/NO151869C/en unknown
- 1982-03-24 DK DK132882A patent/DK132882A/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| FI71835B (en) | 1986-10-31 |
| FI71835C (en) | 1987-02-09 |
| DK132882A (en) | 1982-03-24 |
| NO151869C (en) | 1985-06-19 |
| WO1982000511A1 (en) | 1982-02-18 |
| BE889732A (en) | 1981-11-16 |
| FI820972L (en) | 1982-03-19 |
| NO151869B (en) | 1985-03-11 |
| FR2487488A1 (en) | 1982-01-29 |
| AU7411181A (en) | 1982-03-02 |
| GB2102552B (en) | 1984-08-22 |
| CH649370A5 (en) | 1985-05-15 |
| NO820978L (en) | 1982-03-24 |
| SE8005384L (en) | 1982-01-26 |
| SE424772B (en) | 1982-08-09 |
| GB2102552A (en) | 1983-02-02 |
| DE3152231A1 (en) | 1983-01-13 |
| FR2487488B1 (en) | 1985-04-12 |
| JPS57501141A (en) | 1982-07-01 |
| YU180981A (en) | 1984-02-29 |
| NL8120274A (en) | 1982-11-01 |
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