US20040026071A1 - Heat exchanger for a co2 vehicle air conditioner - Google Patents
Heat exchanger for a co2 vehicle air conditioner Download PDFInfo
- Publication number
- US20040026071A1 US20040026071A1 US10/239,048 US23904802A US2004026071A1 US 20040026071 A1 US20040026071 A1 US 20040026071A1 US 23904802 A US23904802 A US 23904802A US 2004026071 A1 US2004026071 A1 US 2004026071A1
- Authority
- US
- United States
- Prior art keywords
- heat exchanger
- heat transfer
- recited
- heat
- pressure side
- 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.)
- Abandoned
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 22
- 239000000463 material Substances 0.000 claims description 12
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 4
- 229910052802 copper Inorganic materials 0.000 claims description 4
- 239000010949 copper Substances 0.000 claims description 4
- 229910052782 aluminium Inorganic materials 0.000 claims description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 3
- 239000010935 stainless steel Substances 0.000 claims description 3
- 229910001220 stainless steel Inorganic materials 0.000 claims description 3
- 229910000881 Cu alloy Inorganic materials 0.000 claims description 2
- 238000004519 manufacturing process Methods 0.000 claims description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 12
- 229910002092 carbon dioxide Inorganic materials 0.000 description 10
- 239000002826 coolant Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 231100000252 nontoxic Toxicity 0.000 description 1
- 230000003000 nontoxic effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000005476 soldering Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
-
- 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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
Abstract
A heat exchanger is described, having a first channel through which a stream of refrigerant flows on the high pressure side in a first direction, and a second channel, separate from the first channel, through which refrigerant flows on the low pressure side in a second direction opposite the first direction, wherein the first and second channels each have a large number of small channels (11, 12, 13, . . . ) formed in or on individual heat transfer plates (1, 2, 3, . . . ), and a plurality of layers of the heat transfer plates are soldered or welded together.
Description
- The present invention relates to a heat exchanger having a first channel through which a stream of refrigerant flows on the high pressure side and a second channel, separate from the first channel, through which refrigerant flows on the low pressure side.
- A heat exchanger of this sort is known in one application as an inner heat exchanger of a CO2 vehicle air conditioner from Status Report No. 20 of the Deutscher Kälte-und Klimatechnischer Verein [German Refrigeration and Air Conditioning Association]: “Kohlendioxid—Besonderheiten und Einsatzchancen als Kältemittel” [Carbon dioxide-characteristics and prospects for use as a refrigerant], page 137 (November 1998).
- The interest in natural refrigerants as an alternative to CFC is increasing, as an outgrowth of the rules and regulations for eliminating the use of CFC.
- The range of natural refrigerants includes carbon dioxide, which is non-combustible and nontoxic. Research on carbon dioxide, which was first used as a refrigerant in 1866 but disappeared from use in the nineteen-fifties, experienced a renaissance in the eighties through the work of Lorentzen and his associates. Future fields of use are vehicle air conditioning, heat pumps, transportable air conditioners of small capacity, air dehumidifiers, and dryers.
- To increase the performance and efficiency of the CO2 process, an inner or internal heat exchanger has been proposed. The internal heat exchanger has refrigerant (CO2) flowing through it. First, it flows through on the way from the gas cooler to the evaporator, and the second time between the evaporator and the compressor. The main task of the internal heat exchanger is to enable additional cooling by the internal heat exchanger at times when ambient temperatures are high, where the gas cooler consequently is not able to cool the refrigerant sufficiently prior to expansion. The flow of heat passes from the high pressure side, downstream from the gas cooler, to the low pressure side, downstream from the evaporator (before entering the compressor). The refrigerant, still partially liquid on the suction side, then vaporizes completely before reaching the compressor. The internal heat exchanger is practically designed as a counterflow heat exchanger.
- The internal heat exchanger known from the status report of the Deutscher kälte-und klimatechnischer Verein mentioned above is manufactured at present for example as a counterflow double-pipe heat exchanger. The pipe profile is made of extruded aluminum. On the high pressure side the refrigerant flows through the inner pipe, for reasons of strength. A difficulty here is the dimensioning of the heat transfer surface or cross-sectional area of flow on the suction side in order to achieve a satisfactory heat transfer coefficient together with an acceptable drop in pressure of the refrigerant.
- An object of the present invention is to specify a small, compact heat exchanger in which a very large heat transferring area is realizable in a small volume, which is suitable for use as an inner heat exchanger in a CO2 air conditioner.
- Because according to a significant aspect of the present invention the first and second channels are each formed from a large number of small channels located in or on individual heat transfer plates, and because a plurality of layers of the heat transfer plates are joined together, for example by soldering or welding, a heat exchanger of this sort may be made very compact, i.e., having a very small volume, and at the same time with a large heat transferring area. Because of the large number of small channels and the design and manner of operation of the heat exchanger using the counterflow principle, it is possible to improve the transfer of heat compared to the known implementation while keeping the pressure drop at an acceptable level.
- Because of the large number of small channels, the heat transferring area may be increased significantly.
- It is preferable that the hydraulic diameter of the small channels be chosen such that the product of the heat transfer coefficient and the heat transferring area on the high pressure side corresponds to the product of the heat transfer coefficient and the heat transferring area on the low pressure side.
- Alternatively or in addition, the flow path may be chosen, for example by routing the small channels in a zigzag pattern, so that the product of the heat transfer coefficient and the heat transferring area on the high pressure side corresponds to the product of the heat transfer coefficient and the heat transferring area on the low pressure side.
- Because the channels are produced on or in the plates using a manufacturing process that removes or builds up material, the channels—that is, the channel diameters—may be made very small in conformity with the operating pressure conditions.
- Because of its compact design, the proposed heat exchanger may be used for very high pressures up to around 150 bar.
- FIG. 1 in a first embodiment shows the structure and flow conditions of a heat exchanger according to the present invention, made up of individual layers of sheet metal.
- FIG. 2 shows a first arrangement of a compact heat exchanger.
- FIG. 3 shows a second arrangement of a compact heat exchanger.
- FIG. 4 shows a third arrangement of a compact heat exchanger.
- The embodiment of a heat exchanger according to the present invention depicted in FIG. 1 is very compact because of the fact that individual lamellar
heat transfer plates cover plates 8, 9, havesmall channels flow orifices inlet orifice 14 of left cover plate 8 (arrow EH) flows through flow orifice 4 of the left heat transfer plate to middleheat transfer plate 2, downward through the latter'schannels 12 in the direction of the arrow, and from there again flows to the left throughflow orifice 6 of first heat transfer plate 1 and out throughoutlet orifice 16 of cover plate 8 (arrow AH). In addition, as indicated by the hatched arrows, low pressure CO2 (arrow EN) flows into aninlet orifice 15 of left cover plate 8, throughchannels 11 of first heat transfer plate 1 from bottom to top, continuing throughflow orifice 5 of secondheat transfer plate 2 to thirdheat transfer plate 3 and there also through the latter'ssmall channels 13 from bottom to top and through thecorresponding flow orifices 7 of third, second, and firstheat transfer plates outlet orifice 17 of left cover plate 8 (arrow AN). - In this way, the depicted heat exchanger has refrigerant on the high pressure side (black arrows) flowing through it in a first direction, and refrigerant on the low pressure side (hatched arrows) flowing through it in a counterflow.
- The structure of the heat exchanger depicted in the figure, having only three
heat transfer plates - The heat exchanger shown in FIG. 1 is thus made up of individual layers defined by the heat transfer plates, having CO2 flowing through them in counterflow on the one side at high pressure (up to nearly 150 bar) and high temperature, and on the other side at low pressure (up to approximately 60 bar) and low temperature.
- To adapt the heat exchanger ideally to the occurring heat transfer conditions, allowance is made for the fact that the heat transfer is determined by the material properties of the fluid and by the flow condition. However, the heat transfer coefficient on the low pressure side is generally significantly smaller than that on the high pressure side. To utilize the volume of the heat exchanger most efficiently, an effort should therefore be made to match the product of the heat transfer coefficient and the heat transferring area on the high pressure side to the product of the heat transfer coefficient and the heat transferring area on the low pressure side. This may be done in the compact heat exchanger shown, which is made up of individual profiles, i.e.,
heat transfer plates small channels small channels - The possibility also exists of increasing the heat transferring area, i.e., the heat transfer coefficient, by appropriate routing of the flow of the small channels, for example in a zigzag shape.
- A compact heat exchanger of the sort depicted in the figure may be manufactured advantageously of copper or copper alloy, stainless steel, aluminum, and other materials.
- The exemplary embodiment of a heat exchanger according to the present invention described above may be used advantageously as an inner heat exchanger in a CO2 air conditioner in vehicles, in particular in motor vehicles.
- Here, an inner heat exchanger having the structure described above and the stated flow conditions may be designed for high pressures up to approximately 150 bar.
- In this case, the first (high pressure) flow channel, marked in FIG. 1 by black arrows, lies in a first flow path from a gas cooler to an evaporator, and the second (low pressure) flow channel, marked by hatched arrows in the figure, lies in a second flow path from the evaporator to a compressor of the vehicle air conditioner.
- In the first flow path a high pressure up to approximately 150 bar and a high temperature may prevail, and in the second flow path a low pressure up to approximately 60 bar and a relatively low temperature may prevail.
- To those skilled in the relevant art it will have become clear on the basis of the above description that the heat exchanger depicted in FIG. 1 is merely schematic and exemplary, and that another geometry which differs from a lamellar shape of the heat transfer plates, such as a cylindrical structure, may be implemented.
- In the embodiment according to FIG. 2, there are in first heat transfer plate1, for example, two
small channels 11 though which the coolant flows on the low pressure side. The approximately U-shaped cross section ofsmall channels 11 is closed by secondheat transfer plate 2, so that the coolant cannot escape. To attach the twoheat transfer plates 1, 2 to each other, aconnection 20 is provided, for example a soldered connection.Small channels 12 through which coolant flows on the high pressure side are located exactly above each ofsmall channels 11 of the low pressure side, but on the side of secondheat transfer plate 2 which faces away from first heat transfer plate 1. The long side ofsmall channels 12 of the high pressure side might be closed by an additionalheat transfer plate 3 which is not shown in FIG. 2. The coolant flows throughsmall channels - The heat exchanger in FIG. 2 may be made even more compact according to the arrangement in FIG. 3, by positioning the orifices of
small channels 11 of the low pressure side at an offset from the orifices ofsmall channels 12 with the flow from the high pressure side. Afirst bridge 22 of first heat transfer plate 1 which lies between the two orifices ofsmall channels 11 is now exactly opposite the orifice of asmall channel 12 with the flow from the high pressure side, in such a way that it absorbs the forces produced by the pressure difference inchannels small channels 11 on the low pressure side are offset fromsmall channels 12 on the high pressure side in tiers with different pressure levels, it is possible to reduce the requisite thickness ofheat transfer plates 1, 2. This is achieved by having more of the forces produced by the pressure difference inchannels bridge 22 between the orifices. This measure makes it possible to reduce the volume and in particular the mass of the heat exchanger significantly. This is especially important for materials of great density which also have great strength. Through this mass-reducing measure it is now possible also to use materials of great density, since the mass of the heat exchanger is no longer determined only by the density of the material, but also by the density of the fluid which is insmall channels - In the embodiment according to FIG. 4,
second bridge 24 is reduced in comparison tofirst bridge 22 of the embodiment according to FIG. 3, to the point where the stresses caused by the pressure differences in the bridges are of exactly such a magnitude that the permissible stresses of the particular material are not exceeded. The orifices ofsmall channels 11 are again positioned at an offset from the orifices ofsmall channels 12. The embodiment according to FIG. 4 makes it possible to design the heat exchanger even more compactly. - The thickness of
heat transfer plates 1, 2 might vary in the range between 600 and 1000 μm, the dimensions ofsmall channels bridges
Claims (15)
1. A heat exchanger having a first channel through which a stream of refrigerant flows on the high pressure side and a second channel, separate from the first channel, through which refrigerant flows on the low pressure side,
wherein the first and second channels each have a large number of small channels (11, 12, 13, . . . ) formed in or on individual heat transfer plates (1, 2, 3, . . . ), and a plurality of layers of the heat transfer plates are joined together.
2. The heat exchanger as recited in claim 1 ,
wherein the small channels conduct the flow in such a way that the refrigerant stream on the high pressure side and the refrigerant stream on the low pressure side flow through the heat exchanger according to the counterflow principle.
3. The heat exchanger as recited in claim 1 or 2,
wherein the heat transfer plates are of a lamellar shape.
4. The heat exchanger as recited in one of the preceding claims,
wherein the refrigerant on the high pressure and low pressure sides is CO2.
5. The heat exchanger as recited in one of claims 1 through 4,
wherein the hydraulic diameter of the small channels (11, 12, 13, . . . ) is chosen such that the product of the heat transfer coefficient and the heat transferring area on the high pressure side corresponds to the product of the heat transfer coefficient and the heat transferring area on the low pressure side.
6. The heat exchanger as recited in one of the preceding claims,
wherein the manner in which the small channels conduct the flow is chosen such that the product of the heat transfer coefficient and the heat transferring area on the high pressure side corresponds to the product of the heat transfer coefficient and the heat transferring area on the low pressure side.
7. The heat exchanger as recited in claim 6 ,
wherein the small channels are routed in a zigzag pattern in or on the heat transfer plates.
8. The heat exchanger as recited in one of the preceding claims,
wherein the material of the heat transfer plates (1, 2, 3) is chosen from a group which includes copper and copper alloy, stainless steel, aluminum, and additional materials.
9. The heat exchanger as recited in one of the preceding claims,
wherein the small channels are produced in or on the heat transfer plates using a manufacturing process that removes or builds up material.
10. The heat exchanger as recited in one of the preceding claims, wherein the lamellar heat transfer plates are enclosed between two opposing cover plates (8, 9), of which the first cover plate (8) has inlet and outlet orifices (14, 15, 16, 17) in each case for refrigerant on both the high pressure and low pressure sides.
11. Use of the heat exchanger as recited in one of the preceding claims as an inner heat exchanger in a CO2 air conditioner in vehicles, in particular in motor vehicles.
12. The use as recited in claim 11 ,
wherein the inner heat exchanger is designed for high pressures of the CO2 refrigerant up to approximately 150 bar.
13. The use as recited in claim 11 or 12,
wherein CO2 flows through the first channel of the inner heat exchanger in a first flow path from a gas cooler to an evaporator and through the second channel in a second flow path from the evaporator to a compressor of the vehicle air conditioner.
14. The use as recited in one of claims 11 through 13,
wherein in the first flow path a high pressure up to approximately 150 bar and a high temperature prevail, and in the second flow path a low pressure up to approximately 60 bar and a lower temperature prevail.
15. The heat exchanger as recited in one of the preceding claims,
wherein the small channels (11) of the first heat transfer plate (1) are positioned at an offset from the small channels (12) of the second heat transfer plate (2).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10012957 | 2000-03-16 | ||
DE10110828A DE10110828A1 (en) | 2000-03-16 | 2001-03-06 | Heat exchanger for carbon dioxide air-conditioning unit in vehicle; has separate channels for high and low pressure refrigerant flow each with several small channels formed in heat exchanger sheets |
PCT/DE2001/000887 WO2001069157A2 (en) | 2000-03-16 | 2001-03-09 | Heat exchanger for a co2 vehicle air conditioner |
Publications (1)
Publication Number | Publication Date |
---|---|
US20040026071A1 true US20040026071A1 (en) | 2004-02-12 |
Family
ID=26004867
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/239,048 Abandoned US20040026071A1 (en) | 2000-03-16 | 2001-03-09 | Heat exchanger for a co2 vehicle air conditioner |
Country Status (4)
Country | Link |
---|---|
US (1) | US20040026071A1 (en) |
EP (1) | EP1272804A2 (en) |
JP (1) | JP2004508525A (en) |
WO (1) | WO2001069157A2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030120633A1 (en) * | 2001-11-13 | 2003-06-26 | Torre-Bueno Jose De La | System for tracking biological samples |
US20050155749A1 (en) * | 2004-01-20 | 2005-07-21 | Memory Stephen B. | Brazed plate high pressure heat exchanger |
US20050194123A1 (en) * | 2004-03-05 | 2005-09-08 | Roland Strahle | Plate heat exchanger |
US20150153113A1 (en) * | 2013-12-03 | 2015-06-04 | International Business Machines Corporation | Heat sink with air pathways through the base |
US10155428B2 (en) | 2014-12-24 | 2018-12-18 | Denso Corporation | Refrigeration cycle device |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10160380A1 (en) * | 2001-12-10 | 2003-06-18 | Bosch Gmbh Robert | Heat transmission device has coolant as high pressure fluid and liquid heat-carrier as low pressure fluid |
WO2009123517A1 (en) | 2008-04-04 | 2009-10-08 | Alfa Laval Corporate Ab | A plate heat exchanger |
JP5855611B2 (en) * | 2013-07-11 | 2016-02-09 | アルファ ラヴァル コーポレイト アクチボラゲット | Plate heat exchanger |
JP5749786B2 (en) * | 2013-11-28 | 2015-07-15 | 株式会社前川製作所 | Heat exchanger |
JP5847913B1 (en) * | 2014-11-06 | 2016-01-27 | 住友精密工業株式会社 | Heat exchanger |
KR102146101B1 (en) * | 2018-09-21 | 2020-08-20 | 두산중공업 주식회사 | Printed circuit heat exchanger and heat exchanging device comprising it |
KR102073625B1 (en) * | 2018-09-18 | 2020-02-05 | 두산중공업 주식회사 | Printed circuit heat exchanger and heat exchanging device comprising it |
US11333448B2 (en) | 2018-09-18 | 2022-05-17 | Doosan Heavy Industries & Construction Co., Ltd. | Printed circuit heat exchanger and heat exchange device including the same |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6044655A (en) * | 1996-08-22 | 2000-04-04 | Denso Corporation | Vapor compression type refrigerating system |
US6321544B1 (en) * | 1998-10-08 | 2001-11-27 | Zexel Valeo Climate Control Corporation | Refrigerating cycle |
US20040011515A1 (en) * | 2002-06-24 | 2004-01-22 | Hitoshi Matsushima | Plate type heat exchanger |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0136481A3 (en) * | 1983-10-03 | 1986-02-26 | Rockwell International Corporation | Stacked plate/fin-type heat exchanger |
FR2679021B1 (en) * | 1991-07-12 | 1999-02-12 | Const Aero Navales | PLATE HEAT EXCHANGER. |
US6907921B2 (en) * | 1998-06-18 | 2005-06-21 | 3M Innovative Properties Company | Microchanneled active fluid heat exchanger |
DE19832480A1 (en) * | 1998-07-20 | 2000-01-27 | Behr Gmbh & Co | Vehicle air conditioning system with carbon dioxide working fluid is designed for limited variation in efficiency over a given range of high pressure deviation, avoiding need for controls on high pressure side |
-
2001
- 2001-03-09 WO PCT/DE2001/000887 patent/WO2001069157A2/en active Application Filing
- 2001-03-09 US US10/239,048 patent/US20040026071A1/en not_active Abandoned
- 2001-03-09 EP EP01921169A patent/EP1272804A2/en not_active Withdrawn
- 2001-03-09 JP JP2001568001A patent/JP2004508525A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6044655A (en) * | 1996-08-22 | 2000-04-04 | Denso Corporation | Vapor compression type refrigerating system |
US6321544B1 (en) * | 1998-10-08 | 2001-11-27 | Zexel Valeo Climate Control Corporation | Refrigerating cycle |
US20040011515A1 (en) * | 2002-06-24 | 2004-01-22 | Hitoshi Matsushima | Plate type heat exchanger |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20030120633A1 (en) * | 2001-11-13 | 2003-06-26 | Torre-Bueno Jose De La | System for tracking biological samples |
US20050155749A1 (en) * | 2004-01-20 | 2005-07-21 | Memory Stephen B. | Brazed plate high pressure heat exchanger |
US7343965B2 (en) | 2004-01-20 | 2008-03-18 | Modine Manufacturing Company | Brazed plate high pressure heat exchanger |
US20050194123A1 (en) * | 2004-03-05 | 2005-09-08 | Roland Strahle | Plate heat exchanger |
US7600559B2 (en) | 2004-03-05 | 2009-10-13 | Modine Manufacturing Company | Plate heat exchanger |
US20150153113A1 (en) * | 2013-12-03 | 2015-06-04 | International Business Machines Corporation | Heat sink with air pathways through the base |
US10155428B2 (en) | 2014-12-24 | 2018-12-18 | Denso Corporation | Refrigeration cycle device |
Also Published As
Publication number | Publication date |
---|---|
WO2001069157A3 (en) | 2002-10-31 |
EP1272804A2 (en) | 2003-01-08 |
WO2001069157A2 (en) | 2001-09-20 |
JP2004508525A (en) | 2004-03-18 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HESSE, ULLRICH;LEUTHNER, STEPHAN;BEIL, PETRA;REEL/FRAME:013610/0598;SIGNING DATES FROM 20021106 TO 20021125 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |