EP3204709A1 - Verfahren zur montage einer wärmetauschereinrichtung und wärmetauschereinrichtung - Google Patents
Verfahren zur montage einer wärmetauschereinrichtung und wärmetauschereinrichtungInfo
- Publication number
- EP3204709A1 EP3204709A1 EP15774640.5A EP15774640A EP3204709A1 EP 3204709 A1 EP3204709 A1 EP 3204709A1 EP 15774640 A EP15774640 A EP 15774640A EP 3204709 A1 EP3204709 A1 EP 3204709A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- tubular jacket
- refrigerant
- exchanger device
- covers
- 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.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims abstract description 28
- 239000003507 refrigerant Substances 0.000 claims description 61
- 239000012530 fluid Substances 0.000 claims description 27
- 238000005057 refrigeration Methods 0.000 claims description 17
- 239000002826 coolant Substances 0.000 abstract 2
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 27
- 230000002349 favourable effect Effects 0.000 description 11
- 239000007788 liquid Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 239000007791 liquid phase Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
Classifications
-
- 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
- F25B21/00—Machines, plants or systems, using electric or magnetic effects
- F25B21/02—Machines, plants or systems, using electric or magnetic effects using Peltier effect; using Nernst-Ettinghausen effect
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
- F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
- F28F9/0224—Header boxes formed by sealing end plates into covers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2220/00—Closure means, e.g. end caps on header boxes or plugs on conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2275/00—Fastening; Joining
- F28F2275/12—Fastening; Joining by methods involving deformation of the elements
Definitions
- the invention relates to a method for mounting a heat exchanger device of a refrigeration system according to the preamble of claim 1. Furthermore, the invention relates to a heat exchanger device produced by this method.
- Such heat exchanger devices are used in refrigeration systems, in particular in refrigeration systems of an air conditioning system, for example a vehicle air conditioning system.
- the efficiency of the refrigeration system in particular when using CO 2 (R744) as a refrigerant, can be improved.
- the heat exchanger device By means of the heat exchanger device, the low temperature level of the low-pressure region of the refrigeration circuit can be used to further cool the warmer refrigerant in the high-pressure region immediately after the gas cooler.
- the heat exchanger device can be combined with a refrigerant collecting container (accumulator).
- accumulator refrigerant collecting container
- an internal heat exchanger with accumulator for refrigerant circuits in particular in motor vehicle air conditioners, known, comprising a housing of a pressure-bearing tubular cylinder jacket and a cover plate and a bottom plate, concentrically forming a gap in the housing arranged accumulator from a bad Heat conductive material, preferably made of plastic, for the liquid refrigerant at low pressure and a finned tube for the refrigerant at high pressure, which is helically arranged in the gap between the accumulator and the cylinder jacket.
- a bad Heat conductive material preferably made of plastic
- the cover plate and the bottom plate each have a connection plate Connections for refrigerant pipes, wherein in the accumulator a U-shaped suction tube with a steam inlet and a steam outlet for the refrigerant vapor and in the upper region of the accumulator a baffle device for the separation of the liquid and vapor phase of the refrigerant are provided.
- the steam inlet is protected from refrigerant liquid under the baffle device in the accumulator and the steam outlet outside the accumulator.
- the finned tube in turn is sealed at its ends via a thread in the cover plate and the bottom plate, whereby an internal heat exchanger with accumulator is to be provided, which can be produced cost-effectively.
- the invention has for its object to provide a heat exchanger device that combines an internal heat exchanger with a refrigerant tank and their installation is simplified.
- the invention is based on the general idea to mount a housing of the heat exchanger device last, whereby the assembly of heat exchanger coil and refrigerant receiver is easier.
- the heat exchanger coil is pushed over the refrigerant collecting tank and fluidly connected to the at least one lid, pushed the rohrformige jacket over the heat exchanger coil and the rohrformige jacket deformed radially inwardly.
- the assembly and the connection between the at least one lid and the heat exchanger coil are easy, since the rohrformige jacket of the housing does not obstruct access to the heat exchanger coil.
- the connection of the refrigerant collecting tank to the at least one lid and to the heat exchanger coil is accordingly simplified.
- the housing of the heat exchanger device has two covers, the heat exchanger coil is pushed over the refrigerant receiver and fluidly connected to the two covers, the rohrformige jacket is pushed over at least one of the two covers and the heat exchanger coil, and then the rohrformige jacket radially to is deformed inside.
- the flow paths in the heat exchanger device can be simplified. After mounting the heat exchanger coil and the refrigerant collecting container with the two covers then the rohrformige jacket is pushed over at least one of the two covers and deformed radially inwardly.
- the sheath must fit over at least one of the two lids, it may still have a smaller functional diameter after being deformed radially inwardly.
- the assembly of the heat exchanger device can be improved without affecting the function of the heat exchanger device.
- a helical sealing surface is formed, which delimits a, in particular helical, fluid channel between the refrigerant receiver and the tubular jacket.
- the helical fluid channel thereby extends the residence time in the heat exchanger device and thereby improves the heat exchange.
- the tubular jacket is deformed radially inwardly hydraulically or pneumatically.
- a hydraulic or pneumatic deformation process causes a uniform force on the tubular shell and thus a uniform deformation process. Such a deformation process can be flexibly applied to different components, whereby tool costs can be reduced.
- a particularly advantageous solution provides that the tubular jacket is deformed radially inwardly by means of a molding tool.
- the deformation can be accurately controlled. In particular, it can be better ensured in this way that the tubular jacket rests against the heat exchanger coil, without damaging them.
- tubular jacket is deformed more radially inwardly in the region of the heat exchanger coil than in the region of the lid. In this way, the advantages of the solution according to the invention can be exploited particularly favorable.
- tubular jacket is deformed more radially inward in the region of the heat exchanger coil than in the region of the at least one cover.
- a further advantageous possibility provides that before the sliding of the tubular jacket of the refrigerant collecting container is connected to the two lids.
- the advantages according to the invention can also be utilized in the connection of the refrigerant collecting container with the two lids.
- a favorable alternative provides that, prior to deforming the rohrformigen shell this is at least tightly connected to the at least one lid. In this way, the lid and the tubular jacket can form a fluid-tight housing.
- any type of connection between the cover and the rohrformigen coat can be used.
- Another favorable alternative provides that prior to deforming the rohrformigen shell this is at least tightly connected to both lids. In this way, the two covers and the tubular jacket can form a fluid-tight housing. Furthermore, any type of connection between the two covers and the rohrformigen coat can be used.
- tubular shell is at least tightly connected to the at least one cover by the deformation of the tubular jacket.
- the tubular jacket and the at least one cover form a fluid-tight housing, without having to provide further connection means.
- a further favorable alternative provides that the tubular jacket is at least tightly connected to both lids by the deformation of the tubular jacket.
- the tubular jacket and the two covers form a fluid-tight housing, without having to provide any further connection means.
- a heat exchanger device of a refrigeration system with a housing having at least a lid and a rohrformigen jacket, with a heat exchanger coil and a refrigerant receiver, wherein the tubular jacket is connected to the at least one lid, and wherein the tubular jacket in one Rich between two ends of the tubular shell is at least unilaterally tapered.
- tapered in a region is understood to mean that the article in this region has a smaller diameter, in particular inner diameter, than in any other region of the article.
- An advantageous variant provides that an inner diameter of the tubular shell in a region between two axial ends of the tubular shell is smaller than an inner diameter of the tubular shell on at least one of the two axial ends of the tubular shell.
- the housing of the heat exchanger device has two covers, when the tubular jacket is connected to the two covers, and if the shell-shaped jacket is tapered at least on one side in a region between the two covers.
- This configuration enables a heat exchanger device with two lids to be assembled according to the above method, so that the advantages of the method described above also extend to the heat exchanger device.
- the above-mentioned embodiment of the heat exchanger device allows almost any type of connection between the rohrformigen coat and the two covers, since the junction is easily accessible.
- a further advantageous variant provides that the inner diameter of the tubular jacket in a region between two axial ends of the tubular jacket is smaller than the inner diameter of the tubular jacket at both axial ends of the tubular jacket.
- a favorable solution provides that the tubular jacket is in contact with at least one of the two covers or with the at least one cover exclusively with an inner side of the tubular jacket.
- the corresponding lid can be made simpler.
- the outside of the rohrformigen coat can be carried out regardless of restrictions by the connectability to the lid. Thus, costs can be saved.
- a particularly favorable possibility provides that a refrigerant or a heat exchanger fluid, in particular under high pressure, is passed through the heat exchanger coils, and that the heat exchanger coil surrounds the refrigerant receiver at least in sections in a helical manner.
- a second fluid passage which is different from the fluid passage within the heat exchanger coil, is formed.
- this fluid passage is formed between the refrigerant receiver and the tubular jacket. Due to the helical course of the heat exchanger coil has this Fluid passage also a helical course. So that the heat exchanger coil and this fluid passage are guided within the heat exchanger unit a relatively long distance to each other. Thereby, heat can be exchanged particularly well between the fluid flowing in the heat exchanger coil and fluid flowing in the fluid passage.
- the at least one cover or both covers have an outer diameter which is larger than an inner diameter of the tubular shell in a region between axial ends of the tubular shell.
- the two covers have a large cross-sectional area that can be used to attach refrigerant inlets and outlets and / or attachment means.
- a particularly advantageous alternative provides that at least one of the two covers has an outer diameter which is smaller than an inner diameter of the tubular jacket before deforming the same. Thereby, the rohrformige jacket can be pushed over this cover, so that it is possible first to connect the heat exchanger coil, the refrigerant tank and the two covers together and then postpone the tubular jacket and connect with the remaining components.
- FIG. 1 is a schematic diagram of a refrigeration system
- FIG. 2 is a sectional view through a heat exchanger device during assembly and before a tubular jacket is pushed
- FIG. 3 shows a sectional view of the heat exchanger device from FIG. 2, with the tubular jacket pushed on
- FIG. 4 shows a sectional view of the heat exchanger device from FIG. 3 after a deformation of the tubular jacket
- FIG. 5 is a sectional view of the heat exchanger device with arrows for identifying the refrigerant flow
- Fig. 6 is a perspective view of a heat exchanger coil
- Fig. 7 is an illustration of two possible cross-sections of a tube of
- FIG. 8 shows an illustration of two further possible cross sections of a tube of the heat exchanger coil.
- a refrigeration system 10 shown schematically in FIG. 1 comprises a compressor 12, a gas cooler 14, a heat exchanger device 16, a throttle or an expansion valve 18 and an evaporator 20.
- the refrigeration system 10 operates on the known principle of the refrigeration cycle.
- a refrigerant 22 passes through a circuit 28 which is driven by the compressor 12. First, the refrigerant 22 is compressed in the compressor 12, whereby the temperature of the refrigerant 22 increases. From the compressor 12, the refrigerant 22 is passed into the gas cooler 14, where it can give off heat due to the increased by the compression temperature heat to the environment.
- the refrigerant 22 is passed, via an internal heat exchanger 30, to the throttle / expansion valve 18, which throttles the flow of the refrigerant 22 and separates a low pressure area 24 from a high pressure area 26.
- the throttle / expansion valve 18 throttles the flow of the refrigerant 22 and separates a low pressure area 24 from a high pressure area 26.
- the refrigerant 22 flows into the evaporator 20, in which it expands and thereby cools. Due to the fact that the refrigerant 22 in the high-pressure region 26 can deliver heat to the environment, the temperature of the refrigerant 22 in the evaporator 20 is lower than it was when the refrigerant 22 entered the compressor 12.
- the evaporator 20 has a second flow path for a medium to be cooled. medium, such as air, so that the refrigeration system 10 can absorb heat from the medium to be cooled.
- a refrigerant collecting tank 32 is arranged, from which the refrigerant 22 is conducted to the compressor 12 via the internal heat exchange
- the refrigerant used is 22 CO 2 (R744).
- the use of the internal heat exchanger 30 is favorable for the efficiency of the refrigeration system 10.
- About the inner heat exchanger 30 is heat from the refrigerant 22 in the high-pressure region 26, in particular downstream of the gas cooler 14, to the refrigerant 22 in the low pressure region 24, in particular downstream of the throttle / expansion valve 18 transmitted. Thereby, the temperature of the refrigerant 22 at the / the throttle / expansion valve 18 can be further reduced, so that the efficiency of the refrigeration system 10 improves.
- the refrigeration system 10, the heat exchanger device 16 according to the invention which includes the inner heat exchanger 30 and the refrigerant collecting tank 32. Both are arranged in a housing 34 which has at least one, for example two, cover 36 and a tubular jacket 38. Within the housing 34 extend two fluid channels.
- a first fluid idkanal 40 is formed by the inner heat exchanger 30, in particular by a heat exchanger coil 42 of the inner heat exchanger 30.
- a second fluid channel 44 extends within the housing 34 and thereby passes through the refrigerant collecting tank 32 and through a region between the refrigerant collecting tank 32 and the tubular shell 38. In this area also runs the heat exchanger coil 42 of the inner heat exchanger 30 (see FIG. 5).
- the two fluid channels 40, 44 are connected such that in the region between the refrigerant collecting tank 32 and the tubular jacket 38, the two fluid channels 40, 44 are traversed in countercurrent, and so the heat can be transmitted from the one fluid channel to the other fluid channel particularly effective ,
- the first fluid channel 40 and thus the heat exchanger coil 42 are flowed through by refrigerant 22 coming from the high-pressure region 26 from the gas cooler 14, while the second fluid channel 44 is flowed through by refrigerant 22 from the low-pressure region 24 coming from the evaporator 20 or the refrigerant receiver 32.
- the heat of the refrigerant 22 may be discharged from the high-pressure region 26 to the refrigerant 22 on the low-pressure side.
- the heat exchanger coil 42 extends at least in sections helically through the housing 34 of the heat exchanger device 16.
- the heat exchanger coil 42 extends helically in a cylindrical jacket-shaped region between the refrigerant receiver 32 and the tubular jacket 38.
- the heat exchanger coil 42 is applied to the tubular jacket 38, so that a helical sealing surface between the heat exchanger coil 42 and the tubular jacket 38 is formed.
- the heat exchanger coil 42 thereby surrounds the refrigerant receiver 32.
- the heat exchanger coil 42 may also abut against the refrigerant receiver 32 so that the second fluid channel 44 extends helically between the refrigerant receiver 32 and the tubular jacket 38 and thus has a long length and the refrigerant 22 relatively has a lot of time to absorb heat from the heat exchanger coil 42.
- a distance between the heat exchanger coil 42 and the cooling consist medium container 32.
- the second fluid passage 44 is not made helical in the area between the refrigerant receiver 32 and the tubular jacket 38, however, the heat exchanger coil 42 generates the ribbed or corrugated surface so that the fluid 22 when swirling through the second fluid passage 44 is swirled and thereby can absorb effective heat from the heat exchanger coil 42.
- This second variant has a lower flow resistance than the first variant.
- the thermal coupling between the second fluid channel 44 and the first fluid channel 40 is correspondingly lower. It is possible to optimally adapt the heat coupling and flow resistance to the respective requirements.
- the heat exchanger coil 42 is connected to refrigerant connections in the lids 36. So that the refrigerant 22 can be passed through the refrigerant ports in the lids 36 through the heat exchanger coil 42.
- the heat exchanger coil 42 as shown for example in Fig. 6, 7 and 8, have different cross sections, in particular, the heat exchanger coil 42 may have circular, oval or elliptical cross sections. Alternatively or additionally, the heat exchanger coil 42 may also have a relatively flat profile with a plurality of smaller individual channels 50 within the heat exchanger coil 42.
- the refrigerant receiver 32 serves to trap and collect gaseous or liquid refrigerant 22 from the refrigerant gas flow, thus forming a kind of cold reservoir.
- the refrigerant collecting tank 32 has a cylindrical base body, through which the refrigerant 22 is introduced from the evaporator 20 approximately axially. On the same side there is another opening through which the gaseous refrigerant 22 which can flow out of the refrigerant collecting tank 32.
- the refrigerant 22 after flowing into the refrigerant collecting tank 32, the refrigerant 22 must pass through an arc through which liquid or solid portions of the refrigerant 22 are separated.
- the refrigerant receiver 32 is connected to at least one of the lids 36 so that refrigerant 22 can flow through a refrigerant inlet in the refrigerant receiver 32.
- the assembly of the refrigerant collecting tank 32 and the heat exchanger coil 42 to the lid 36 would be difficult if the tubular shell 38 would be already connected to one of the cover 36. For this reason, the tubular shell 38 is formed so that it can be mounted as the last part of the heat exchanger device 16.
- connection between the covers 36 and refrigerant collecting tank 32 and the connection between the covers 36 and the heat exchanger coil 42 can be made very simple, so that also favorable and / or otherwise particularly advantageous connection possibilities can be applied.
- the tubular jacket 38 initially has an inner diameter 46 which is larger than an outer diameter 48 of the cover 36 (see FIG. 3). As a result, the tubular jacket 36 can be pushed over the two covers 36. It is sufficient if the tubular jacket 38 is slidable only about one of the two covers 36. Consequently, one of the two covers 36 a Outer diameter 48 which is greater than the inner diameter 46 of the tubular shell 38th
- the tubular jacket 38 Since the tubular jacket 38 is intended to be in contact with the heat exchanger coil 42, the tubular jacket 38 is deformed radially inward after being pushed onto the heat exchanger device 16 (see FIG. 4). As a result of this radial deformation process, the tubular jacket 38 can also be connected to the lids 36 in a fluid-tight manner. Alternatively, the tubular jacket 38 may also be connected to the covers 36 prior to the radial deformation process.
- the radial deformation of the tubular jacket 38 can be achieved for example by hydraulic or pneumatic pressure, which is applied from the outside to the tubular jacket 38. Alternatively or additionally, the radial deformation of the tubular shell 38 can be effected by a molding tool.
- the connection of the cover 36 with the heat exchanger coil 42 and the refrigerant collecting tank 32 is not disturbed by the tubular jacket 38 and facilitates the installation of the heat exchanger device 16 considerably.
- the inner diameter 46 of the tubular shell 38 is reduced in a region 45 between two axial ends 47 of the tubular shell 38.
- the tubular jacket 38 can rest against the heat exchanger coil 42.
- the diameter 48 of the at least one cover 36 is greater than the diameter of the heat exchanger coil 42. Consequently, the inner diameter 46 of the tubular jacket 38 is greater at the axial ends 47 than in the region 45 between the axial ends 47.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014220403.8A DE102014220403A1 (de) | 2014-10-08 | 2014-10-08 | Verfahren zur Montage einer Wärmetauschereinrichtung und Wärmetauschereinrichtung |
PCT/EP2015/073023 WO2016055458A1 (de) | 2014-10-08 | 2015-10-06 | Verfahren zur montage einer wärmetauschereinrichtung und wärmetauschereinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3204709A1 true EP3204709A1 (de) | 2017-08-16 |
EP3204709B1 EP3204709B1 (de) | 2020-02-26 |
Family
ID=54249511
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15774640.5A Active EP3204709B1 (de) | 2014-10-08 | 2015-10-06 | Verfahren zur montage einer wärmetauschereinrichtung und wärmetauschereinrichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US20170307262A1 (de) |
EP (1) | EP3204709B1 (de) |
CN (1) | CN106796064B (de) |
DE (1) | DE102014220403A1 (de) |
WO (1) | WO2016055458A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016108312A1 (de) * | 2016-05-04 | 2017-11-09 | Hanon Systems | Wärmeübertrager |
DE102017221771A1 (de) * | 2017-12-04 | 2019-06-06 | Mahle International Gmbh | Heizungs- oder Klimaanlage |
WO2019161785A1 (zh) * | 2018-02-24 | 2019-08-29 | 三花控股集团有限公司 | 气液分离器及换热*** |
CN110195948A (zh) * | 2018-02-24 | 2019-09-03 | 三花控股集团有限公司 | 气液分离器及换热*** |
Family Cites Families (24)
Publication number | Priority date | Publication date | Assignee | Title |
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US1911464A (en) * | 1929-04-12 | 1933-05-30 | Swan A Pearson | Refrigerating system |
DE1751582B2 (de) * | 1967-10-27 | 1980-03-27 | R. & G. Schmoele Metallwerke Gmbh & Co Kg, 5750 Menden | Ölkühler mit einem an beiden Stirnseiten von je einem flachen Deckel verschlossenen zylindrischen Mantel |
US3765192A (en) * | 1972-08-17 | 1973-10-16 | D Root | Evaporator and/or condenser for refrigeration or heat pump systems |
US4078150A (en) * | 1976-08-04 | 1978-03-07 | Westinghouse Electric Corporation | Liquid-cooled stud for terminal bushings of a generator |
DE3127317A1 (de) * | 1981-05-15 | 1983-01-27 | Erich Schultze KG, 1000 Berlin | "anlagen-waermeaustauscher fuer kaelteanlagen" |
DE3119440A1 (de) * | 1981-05-15 | 1982-12-09 | Erich Schultze KG, 1000 Berlin | "anlagen-waermeaustauscher fuer kaelteanlagen" |
EP0215927A1 (de) * | 1985-03-22 | 1987-04-01 | McLAREN, Keith, Stuart | Wärmeaustauscher |
US5309987A (en) * | 1992-07-21 | 1994-05-10 | Astec | Method and apparatus for heating and cooling food products during processing |
SG115335A1 (en) * | 1997-07-04 | 2005-10-28 | Tokyo Electron Ltd | Process solution supplying apparatus |
DE19903833A1 (de) * | 1999-02-01 | 2000-08-03 | Behr Gmbh & Co | Integrierte Sammler-Wärmeübertrager-Baueinheit |
US6253573B1 (en) * | 1999-03-10 | 2001-07-03 | Specialty Equipment Companies, Inc. | High efficiency refrigeration system |
US6463757B1 (en) * | 2001-05-24 | 2002-10-15 | Halla Climate Controls Canada, Inc. | Internal heat exchanger accumulator |
DE10204107B4 (de) * | 2002-02-01 | 2018-12-13 | Mahle International Gmbh | Abgaswärmeübertrager |
US6779596B2 (en) * | 2002-03-22 | 2004-08-24 | Exxonmobil Research And Engineering Company | Heat exchanger with reduced fouling |
US20060005955A1 (en) * | 2004-07-12 | 2006-01-12 | Orr Troy J | Heat exchanger apparatus and methods for controlling the temperature of a high purity, re-circulating liquid |
JP4864439B2 (ja) * | 2005-12-06 | 2012-02-01 | 株式会社デンソー | 二重管、およびその製造方法 |
DE102006031197B4 (de) | 2006-07-03 | 2012-09-27 | Visteon Global Technologies Inc. | Innerer Wärmeübertrager mit Akkumulator |
DE102006051687A1 (de) * | 2006-10-30 | 2008-05-08 | Visteon Global Technologies Inc., Van Buren | Mechanische Verbindung eines Wärmeübertragerrohrs |
DE102008028853A1 (de) * | 2008-06-19 | 2009-12-24 | Behr Gmbh & Co. Kg | Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit |
GB0909221D0 (en) * | 2009-04-30 | 2009-07-15 | Eaton Fluid Power Gmbh | Heat exchanger |
US20110024080A1 (en) * | 2009-07-29 | 2011-02-03 | Prodigy Energy Recovery Systems, Inc. | Heat Exchanger |
KR101358271B1 (ko) * | 2009-11-24 | 2014-02-05 | 엠. 테크닉 가부시키가이샤 | 열교환기 |
DE102013201465A1 (de) * | 2013-01-30 | 2014-07-31 | Eberspächer Exhaust Technology GmbH & Co. KG | Wärmetauscher einer Brennkraftmaschine |
CN103115507A (zh) * | 2013-02-04 | 2013-05-22 | 方彦 | 高效筒式换热器 |
-
2014
- 2014-10-08 DE DE102014220403.8A patent/DE102014220403A1/de not_active Withdrawn
-
2015
- 2015-10-06 CN CN201580053237.9A patent/CN106796064B/zh active Active
- 2015-10-06 EP EP15774640.5A patent/EP3204709B1/de active Active
- 2015-10-06 US US15/517,892 patent/US20170307262A1/en not_active Abandoned
- 2015-10-06 WO PCT/EP2015/073023 patent/WO2016055458A1/de active Application Filing
Also Published As
Publication number | Publication date |
---|---|
CN106796064B (zh) | 2020-03-13 |
WO2016055458A1 (de) | 2016-04-14 |
DE102014220403A1 (de) | 2016-04-14 |
CN106796064A (zh) | 2017-05-31 |
EP3204709B1 (de) | 2020-02-26 |
US20170307262A1 (en) | 2017-10-26 |
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