WO2003054468A1 - Dispositif de transmission de chaleur - Google Patents

Dispositif de transmission de chaleur Download PDF

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Publication number
WO2003054468A1
WO2003054468A1 PCT/DE2002/003216 DE0203216W WO03054468A1 WO 2003054468 A1 WO2003054468 A1 WO 2003054468A1 DE 0203216 W DE0203216 W DE 0203216W WO 03054468 A1 WO03054468 A1 WO 03054468A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat transfer
pressure side
low
pressure
fluid
Prior art date
Application number
PCT/DE2002/003216
Other languages
German (de)
English (en)
Inventor
Stephan Leuthner
Peter Satzger
Petra Kanters
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to DE50210002T priority Critical patent/DE50210002D1/de
Priority to EP02760144A priority patent/EP1456591B1/fr
Priority to JP2003555137A priority patent/JP2005513404A/ja
Publication of WO2003054468A1 publication Critical patent/WO2003054468A1/fr

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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
    • F28F3/048—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 in the form of ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/104—Particular pattern of flow of the heat exchange media with parallel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • the invention relates to a device for heat transfer with a first channel through which a high-pressure fluid flows and a second channel through which a low-pressure fluid flows, which is separated from the first channel, the device having a stack-like structure of alternating heat transfer plates for the high-pressure fluid or the low-pressure fluid.
  • Such a heat exchanger is known in an application as an internal heat exchanger of a C0 2 vehicle air conditioning system from the status report No.20 of the German refrigeration and air conditioning association with the title: "Carbon dioxide - special features and application opportunities as a refrigerant”.
  • a flow module with a plurality of plate elements is known from EP 0 805 328, in which flow spaces are formed between adjacent plate elements from a plurality of rectilinear, parallel flow channels, which can be charged alternately with a first and a second fluid via supply and discharge channels.
  • the supply and discharge channels are formed by aligned openings in the plate elements.
  • These openings in the plate elements of EP 0 805 328 have a plurality of webs for mechanical stabilization, and in profiled plate elements those webs which are in the inlet area or outlet area of the Profiling are arranged, end below the plate element surface.
  • the heat exchanger according to the invention has a first fluid channel, through which a refrigerant is passed at high pressure, so that the high-pressure refrigerant can interact thermally with a heat transfer fluid which has a low pressure and is passed through a second fluid channel of the heat exchanger ,
  • the refrigerant circuit is thermally coupled to a cooling water circuit in this way, for example, an advantageous circuit variant is possible which introduces the heat obtained from a heat pump operation of the air conditioning system into the cooling water.
  • the cooling water circuit is, for example, the engine cooling circuit
  • the cooling water can be actively heated by the cooling circuit. With the cooling water heated in this way, the vehicle cabin can then be heated, as is customary in today's vehicles.
  • a heating function of the refrigerant circuit via a so-called hot gas mode can also be implemented in an advantageous manner by means of the heat exchanger according to the invention.
  • the device for heat transfer according to the invention can advantageously For example, cooling water, engine, engine and transmission oil are brought to near-operational temperatures before the vehicle is started. As a result, this leads to reduced emissions and reduced consumption of the vehicle.
  • a refrigeration system operating in the heat pump mode can thus advantageously also be used as an auxiliary heater for a motor vehicle via the device according to the invention.
  • circuit arrangements are possible which serve to pre-air-condition vehicles by air-conditioning the vehicle cabin, which is heated, for example, by sunlight, for a few minutes before the start of the journey.
  • a heat exchanger is necessary for this circuit arrangement in order to transfer the heat of the refrigerant to the cooling water or other operating materials.
  • This connecting link advantageously represents the device according to the invention as a coupling heat exchanger.
  • first, high-pressure side and the second, low-pressure side channel in the heat transfer device according to the invention are each formed from a plurality of in or on individual
  • Small channels formed heat transfer plates such a heat exchanger can be produced very compactly, ie with a small construction volume and at the same time a large heat transfer surface.
  • the heat transfer area of the device can be significantly increased by a large number of the small channels for both the high pressure heat transfer plates and for the low pressure heat transfer plates.
  • this design enables a coupling heat exchanger, which the different pressure levels on the. Can withstand high pressure and low pressure.
  • the number of high-pressure heat transfer plates can be adjusted relative to the number of low-pressure heat transfer plates in the device for heat transfer according to the invention to the respective requirements and the application of the heat exchanger according to the invention.
  • a suitable ratio of high-pressure heat transfer plates to low-pressure heat transfer plates can be realized in the device according to the invention, depending on the heat transfer surface required.
  • the small channels in the low-pressure heat transfer plates run parallel to one another.
  • either the low-pressure channels can be made narrower, which creates a higher heat-transfer area per low-pressure heat transfer plate. This in turn leads to an overall smaller heat exchanger, which can then transfer the same heat output with fewer plates.
  • a smaller pump can then be used in the overall circuit, which in turn leads to mass and cost savings in the overall system.
  • a very good heat transfer of the device according to the invention can advantageously be achieved if the small channels on the low pressure side are arranged essentially parallel to the small channels on the high pressure side. In addition to a very good heat transfer between the high-pressure medium and the low-pressure medium, this also enables the high-pressure-side refrigerant flow and the low-pressure-side fluid flow to flow through the device according to the invention either in the cocurrent or countercurrent principle.
  • the small channels on the low-pressure side of the heat exchanger flow in or out essentially in the direction of these channels. Since such small channels generally lead to a high pressure loss in heat exchangers, a large number of such channels are used in a single heat transfer plate by means of parallel connection and, in addition, a parallel connection of several such heat transfer plates is used in the device according to the invention.
  • the straight course of the individual small channels in the heat transfer plates also contributes to the desired, low pressure loss on the low pressure side of the device according to the invention.
  • the heat transfer device has a flange connection which optimizes the inflow or outflow, in particular, of the depressurized fluid.
  • a flange on the low-pressure side can also be integrated, for example, in an advantageous manner into a housing or a casing which surrounds the actual heat exchanger and seals it against overpressure.
  • a fluid guide element can be used in one or more flanges of the device according to the invention.
  • These fluid guide elements integrated in the flange allow the fluid flow to be influenced and the fluid flow to be distributed over the individual small channels of the device in a simple and very advantageous manner.
  • these guide elements can be designed, for example, as guide plates which divide the interior of the flange and thus deflect the low-pressure fluid flowing into the flange to a certain extent in order to evenly distribute the flow of the fluid. At the same time, the opening angle of the flow is reduced, which leads to a reduction in the flow pressure loss.
  • the low-pressure connection flanges can advantageously be produced, for example, from recyclable plastics, in particular by injection molding, which leads to low costs and a low additional weight.
  • the flanges can also be integrated directly into a housing which surrounds the device according to the invention in a sealing manner and, for example, thereby also provides the necessary connection options for the heat exchanger according to the invention to a cooling system or an air conditioning system.
  • connection or Outflow of the small channels on the low pressure side in the heat exchanger in a plane perpendicular to the level of the inflow and outflow of the high pressure side allows the simple and space-saving integration of the device according to the invention in a cooling or heating system.
  • the course of the small channels on the low-pressure side can be optimized in terms of flow technology, since the high-pressure or low-pressure collecting channels that lead to the individual small channels of the heat transfer plates run in different planes.
  • a further, very advantageous embodiment of the device according to the invention provides a coolant, for example the engine coolant of a motor vehicle, as the high-pressure side refrigerant C0 2 and as the low-pressure side heat transfer fluid.
  • the heat exchanger according to the invention enables the coupling of vehicle air conditioning systems, which due to legal regulations will have the refrigerant C0 2 in the future, to the cooling circuit of the vehicle.
  • the engine coolant of the vehicle for example, can thus be warmed up much more quickly during a cold start, in that a C0 2 air conditioning system of the vehicle operates as a heat pump.
  • the coolant can be used to transfer the heat of the refrigerant C0 2 to the cooling water or other operating materials by means of the coupling heat exchanger according to the invention.
  • Most upper and increasingly middle-class vehicles are equipped with air conditioning as standard. These components can be used as a heat pump at low temperatures by reversing the refrigeration cycle.
  • the heat pump is characterized by low energy consumption and a spontaneous response with high heating output.
  • auxiliary heater concepts that are related to consumption-optimized engines, for example direct-injection diesel engines, are becoming more and more up-to-date, a future-oriented concept in terms of safety and comfort.
  • the device according to the invention can thus be used to introduce the heat obtained from a heat pump operation of the air conditioning system into the cooling water of the motor vehicle
  • the device according to the invention thus represents a light, compact coupling heat exchanger which in particular withstands the high pressures of a refrigerant fluid and causes as little pressure loss as possible, in particular for a liquid low-pressure heat transfer fluid.
  • the inventive heat exchanger for coupling a C0 2 heating or. Cooling circuit can be used with the cooling circuit of an internal combustion engine.
  • FIG. 1 shows a simplified, perspective illustration of the heat transfer device according to the invention in a schematic illustration
  • FIG. 2 shows a view of the end face of the device according to the invention according to the exemplary embodiment in FIG. 1,
  • Figure 3 shows a cross section through a second
  • FIG. 4 shows a top view of a heat transfer plate on the low pressure side
  • FIG. 5 shows a plan view of a heat transfer plate on the high-pressure side
  • FIG. 6 shows a simplified, perspective illustration of a third exemplary embodiment of the device according to the invention.
  • FIG. 7 shows a perspective view of a connecting flange on the low-pressure side
  • FIG. 8 shows a fourth exemplary embodiment of the device according to the invention in a simplified, schematic perspective illustration
  • FIG. 9 shows a plan view of a heat transfer plate on the low-pressure side according to the fourth exemplary embodiment of the device according to the invention.
  • Figure 10 is a plan view of a high pressure side
  • Heat transfer plate according to the fourth embodiment.
  • the first exemplary embodiment of a heat transfer device 10 according to the invention shown in FIG. 1 has a plurality of heat transfer plates 12, 14, of which only a few are shown in FIG. 1 in order to clarify the structure of the heat exchanger.
  • the real heat exchanger has a large number of such heat transfer plates 12, 14. This is indicated by points 16 in FIG. 1.
  • the individual heat transfer plates 12, 14, also called microchannel plates, are layered one above the other, arranged between two end plates 22 and 24, and soldered or welded to one another.
  • the layered or stacked arrangement of the heat transfer plates 12, 14 is not limited to flat plates, as shown in FIG. 1. Rather, in other exemplary embodiments of the device according to the invention, curved plates or a bowl-shaped or concentric arrangement of corresponding heat transfer plates can also be used. In this sense, the term stack-like heat transfer plates further represents only one possible embodiment and no limitation of the device according to the invention.
  • the stack-like arrangement of the heat transfer plates 12 or of the heat exchanger according to the exemplary embodiment in FIG. 1 results in a base body 18 of the device 10 according to the invention.
  • the device according to the invention can, for example, enable heat exchange between a high-pressure side heating or cooling circuit and a low-pressure side cooling circuit.
  • the pressures on the high pressure side of this system are in the range from 0 to approx. 250 bar, with a typical working pressure on the high pressure side of approximately 130 bar.
  • the pressures are on the low pressure side typically between 0 and about 10 bar with a preferred pressure of about 3 bar.
  • high-pressure side heat transfer plates 12 alternate with low-pressure side heat transfer plates 14 in the stack.
  • a suitable ratio of high-pressure duct plates 12 to low-pressure duct plates 14 can be selected.
  • a channel plate 14 on the high-pressure side is followed by two channel plates 14 on the low-pressure side, which in turn is followed by a channel plate 14 on the high-pressure side.
  • a number between twenty and thirty can be regarded as a typical value for the number of, for example, the low-pressure side channel plates 14.
  • the high-pressure side channel plates of the heat exchanger according to FIG. 1 are connected to one another by two connecting channels 26 and 28, respectively.
  • the connecting channels 26 and 28 open into an inlet 30 and an outlet channel 32 of the high-pressure side of the device 10 according to the invention molded an air conditioning system.
  • the heat transfer plates 12 and 14 of the device 10 there is a multiplicity of small channels 34 and 42 arranged essentially parallel to one another, of which only the channels 42 of the heat transfer plates 14 on the low-pressure side can be seen in FIG.
  • the small channels 34 and 42 each provide a connection between the high pressure side and the low pressure side Inlet area of the heat exchanger and its outlet area through which the high-pressure side or the low-pressure side fluid is guided.
  • the high-pressure side fluid enters the heat exchanger via the inlet connection 31 and is distributed over the connecting channel 26 to the individual high-pressure side heat transfer plates 12.
  • the high-pressure side fluid flows through the plurality of high-pressure side heat transfer plates 12 and in the process releases its heat content to the base body 18 of the device 10.
  • the heat transfer plates 12, 14 that form the base body 18 typically consist of copper in order to avoid corrosion and to ensure good thermal conductivity between the individual transfer plates 12 and 14.
  • Heat transfer plates and thus for the base body 18 of the device according to the invention can be used.
  • the high-pressure side fluid is collected again in the connecting channel 28 and passed through this channel 28 to the outlet channel 32 of the high-pressure side of the device 10 according to the invention.
  • the connecting channel 26 is in open connection with individual, small channels 34 which are worked out in the heat transfer plates 12.
  • the small channels 34 are formed and are separated from one another by webs 35.
  • the heat transfer plates 12 of the device 10 for Heat transfer has a multiplicity of such channels 34, so that the illustration in FIG. 5 in this respect can only be regarded as a symbolic illustration that reflects the basic structure.
  • These small channels 34 direct the high-pressure fluid, coming from the connecting channel 26, via an inlet area 36 and an area of parallel small channels 38 to an outlet area 40, which in turn opens into the connecting channel 28. Except for the inlet area 36 and the outlet area 40, the course of the small channels in the exemplary embodiment in FIG. 5 is parallel, so that the overall course of the high-pressure side connection channels 34 should be regarded as essentially parallel.
  • the individual high-pressure side heat transfer plates 12 are connected to one another via the connecting channels 26 and 28, so that the refrigerant flowing into the device 10 according to the invention through the inlet channel 30 is distributed to the individual high-pressure side channel plates 14 (heat transfer plates).
  • the high-pressure side connection channels 26 and 28 are not in open connection with the low-pressure side heat transfer plates 14, as can also be seen, for example, in FIG. 4, the exemplary illustration of a low-pressure side heat transfer plate 14.
  • the inlet channel 30, the connecting channel 26, the high-pressure side small channels 34, the connecting channel 28 and the outlet channel 32 together form the high-pressure side channel of the heat exchanger.
  • each low-pressure side heat transfer plate 14 likewise has a multiplicity of small channels 42 which run essentially parallel to one another, as can be seen, for example, in FIG. 4, an exemplary illustration of a low-pressure side heat transfer plate 14.
  • the small channels 42 of the low-pressure heat transfer plates 14 run continuously from a first end face 44 of the heat transfer plates 14 to a second end face 46 of heat transfer plates 14.
  • the small channels 42 are formed, among other things, by webs 43 in the heat transfer plates 14.
  • the channel on the low-pressure side of the device according to the invention according to the exemplary embodiment in FIG. 1 is formed by the large number of small channels 42 arranged in parallel in terms of flow technology.
  • the small channels 34 and 42 of the high-pressure and low-pressure side heat transfer plates are arranged essentially parallel to one another, so that a direct current or a countercurrent heat exchanger can be implemented.
  • optimal heat coupling with the refrigerant C0 as high-pressure side fluid can be achieved with a channel cross-section of the small channels 42 of the low-pressure side heat transfer plates 14 of typically approximately 1 mm 2 .
  • the channel diameter should be larger than that in the water, for example in the cooling water circulating pollution. For an application in a motor vehicle, this means that the smallest diameter of the small channels 42 of the low-pressure side heat transfer plates 14 should be greater than 0.4 mm.
  • Channels with a height-to-width ratio of less than 0.6 are advantageous for easy manufacture of the channel plates.
  • Typical widths of the small channels 42 on the low-pressure side of the device according to the invention are in the range of a few millimeters, the height of the channels then correspondingly less than one millimeter.
  • the small channels 42 on the low-pressure side as well as the corresponding channels 34 on the high-pressure side can be made, for example, from the plate material
  • Heat transfer plates 12 and 14 can be etched out, or the webs 35 and 43, which separate the individual channels of a plate, could be applied to the plate material. Other manufacturing processes known to those skilled in the art for such microchannel plates are of course also possible.
  • FIG. 2 shows a top view of the end face 44 of the device 10 according to the invention according to FIG. 1.
  • a high-pressure side heat transfer plate 12 is alternately combined with two low-pressure side heat transfer plates 14.
  • the high-pressure side heat transfer plates 12 are connected to one another via the inlet channel 30 and the outlet channel 32 and the connecting channels 26 and 28, which are not shown in FIG.
  • the heat transfer plates 14 on the low-pressure side have no fluidic connection with one another.
  • Such a connection of the heat transfer plates 14 on the low-pressure side can take place, for example, by means of a flange connection to the base body 18 of the device according to the invention, as shown in the further description in various exemplary embodiments.
  • FIG. 3 shows a further exemplary embodiment of the device according to the invention.
  • the device 110 according to the invention according to FIG. 3 again consists of a stack-like arrangement of a plurality of two low-pressure side channel plates 114, which are alternately mechanically connected to a high-pressure side channel plate 112, so that a corresponding base body 118 of the heat exchanger is again formed.
  • the base body 118 of the heat exchanger according to the exemplary embodiment in FIG. 3 is flowed through on the one hand by a high pressure fluid and on the other hand by a low pressure fluid in the manner already described, so that it is not necessary to go into this at this point.
  • the base body 118 of the device according to the invention is surrounded by a housing 152 which has an inlet channel 154 and an outlet channel 156 on the low-pressure side.
  • the housing also has two openings 178 and 180 through which the inlet 130 and outlet channels 132 of the high-pressure side of the device according to the invention are guided.
  • the interior of the housing 152 which accommodates the base body 118 and the actual heat exchanger, is sealed off from the inlet channel 130 and the outlet channel 132 by appropriate sealing means, for example sealing rings 184.
  • the low-pressure inlet channel 154 and the outlet channel 156 of the low-pressure fluid are each designed in the form of a flange 153 or 155, which are connected in a sealing manner to a central part 158 of the housing 152.
  • This central part 158 of the housing 152 surrounds the base body 118 of the heat exchanger.
  • a sealing ring 160 or 162 can be provided between the connection flange 153 and the central part 158 of the housing
  • the connecting flanges 153 and 155 are designed so that they can be tightly fitted into corresponding lines 164 and 166, for example of the engine cooling circuit of a motor vehicle.
  • connection flange A possible configuration of such a connection flange
  • the flange 253 has a connecting piece 268 for connection to a line system. On the side 270 facing the heat exchanger, such a connection flange can have a recess 272 for receiving a flat seal, not shown, for example a paper seal.
  • the connecting flange 253 according to FIG. 7 has a series of guide plates 274 which are inserted or glued into grooves 276, which are milled into the flange 253, for example.
  • the baffles 274 reduce the opening angle of the flow on the low-pressure side, which in turn leads to a reduction in the loss of flow pressure.
  • the flange 253 can be tightly connected to the central part 158 of the housing 152 via fastening means 273.
  • the connecting flange 153, 155 or 253 on the low-pressure side can be produced, for example, from a metal, such as copper, or preferably also from plastic.
  • the baffles in the low-pressure flange do not necessarily have to be made of metal. Baffles another material, for example plastic, is also possible, so that the term sheet metal is not to be seen as a restriction.
  • the entire housing 152 of the device 110 according to the invention according to FIG. 3 can advantageously be made of plastic, so that, for example, the connecting flanges 153, 155 or 253 of the device 110 can also be formed in one piece with the central part 158 of the housing 152.
  • the flange 153 or 155 and in particular the means for uniformly distributing the flow or for influencing the opening angle of the flow can thus be integrated directly in the housing 152 of the device according to the invention.
  • the housing 152 should also have a cover in order to be able to introduce the actual heat exchanger, the main body 118 of the device 110 according to the invention, into the housing 152.
  • the cover of this housing there are also the two passages for the high-pressure connections 132 and 130, which in turn each seal the low-pressure fluid from the environment via a seal, for example an O-ring or an adhesive.
  • the cover can either be connected to the housing by means of a non-detachable connection, for example welding, gluing, soldering, or by a screw connection or other relevant connection methods.
  • FIG. 6 shows a further embodiment of the device according to the invention.
  • the basic stack or layer structure of the base body 218 of the exemplary embodiment in FIG. 6 is the same as the embodiments of the heat exchanger in FIGS. 1, 2 or 3, so that it will not be discussed again here.
  • nose-shaped shapes 286 which are rectangular in the exemplary embodiment and which, when the individual heat transfer plates 212 and 214 are arranged one above the other in the manner described, massive, cuboid protrusions 288 at the corners of the base body 218 of the device 210 result.
  • a connecting flange for a low-pressure side system can then be fastened, for example screwed, to these projections 288 without the course of both the high-pressure side and the low-pressure side small channels in the individual heat transfer plates 212 or 214 being influenced by the fastening means for the low-pressure flange, so that a flow-optimized course, in particular the small channels 214 is possible.
  • the course of the small channels on the low-pressure side must be chosen carefully, since it is important to prevent excessive pressure loss, especially on this side of the heat exchanger.
  • Such a pressure drop depends on the speed of the fluid, its fluid properties at that prevailing temperature and the geometry of the small channels.
  • flow widenings such as can occur in the heat transfer plates on the low-pressure side and, for example, as shown in FIG. 4, the means described in the device according to the invention ensure that these flow widenings remain below a value of typically 7 °, if possible, since at larger values the pressure loss quickly increases.
  • the configuration of the device according to the invention according to the exemplary embodiment in FIG. 6 makes it possible to provide the base body 218 of the device directly with a flange in which it is screwed onto the base body 218 or fastened to the base body in a different manner. This eliminates the need for an additional housing for accommodating the base body 218 of the device 210, so that the device according to the invention can be implemented in a very compact and lightweight manner.
  • the projections 288 for fastening a flange on the low-pressure side to the base body 218 can extend, for example, over the full height 219 of the base body 218 of the device, as is shown in FIG. 6 at the rear end 290 of the base body 218 facing the high-pressure side outlet channel 232, or alternatively only in each case extend over a portion of the height, as is shown at the front end 292 of the base body 218 of the device according to the invention facing the high-pressure inlet channel 230 in the form of two laterally arranged projections 294 and 296 or 295 and 297.
  • Heat transfer plates are manufactured (with and without nose-shaped arm 286) or a corresponding increase in the total weight of the heat exchanger due to the overhangs 288 extending over the entire height of the base body must be accepted if all heat transfer plates of the base body 218 are provided with the corresponding nose-shaped arms 286 are.
  • the increase in the total weight of the heat exchanger must be weighed in individual cases against the advantages of improved tightness, ease of installation and simpler installation situation for the device.
  • FIG. 8 shows a fourth embodiment of the device for heat transfer according to the invention, which shows a further, slight modification compared to the embodiment of FIG. 6.
  • the basic structure of the heat exchanger in FIG. 8 corresponds to the stack-like structure of various heat transfer plates 312 and 314, as has already been described in detail in connection with the exemplary embodiments in FIG. 6, FIG. 3 and FIG. 1.
  • the base body 318 of the device has a multiplicity of alternating high-pressure-side 312 and low-pressure-side heat transfer plates 314, which, depending on the requirements of the heat exchanger, are combined in a desired number relative to one another.
  • the high-pressure side heat transfer plates 312 are connected to one another via connecting channels 326 and 328, which are not shown.
  • the connection channels 326 and 328 in the base body 318 of the device open into an inlet channel 330 or at its other end into an outlet channel 332.
  • the inlet channel 330 and the outlet channel 332 are likewise permanently connected to an upper end plate 322 as a connecting piece.
  • connection of the inlet channel 330 to the outlet channel 332 is realized by a large number of small channels connected in parallel in terms of flow in the high-pressure side heat transfer plates 312.
  • the individual, high-pressure side heat transfer plates 312, for their part, are also connected in terms of flow in parallel to one another, between the connection channel 326 and the connection channel 328.
  • Figure 10 shows an example of a high-pressure side heat transfer plate 312 of the inventive device according to the embodiment of Figure 8.
  • the plate has recesses 390 and 392, respectively, which result in holes 394 and 396 in the base body 318, by means of which a low-pressure side flange directly on the base body 318
  • the device 310 according to the invention can be fastened, as has been described, for example, in connection with FIG. 6.
  • the holes 394 and 396 can also only be drilled into the base body 318, which leads to a simplification of the heat exchanger plates.
  • Attachment projections 388 of the base body 318 arranged. For this reason, at least the two projections 388 receiving the connecting channels 326 and 328 must extend over the full height 319 of the base body 318.
  • the two remaining fastening projections 394 or 395 can, as shown in FIG. 6, optionally extend over the entire height 219 of the base body 318 or, for reasons of weight, as shown in FIG. 8, can only be designed as large as is necessary for receiving the fastening means for the low-pressure side flanges is. In this way, shown in FIGS. 8 to 10, it is possible to align the course of the small channels 342 of the low-pressure side channel plates 314 completely parallel to one another, so that there is a straight flow course of the low-pressure fluid in the heat exchanger, which is accompanied by minimal pressure losses.
  • Figure 9 shows such a low-pressure side
  • Heat transfer plate 314 with straight, small channels 342 running parallel between the two end faces 344 and 346, which are separated from one another by corresponding webs 343.
  • the pressure loss of the low-pressure side fluid over the heat exchanger is further reduced.
  • the device according to the invention is not limited to the exemplary embodiments shown in the figures.
  • the device according to the invention is in particular not limited to use as a coupling heat exchanger between the refrigerant circuit of an air conditioning system of a motor vehicle and the coolant circuit of, for example, an internal combustion engine of this motor vehicle.
  • Such a heat exchanger according to the invention can be used wherever heat is to be exchanged between a refrigerant under high pressure and a liquid heat transfer fluid under low pressure.
  • the device according to the invention can also be used in stationary heating or air-conditioning systems.
  • the heat exchanger according to the invention can also be used in Sterling machines which also operate at very high pressures (50-150 bar) and which are cooled or heated with liquid.
  • the device according to the invention can be used as a pure heat exchanger, but also as a reactor.
  • the heat exchanger can be used as an evaporator, for example for cooling cooling water or for using the heat contained therein.

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

L'invention concerne un dispositif (110) de transmission de chaleur qui comprend au moins un premier canal traversé par un fluide côté haute pression et au moins un second canal, séparé du premier, traversé par un fluide côté basse pression. La structure de ce dispositif est constituée d'au moins une plaque de transmission de chaleur (112) destinée au fluide haute pression et d'au moins une plaque de transmission de chaleur (114) destinée au fluide basse pression. Selon l'invention, il est proposé que le fluide haute pression soit un réfrigérant et que le fluide basse pression soit un caloporteur liquide.
PCT/DE2002/003216 2001-12-10 2002-08-31 Dispositif de transmission de chaleur WO2003054468A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE50210002T DE50210002D1 (de) 2001-12-10 2002-08-31 Vorrichtung zur wärmeübertragung
EP02760144A EP1456591B1 (fr) 2001-12-10 2002-08-31 Dispositif de transmission de chaleur
JP2003555137A JP2005513404A (ja) 2001-12-10 2002-08-31 熱伝達のための装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10160380A DE10160380A1 (de) 2001-12-10 2001-12-10 Vorrichtung zur Wärmeübertragung
DE10160380.0 2001-12-10

Publications (1)

Publication Number Publication Date
WO2003054468A1 true WO2003054468A1 (fr) 2003-07-03

Family

ID=7708530

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2002/003216 WO2003054468A1 (fr) 2001-12-10 2002-08-31 Dispositif de transmission de chaleur

Country Status (4)

Country Link
EP (1) EP1456591B1 (fr)
JP (1) JP2005513404A (fr)
DE (2) DE10160380A1 (fr)
WO (1) WO2003054468A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1571407A2 (fr) 2004-03-05 2005-09-07 Modine Manufacturing Company Echangeur de chaleur à plaques
US20190137197A1 (en) * 2017-11-03 2019-05-09 Doosan Heavy Industries & Construction Co., Ltd Printed circuit-type heat exchanger having integral structure

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10331372A1 (de) * 2003-07-11 2005-01-27 Zf Friedrichshafen Ag Plattenwärmeübertrager, insbesondere Getriebeölkühler
US7343965B2 (en) 2004-01-20 2008-03-18 Modine Manufacturing Company Brazed plate high pressure heat exchanger
DE102004049988A1 (de) * 2004-10-14 2006-04-20 Modine Manufacturing Co., Racine Plattenwärmetauscher
DE102005058153B4 (de) * 2005-04-22 2007-12-06 Visteon Global Technologies Inc., Van Buren Wärmeübertrager mit Mehrkanalflachrohren
DE102005021464A1 (de) * 2005-05-10 2006-11-16 Modine Manufacturing Co., Racine Vorrichtung zur Zwischenkühlung
HUE045594T2 (hu) 2012-06-05 2020-01-28 Soc Technique Pour Lenergie Atomique Lemezes hõcserélõ a járatok közötti homogén közegáramlások megvalósításához
KR102119798B1 (ko) * 2012-12-13 2020-06-05 엘지이노텍 주식회사 차량용 냉각 플레이트
DE102012224353A1 (de) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager
SE541591C2 (en) 2016-02-24 2019-11-12 Alfa Laval Corp Ab A heat exchanger plate for a plate heat exchanger, and a plate heat exchanger
CN108332588B (zh) * 2018-04-26 2023-09-22 江苏宝得换热设备股份有限公司 一种高寿命多系统板式换热器及其实现方法

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Publication number Priority date Publication date Assignee Title
EP0543132A1 (fr) * 1991-11-16 1993-05-26 Forschungszentrum Karlsruhe GmbH Moteur stirling
EP0805328A2 (fr) 1996-05-02 1997-11-05 DORNIER GmbH Module d'écoulement
GB2314149A (en) * 1996-06-14 1997-12-17 Star Refrigeration Thermosyphon refrigeration apparatus
WO2001069157A2 (fr) * 2000-03-16 2001-09-20 Robert Bosch Gmbh Echangeur de chaleur pour un climatiseur de vehicule au co¿2?
WO2001088454A1 (fr) * 2000-05-19 2001-11-22 Llanelli Radiators Limited Condenseur et echangeur thermique de vehicule automobile

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543132A1 (fr) * 1991-11-16 1993-05-26 Forschungszentrum Karlsruhe GmbH Moteur stirling
EP0805328A2 (fr) 1996-05-02 1997-11-05 DORNIER GmbH Module d'écoulement
GB2314149A (en) * 1996-06-14 1997-12-17 Star Refrigeration Thermosyphon refrigeration apparatus
WO2001069157A2 (fr) * 2000-03-16 2001-09-20 Robert Bosch Gmbh Echangeur de chaleur pour un climatiseur de vehicule au co¿2?
WO2001088454A1 (fr) * 2000-05-19 2001-11-22 Llanelli Radiators Limited Condenseur et echangeur thermique de vehicule automobile

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1571407A2 (fr) 2004-03-05 2005-09-07 Modine Manufacturing Company Echangeur de chaleur à plaques
US7600559B2 (en) 2004-03-05 2009-10-13 Modine Manufacturing Company Plate heat exchanger
US20190137197A1 (en) * 2017-11-03 2019-05-09 Doosan Heavy Industries & Construction Co., Ltd Printed circuit-type heat exchanger having integral structure

Also Published As

Publication number Publication date
EP1456591A1 (fr) 2004-09-15
EP1456591B1 (fr) 2007-04-18
JP2005513404A (ja) 2005-05-12
DE10160380A1 (de) 2003-06-18
DE50210002D1 (de) 2007-05-31

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