EP1456591B1 - Vorrichtung zur wärmeübertragung - Google Patents

Vorrichtung zur wärmeübertragung Download PDF

Info

Publication number
EP1456591B1
EP1456591B1 EP02760144A EP02760144A EP1456591B1 EP 1456591 B1 EP1456591 B1 EP 1456591B1 EP 02760144 A EP02760144 A EP 02760144A EP 02760144 A EP02760144 A EP 02760144A EP 1456591 B1 EP1456591 B1 EP 1456591B1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
pressure
low
small channels
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02760144A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1456591A1 (de
Inventor
Stephan Leuthner
Peter Satzger
Petra Kanters
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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
Publication of EP1456591A1 publication Critical patent/EP1456591A1/de
Application granted granted Critical
Publication of EP1456591B1 publication Critical patent/EP1456591B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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 side fluid flows and a second channel through which a low-pressure side fluid is separated from the first channel, wherein the device has a stacked construction heat transfer plates for the high-pressure fluid or the low-pressure fluid.
  • Such a heat exchanger is in an application as an internal heat exchanger of a CO 2 vehicle air conditioning from the status report no. 20 of the German refrigeration and air conditioning association with the title: "Carbon dioxide - peculiarities and opportunities for use as a refrigerant" known.
  • a flow module with a plurality of plate elements in which between adjacent plate elements flow spaces of a plurality of rectilinear, parallel flow channels are formed, which can be fed via supply and discharge channels alternately with a first and a second fluid.
  • the supply and discharge channels are formed by aligned openings in the plate elements.
  • These apertures in the plate elements of EP 0 805 328 have a plurality of webs for mechanical stabilization, wherein in profiled plate elements those webs which in the inlet region or outlet region of the Profiling are arranged to end below the plate element surface.
  • a heat exchanger system for the automotive sector which has a, traversed by a high-pressure side fluid first channel and a flow of a Bermos marcem fluid, separated from the first channel second channel.
  • the heat transfer device of WO 01/88454 A1 has a layered structure consisting of a plurality of heat transfer plates for the pressurized fluid and a plurality of low pressure fluid heat transfer plates, wherein the high pressure fluid may be a refrigerant and the low pressure fluid may be a liquid heat transfer fluid.
  • 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 with a heat transfer fluid, which has a low pressure and is passed through a second fluid channel of the heat exchanger, thermally interact can.
  • the refrigerant circuit is thermally coupled in this way, for example, with a cooling water circuit, so an advantageous circuit variant is possible, which brings the heat obtained from a heat pump operation of the air conditioning heat in the cooling water.
  • the cooling water circuit is the engine cooling circuit
  • the cooling water can be actively heated by the refrigeration cycle. With the thus heated cooling water can then, as usual in today's vehicles, the vehicle cab be heated.
  • a heating function of the refrigerant circuit via a so-called heating gas mode can be realized in an advantageous manner by means of the heat exchanger according to the invention.
  • the inventive device for heat transfer For example, cooling water, engine, engine and transmission oil are brought to operating temperatures before commissioning the vehicle. As a result, this leads to reduced emissions and a reduced consumption of the vehicle.
  • a refrigeration system operating in heat pump mode can thus also be advantageously used via the device according to the invention as a heater for a motor vehicle.
  • circuit arrangements are possible, which are used for pre-air conditioning of vehicles, for example, by the heated for example by sunlight vehicle cabin is conditioned for several minutes before the start of the journey.
  • a heat exchanger is necessary to deliver the heat of the refrigerant to the cooling water or other supplies.
  • This connecting member is advantageously the device according to the invention as a coupling heat exchanger.
  • the 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 formed in or on individual heat transfer plates small channels, such a heat exchanger can be very compact, ie with a small volume at the same time large heat-transferring surface. With a large number of small channels for both the high pressure heat transfer plates and the low pressure heat transfer plates, the heat transferring area of the device can be significantly increased.
  • this design allows a coupling heat exchanger, the different pressure levels on the. High pressure and the low pressure side can withstand.
  • the number of high-pressure heat transfer plates relative to the number of low-pressure heat transfer plates can be adapted 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 of the invention depending on the required heat transfer surface.
  • a very good heat transfer of the device according to the invention can be realized in an advantageous manner, when the small channels of the low pressure side are arranged substantially parallel to the small channels of the high pressure side.
  • this also makes it possible for the high-pressure-side refrigerant flow and the low-pressure-side fluid flow to be able to flow through the device according to the invention in a cocurrent or countercurrent principle.
  • the inflow or outflow of the small channels of the low pressure side of the heat exchanger takes place substantially in the direction of these channels. Since such small channels in heat exchangers generally lead to a high pressure loss, a plurality of such channels are used in a single heat transfer plate by parallel connection and additionally a parallel connection of several such heat transfer plates 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 drop on the low pressure side of the device according to the invention.
  • the low-pressure fluid it is essential that it undergoes only a very small pressure loss when passing through the heat transfer device according to the invention, since too great a pressure loss would require the use of an additional, but at least a larger pump for circulating the low-pressure fluid.
  • this has a flange connection, which optimizes the flow or outflow, especially of the low-pressure fluid.
  • flange on the low-pressure side can also, for example, in an advantageous. Way be integrated into a housing or enclosure, which surrounds the actual heat exchanger and seals overpressure.
  • a fluid guide element can be used in one or more flanges of the device according to the invention.
  • These poidleitieri integrated in the flange allow in a simple and very advantageous manner, the influence of the fluid flow or the distribution of the fluid flow to the individual small channels of the device.
  • These guide elements can be embodied in an advantageous embodiment of the device according to the invention, for example as baffles, which divide the flange interior and thus deflect the low-pressure fluid flowing into the flange to a certain extent in order to distribute the flow of the fluid evenly. At the same time, the opening angle of the flow is reduced, which leads to a reduction of the flow pressure loss.
  • the low-pressure side flanges can for example be made of recyclable plastics, in particular by injection molding, resulting in low cost and 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 required connection possibilities of the heat exchanger according to the invention to a cooling system or an air conditioning system.
  • the device according to the invention provides as high-pressure side refrigerant CO 2 and as a low-pressure side heat transfer fluid, a coolant, for example, the engine coolant of a motor vehicle before.
  • a coolant for example, the engine coolant of a motor vehicle before.
  • the heat exchanger according to the invention enables the coupling of vehicle air conditioning systems, which will have the refrigerant CO 2 due to legal regulations in the future, to the cooling circuit of the vehicle.
  • the engine coolant of the vehicle can be heated significantly faster in a cold start by a CO 2 air conditioning system of the vehicle operates as a heat pump.
  • the coolant can be used to deliver the heat of the refrigerant CO 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 at low temperatures by reversing the refrigeration cycle as a heat pump.
  • the heat pump is characterized by low energy consumption and a spontaneous response at high heat output. This is for auxiliary heater concepts associated with Consumption-optimized engines, such as direct-injection diesel engines, are becoming more and more recent, with regard to safety and comfort a forward-looking concept.
  • the device according to the invention can be used to bring the heat obtained from a heat pump operation of the air conditioning heat in the cooling water of the motor vehicle
  • the device according to the invention thus constitutes a lightweight, compactly constructed coupling heat exchanger, which in particular withstands the existing high pressures of a refrigerant fluid and thereby causes as little pressure loss as possible, in particular for a liquid low-pressure heat transfer fluid.
  • the inventive heat exchanger for coupling a CO 2 heating or cooling circuit can be used with the cooling circuit of an internal combustion engine.
  • the first embodiment of a device 10 for heat transfer according to the invention comprises a plurality of heat transfer plates 12,14, of which only a few are shown in Figure 1 in a schematic representation to illustrate the structure of the heat exchanger.
  • the real heat exchanger has a plurality of such heat transfer plates 12,14. This is indicated by the points 16 in FIG.
  • 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 against each other or welded.
  • the layered or stacked arrangement of the heat transfer plates 12,14 is not limited to flat plates, as shown in Figure 1. Rather, in other embodiments of the device according to the invention also curved plates or a cup-shaped or concentric arrangement of corresponding heat transfer plates can be used. In this sense, the term stackable arranged heat transfer plates hereinafter only one possible embodiment and no limitation of the device according to the invention.
  • the stack-shaped arrangement of the heat transfer plates 12 and the heat exchanger according to the embodiment of Figure 1 results in a main body 18 of the device 10 according to the invention.
  • the device according to the invention can, for example, allow heat exchange between a not shown high-pressure side heat or refrigeration cycle and a low pressure side cooling circuit.
  • the pressures on the high pressure side of this system range from 0 to about 250 bar, with a typical high pressure working pressure of about 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 channel plates 12 to low pressure channel plates 14 can be selected.
  • a high-pressure side channel plate 12 two low-pressure side channel plates 14, in turn, followed by a high-pressure side channel plate 14.
  • a number between twenty and thirty may be considered.
  • the high pressure side channel plates of the heat exchanger according to Figure 1 are connected by two connecting channels 26 and 28 with each other.
  • 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.
  • the inlet channel 30 and the outlet channel 32 of the device according to the invention are in the form of connecting pieces 31 and 33, respectively, for connection lines, not shown, for example, of a refrigeration cycle formed of an air conditioner.
  • the heat transfer plates 12 and 14 of the device 10 is a plurality of substantially parallel to each other arranged small channels 34 and 42, of which in Figure 1, only the low-pressure side channels 42 of the heat transfer plates 14 can be seen.
  • the small channels 34 and 42 provide separately for the high pressure side and the low pressure side a connection between the Inlet region of the heat exchanger and the outlet region forth through which the high-pressure side and the low-pressure side fluid is passed.
  • the high-pressure side fluid enters the heat exchanger via the inlet port 31 and is distributed via 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 thereby releases its heat content to the main body 18 of the device 10.
  • the heat transfer plates 12, 14, which construct the main body 18, are typically made of copper in order to prevent corrosion and to ensure a good thermal conductivity between the individual transfer plates 12 and 14.
  • the high-pressure side fluid in the connecting channel 28 is collected again 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 communication with individual, small channels 34 which are worked out in the heat transfer plates 12.
  • the small channels 34 are formed and are separated by webs 35.
  • the heat transfer plates 12 of the device 10 for Heat transfer has a plurality of such channels 34, so that the representation in Figure 5 can be regarded in this regard only as a symbolic, the basic structure reproducing representation.
  • These small channels 34 direct the high-pressure fluid, coming from the connecting channel 26, through an inlet region 36 and a region of parallel small channels 38 to an outlet region 40, which in turn opens into the connecting channel 28. Except for the inlet region 36 and the outlet region 40, the course of the small channels in the embodiment of Figure 5 is parallel, so that the overall course of the high pressure side connecting channels 34 should be considered as substantially parallel.
  • the individual high-pressure side heat transfer plates 12 communicate with each other, 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 connecting channels 26 and 28 are not in open communication with the low-pressure side heat transfer plates 14, as shown for example in Figure 5, the exemplary representation of a low-pressure side heat transfer plate 14.
  • the inlet passage 30, the communication passage 26, the high pressure side small passages 34, the communication passage 28, and the outlet passage 32 together constitute the high pressure side passage of the heat exchanger.
  • Each low-pressure side heat transfer plate 14 also has a plurality of small channels 42, which are substantially parallel to each other, as for example in Figure 5, an exemplary representation of a low-pressure side heat transfer plate 14 can be seen.
  • the small channels 42 of the low-pressure heat transfer plates 14 extend continuously from a first end face 44 of the heat transfer plates 14 to a second end face 46 heat transfer plates 14.
  • the small channels 42 are formed, inter alia, by webs 43 in the heat transfer plates fourteenth
  • the low-pressure-side channel of the device according to the invention according to the embodiment of Figure 1 is formed by the plurality of fluidly arranged parallel to each other small channels 42nd
  • the small channels 34 and 42 of the high pressure or low pressure side heat transfer plates are arranged substantially parallel to each other, so that a DC or a countercurrent heat exchanger can be realized.
  • the small channels 42 of the low-pressure side and the corresponding channels 34 on the high-pressure side may for example be etched out of the plate material of the heat transfer plates 12 and 14, respectively, the webs 35 and 43, which separate the individual channels of a plate could be applied to the plate material.
  • Other, known to those skilled in manufacturing methods for such microchannel plates are of course also possible.
  • FIG. 2 shows a plan view of the end face 44 of the device 10 according to the invention as shown in FIG.
  • On the end plate 24 are alternately a high-pressure side heat transfer plate 12 combined with two low-pressure side heat transfer plates 14.
  • the high-pressure side heat transfer plates 12 are connected via the inlet channel 30 and the outlet channel 32 and the connection channels 26 and 28, not shown in Figure 2 with each other.
  • the low-pressure side heat transfer plates 14 have no fluidic connection with each other.
  • Such a connection of the low-pressure-side heat transfer plates 14 can take place, for example, by means of a flange connection to the main body 18 of the device according to the invention, as shown in the further description in various embodiments.
  • FIG. 3 shows a further exemplary embodiment of the device according to the invention.
  • the inventive device 110 according to FIG. 3 again consists of a stacked arrangement of a multiplicity of two low-pressure-side channel plates 114, which are alternately mechanically connected to a high-pressure-side channel plate 112, so that in turn a corresponding main body 118 of the heat exchanger is formed.
  • the main body 118 of the heat exchanger according to the embodiment of Figure 3 is traversed in the manner already described on the one hand by a high-pressure fluid and on the other hand by a low-pressure fluid, so that at this point not further discussed.
  • 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, respectively, 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 receives the main body 118 and the actual heat exchanger, is sealed by means of corresponding sealing means, for example sealing rings 184, with respect to the inlet channel 130 and the outlet channel 132, respectively.
  • the low-pressure side inlet channel 154 and the outlet channel 156 of the low-pressure fluid are each in the form of a flange 153 or 155, which are connected in a sealing manner with a central part 158 of the housing 152.
  • This central part 158 of the housing 152 surrounds the main body 118 of the heat exchanger.
  • connection flange connections 153 or 155 For sealing the flange connections 153 or 155, as shown in the exemplary embodiment of FIG. 3, a respective sealing ring 160 or 162 between the connection flange 153 and the central part 158 of the housing 152 or between the central part 158 of the housing 152 and the Connection flange 155 inserted.
  • the connecting flanges 153 and 155 are formed so that they can be fitted tightly into corresponding lines 164 and 166, for example, the engine cooling circuit of a motor vehicle.
  • connection flange 153 or 156 A possible embodiment of such a connection flange 153 or 156 is shown in FIG.
  • the flange 253 has a spigot 268 for connection to a conduit system.
  • a flange On the side facing the heat exchanger 270, such a flange may have a recess 272 for receiving a flat gasket, not shown, for example, a paper seal.
  • the connection flange 253 has according to Figure 7, a number of baffles 274, which are inserted or glued in grooves 276, which are milled into the flange 253, for example.
  • the opening angle of the low-pressure side flow is reduced by the baffles 274, which in turn leads to a reduction of the flow pressure loss.
  • the flange 253 can be tightly connected via fastening means 273 to the central part 158 of the housing 152.
  • the low-pressure side connecting flange 153, 155 or 253 can be made, for example, from a metal, such as copper or preferably also from plastic.
  • the baffles present in the low-pressure side flange do not necessarily have to be made of metal. Baffles Another material, for example, plastic are also possible, so that the term of the sheets is not to be seen as a restriction.
  • the entire housing 152 of the device 110 according to the invention of FIG. 3 can be made of plastic, so that, for example, the connection flanges 153, 155 or 253 of the device 110 can also be formed integrally with the central part 158 of the housing 152.
  • the flange 153 or 155 and in particular the means for uniform distribution of the flow, or for influencing the opening angle of the flow can thus be integrated directly into the housing 152 of the device according to the invention.
  • the housing 152 should additionally 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 lid of this housing then also contains the two passages for the high-pressure connections 132 and 130, which in turn seal the low-pressure fluid to the environment via a seal, for example an O-ring or an adhesive bond.
  • the cover can either be connected to the housing via a non-detachable connection, for example welding, gluing, soldering or via a screw connection or other relevant connection methods. In the case of a screw connection, however, a further seal would be required for the housing.
  • FIG. 6 shows a further embodiment of the device according to the invention.
  • the basic stack-wise or layered structure of the main body 218 of the embodiment in Figure 6 is similar to the embodiments of the heat exchanger in Figures 1,2 or 3, so that it will not be discussed again at this point.
  • the heat transfer plates 12 and 14 of the device 210 according to the invention according to Figure 6 nose-shaped, rectangular in the embodiment formations 286, which, when the individual heat transfer plates 212 and 214 are arranged in the manner described above one above the other, massive, rectangular protrusions 288 at the corners of the main body 218 of the device 210 result.
  • a flange for a low-pressure side system attached for example, be screwed without the course of both the high-pressure side and the low-pressure side small channels in the individual heat transfer plates 212 and 214 is influenced due to the fastening means for the low pressure flange, so that a aerodynamically optimized course, in particular the small channels 214 is possible.
  • the course of the small channels on the low pressure side must be carefully chosen, since it is important to prevent excessive pressure loss especially on this side of the heat exchanger.
  • Such pressure loss depends on the velocity of the fluid, its fluid properties in the process respective prevailing temperature and the geometry of the small channels.
  • the projections 288 for attaching a low-pressure side flange on the main body 218 may extend over the full height 219 of the body 218 of the device, as shown in Figure 6 at the rear, the high pressure side outlet port 232 facing end 290 of the body 218 or alternatively each only extend over a portion of the height, as shown at the front, the high-pressure side inlet channel 230 facing the end 292 of the main body 218 of the device according to the invention in the form of two laterally arranged protrusions 294 and 296 and 295 and 297, respectively.
  • the mounting projections it is possible to attach each of the low-pressure flanges individually on the body 218 of the heat exchanger directly, so that, for example, a mutual bracing of the flanges between them, threaded rods or similar means is no longer necessary.
  • Figure 8 shows a fourth embodiment of the device according to the invention for heat transfer, which shows a further, slight modification compared to the embodiment of Figure 6.
  • the basic construction of the heat exchanger in FIG. 8 corresponds to the stacked construction 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.
  • the main body 318 of the apparatus has a plurality of high pressure side 312 and low pressure side heat transfer plates 314, which are combined in a desired relative number to each other depending on the requirements of the heat exchanger.
  • the high-pressure side heat transfer plates 312 are connected to each other via connecting channels 326 and 328, not shown.
  • the connecting channels 326 and 328 in the main body 318 of the device open into an inlet channel 330 and at the other end in an outlet channel 332.
  • the inlet channel 330 and the outlet channel 332 are also connected in the embodiment of Figure 8 as a connecting piece firmly with an upper end plate 322.
  • connection of the inlet channel 330 with the outlet channel 332 is realized by a plurality of small fluidically parallel channels in the high pressure side heat transfer plates 312.
  • the individual, high-pressure-side heat transfer plates 312 in turn are also fluidically connected in parallel to one another, between the connecting channel 326 and the connecting channel 328.
  • FIG. 10 shows an example of a high-pressure side heat transfer plate 312 of the device according to the invention according to the embodiment of Figure 8.
  • the plate has recesses 390 and 392, 318 in the base body bores 394 and 396 results, by means of which a low-pressure side flange directly to the main body 318 of Device 310 according to the invention can be attached, as has been described, for example, analogously in connection with Figure 6.
  • the bores 394 and 396 can also be subsequently introduced into the main body 318, which leads to a simplification of the heat exchanger plates.
  • the connecting channels 326 and 328 are arranged in the mounting projections 388 of the main body 318. For this reason, at least the two, the connecting channels 326 and 328 receiving projections 388 must extend over the full height 319 of the body 318.
  • the two remaining attachment 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 configured as large as necessary for receiving the fastening means for the low-pressure side flanges is.
  • Figure 9 shows such a low-pressure side heat transfer plate 314 with straight, between the two end faces 344 and 346 parallel extending small channels 342, which are separated by respective webs 343.
  • the pressure loss of the low-pressure-side fluid above the heat exchanger is further reduced.
  • the device according to the invention is not limited to the exemplary embodiments illustrated in the figures.
  • the device according to the invention is in particular not limited to the use as a coupling heat exchanger between the refrigerant circuit of an air conditioning system of a motor vehicle and the coolant circuit, 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 carrier fluid under low pressure.
  • the device according to the invention can also be used in stationary heat 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 of cooling water or to use 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)
EP02760144A 2001-12-10 2002-08-31 Vorrichtung zur wärmeübertragung Expired - Lifetime EP1456591B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
1993-11-19
DE10160380A DE10160380A1 (de) 2001-12-10 2001-12-10 Vorrichtung zur Wärmeübertragung
PCT/DE2002/003216 WO2003054468A1 (de) 2001-12-10 2002-08-31 Vorrichtung zur wärmeübertragung

Publications (2)

Publication Number Publication Date
EP1456591A1 EP1456591A1 (de) 2004-09-15
EP1456591B1 true EP1456591B1 (de) 2007-04-18

Family

ID=7708530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02760144A Expired - Lifetime EP1456591B1 (de) 2001-12-10 2002-08-31 Vorrichtung zur wärmeübertragung

Country Status (4)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10767933B2 (en) 2016-02-24 2020-09-08 Alfa Laval Corporate Ab Heat exchanger plate for a plate heat exchanger, and a plate heat exchanger

Families Citing this family (11)

* 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
DE102004010640A1 (de) 2004-03-05 2005-09-22 Modine Manufacturing Co., Racine Plattenwärmeübertrager
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
JP2019086278A (ja) * 2017-11-03 2019-06-06 ドゥサン ヘヴィー インダストリーズ アンド コンストラクション カンパニー リミテッド 一体型構造を含む印刷基板型熱交換器
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***板式换热器及其实现方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137756C2 (de) * 1991-11-16 1993-11-11 Kernforschungsz Karlsruhe Wärmekraftmaschine nach dem Stirling-Prinzip
DE19617396C2 (de) 1996-05-02 1998-03-26 Dornier Gmbh Strömungsmodul
GB9612445D0 (en) * 1996-06-14 1996-08-14 Star Refrigeration Thermosyphon refrigeration apparatus
JP2004508525A (ja) * 2000-03-16 2004-03-18 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング 車両に設けられたｃｏ２空調装置に用いられる熱交換器
GB0012033D0 (en) * 2000-05-19 2000-07-05 Llanelli Radiators Ltd Condenser arrangement and heat exchanger system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10767933B2 (en) 2016-02-24 2020-09-08 Alfa Laval Corporate Ab Heat exchanger plate for a plate heat exchanger, and a plate heat exchanger

Also Published As

Publication number Publication date
WO2003054468A1 (de) 2003-07-03
EP1456591A1 (de) 2004-09-15
DE50210002D1 (de) 2007-05-31
DE10160380A1 (de) 2003-06-18
JP2005513404A (ja) 2005-05-12

Similar Documents

Publication Publication Date Title
DE69004220T2 (de) Wärmetauscher mit einer umfangsförmigen Zirkulation.
DE69509469T2 (de) Kühlmittelverdampfer
EP3119623B1 (de) Heizkühlmodul
EP1682840B1 (de) Wärmeübertrager, insbesondere für kraftfahrzeuge
EP1985953B1 (de) Wärmetauscher, insbesondere zur Abgaskühlung, Verfahren zum Betreiben eines solchen Wärmetauschers und System mit einem Abgaskühler
EP1626238B1 (de) Wärmetauscher, bestehend aus Flachrohren
DE69310842T2 (de) Wärmetauscher
DE112016004446T5 (de) Kühlsystem mit integrierter Kernstruktur
EP1456591B1 (de) Vorrichtung zur wärmeübertragung
DE19719254B4 (de) Sammler eines Wärmetauschers für Kraftfahrzeuge mit Kammerunterteilung aus sich kreuzenden Flachstegen
DE3319521C2 (ja)
DE60310992T2 (de) Hochdruckwärmetauscher
DE102006049106A1 (de) Wärmetauscher
DE102020204271A1 (de) Wärmetauscheranordnung mit integriertem Ventil und Druckbypass
DE202019102083U1 (de) Kühlfluiddurchströmte Wellrippenanordnung und Kraftfahrzeugbauteil
EP1600314B1 (de) Anordnung in einem Kältemittelkreislauf und Arbeitsverfahren
DE69618084T2 (de) Thermostatgehäuse für eine Brennkraftmaschine
DE102006016839A1 (de) Hochleistungswärmetauscher für Kraftfahrzeuge
DE69903350T2 (de) Ringförmiger wärmetauscher mit radialströmung
DE19547928C2 (de) Plattenwärmetauscher
EP1734324A2 (de) Verstellbarer innerer Wärmeübertrager
EP2886991B1 (de) Wärmeübertrager
EP0910780A1 (de) Sammler eines wärmetauschers für kraftfahrzeuge mit mindestens zweiteiligem gehäuseaufbau
EP2735833A2 (de) Verdampfer zur teilweisen oder vollständigen Verdampfung eines Flüssigkeitsstromes
EP2194245A2 (de) Öl-Abgas-Kühlmodul für eine Verbrennungskraftmaschine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20040712

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR IE IT LI LU MC NL PT SE SK TR

17Q First examination report despatched

Effective date: 20050408

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RBV Designated contracting states (corrected)

Designated state(s): DE FR

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 50210002

Country of ref document: DE

Date of ref document: 20070531

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20080121

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080818

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20081024

Year of fee payment: 7

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20100430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100302

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090831