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EP3635320B1 - Dispositif de récupération de chaleur d'un fluide chauffant - Google Patents

Dispositif de récupération de chaleur d'un fluide chauffant Download PDF

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Publication number
EP3635320B1
EP3635320B1 EP18728066.4A EP18728066A EP3635320B1 EP 3635320 B1 EP3635320 B1 EP 3635320B1 EP 18728066 A EP18728066 A EP 18728066A EP 3635320 B1 EP3635320 B1 EP 3635320B1
Authority
EP
European Patent Office
Prior art keywords
fluid
tube
heat exchanger
flow duct
duct
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.)
Active
Application number
EP18728066.4A
Other languages
German (de)
English (en)
Other versions
EP3635320A1 (fr
Inventor
Jens Gockel
Hilmar LÄMMER
Christian Urban
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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Filing date
Publication date
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Publication of EP3635320A1 publication Critical patent/EP3635320A1/fr
Application granted granted Critical
Publication of EP3635320B1 publication Critical patent/EP3635320B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • 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
    • F28D7/10—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 arranged one within the other, e.g. concentrically
    • F28D7/106—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 arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial 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
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • 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
    • F28F2250/06—Derivation channels, e.g. bypass

Definitions

  • the invention relates to a device for heat recovery from a heating fluid that flows through a heating fluid tract when a heating fluid generator is in operation, having a channel closure element and a heat exchanger arrangement, the heat exchanger arrangement having a main flow channel surrounded by a secondary flow channel, here the main flow channel and secondary flow channel each having at least one inlet and at least one downstream of the inlet formed outlet for throughflow by means of the heating fluid, a volume flow of the heating fluid through the main flow channel and / or the secondary flow channel can be regulated depending on an opening rate of the channel closure element, the channel closure element is arranged downstream of the outlets of the main flow channel and the secondary flow channel of the heat exchanger arrangement and the secondary flow channel is arranged via the Outlet of the secondary flow channel with an inlet and an outlet aufwe isenden closure bypass channel is connected in a fluid-permeable manner.
  • EP 1 884 634 discloses an apparatus according to the preamble of claim 1.
  • a challenge of modern motor vehicle construction is the lofty goal of continuously minimizing fuel consumption and, associated with this, the pollutant emissions of an internal combustion engine in the motor vehicle.
  • the steam generator here has a housing with an inlet and an outlet area, a tubular feed-through line extending from the inlet to the outlet area being arranged inside and coaxially to the housing.
  • This feed-through line is also slotted at its end sections located in the inlet and outlet area, so that the exhaust gas flowing into the steam generator can get into a space between the housing wall and the feed-through line. In this space is adjacent to the Through line arranged a spiral tube through which a fluid to be evaporated flows.
  • the spiral tube which in one embodiment has disk-like ribs to increase the heat transfer, serves as a heat transfer module, via which the thermal energy present in the exhaust gas is transferred to the fluid to be evaporated.
  • a control flap is arranged within the steam generator, more precisely within the feed-through line, by means of which the feed-through line is in a closed or open state depending on the position of the control flap.
  • the control flap is preferably arranged in the inlet area, with the exhaust gas passing through the slotted end area of the lead-through line into the space between the lead-through line and the housing when the lead-through line is closed and flows over the spiral tube.
  • the exhaust gas passes directly from the inlet to the outlet area, bypassing the intermediate area, which largely prevents heat transfer from the exhaust gas into the fluid to be evaporated.
  • a disadvantage of the described arrangement is in particular the positioning of the control flap within the steam generator, since this means that the flap shaft moving the locking flap must have a great length in order to reach into the interior of the feed-through line. This requires low manufacturing tolerances for the valve shafts and their storage, which, in connection with the temperatures reached in the exhaust tract, leads to distortion and malfunctions of the shut-off valve.
  • the DE 10 2011 056 212 A1 describes a similarly designed arrangement for the recovery of thermal energy from an exhaust gas for heating transmission oil, in which the control flap is arranged within the feed-through line, but in the outlet area, and the feed-through line also only in the outlet area via openings for the transition of the exhaust gas into the intermediate area between Feedthrough line and housing wall has.
  • the feed-through line is also closed by means of the control flap.
  • two interconnected, annular chambers for receiving a coolant are formed, around which the exhaust gas directed into the intermediate space flows for the purpose of heat transfer.
  • a spiral tube through which the transmission oil flows is arranged within one of the chambers.
  • DE 10 2012 105 588 A1 an essentially the function of the DE 10 2011 056 212 A1 corresponding arrangement for the recovery of thermal energy is known, which is also used to heat transmission oil.
  • the arrangements disclosed do not apply to a spiral tube.
  • the arrangement shows separate, but adjoining and coaxially running, annular chambers for receiving coolant and gear oil, with several mat-like tube bundles extending in a straight line in the longitudinal direction of the arrangement being arranged within the coolant chambers, through which exhaust gas flows over Openings in the lead-through line is passed into an end-face intermediate area between the lead-through line and the housing.
  • the tube bundles have a plurality of individual tubes which run essentially both parallel to one another and parallel to the lead-through line.
  • a central section of the individual tubes has a wall that is essentially spiral-shaped in order to enlarge its surface.
  • the disadvantage of such individual pipes running parallel to one another and parallel to the feed-through line is the possibility that the exhaust gas flowing through the individual pipes can be subject to an uneven distribution over the individual pipes and, as a result, in the case of a coolant that is to be evaporated, evaporation can sometimes not occur.
  • the EP 2 942 500 A1 a heat exchanger with an internal bypass pipe and a control flap arranged on the inlet side can also be seen in order to direct an exhaust gas flow through a heat exchanger duct or the bypass pipe.
  • a spiral tube through which a medium can flow is arranged around the bypass tube in the heat exchanger duct.
  • the WO 03/040 641 A1 shows a heat exchanger with an internal bypass tube, which is also surrounded by a spiral tube.
  • a regulating flap is again arranged, by means of which the flow of a first medium through the bypass pipe can be adjusted.
  • each cylindrical heat exchanger can be found for arrangement in an exhaust tract.
  • a bypass consisting of an inner pipe can be closed by means of a flap arranged downstream, so that exhaust gas flows into one via openings formed on the inlet side Flow area is passed between the inner pipe and a corrugated pipe section functioning as a separating element.
  • cooling water is also conducted in a cooling water area between the corrugated pipe section and the outer housing of the heat exchanger.
  • the invention is based on the object of designing a device of the type mentioned at the outset in such a way that, compared to the prior art, the construction is simplified, greater manufacturing tolerances are possible and malfunctions can thereby be minimized.
  • a device for heat recovery from a heating fluid the heating fluid flowing through a heating fluid tract when a heating fluid generator is in operation.
  • the device has a channel closure element and a heat exchanger arrangement, the heat exchanger arrangement also having a main flow channel surrounded by a secondary flow channel.
  • the main flow channel and secondary flow channel each have at least one inlet and at least one outlet formed downstream of the inlet for the flow of the heating fluid through, with at least one heat exchanger element through which a working fluid can flow during operation of the device being arranged in the secondary flow channel and a volume flow of the heating fluid through the main flow channel and / or the secondary flow channel can be regulated as a function of an opening rate of the channel closure element, so z.
  • the channel closure element is arranged downstream of the outlets of the main flow channel and the secondary flow channel of the heat exchanger arrangement.
  • the device for heat recovery is arranged in the heating fluid tract, with at least the inlet of the main flow channel connected to a first section of the heating fluid tract in a fluid-permeable manner upstream of the device, and the device downstream of the closure device being able to open into a second section of the heating fluid tract.
  • the heating fluid is diverted downstream of the closure device into an aftertreatment system or the environment.
  • the length of the main flow channel would be downstream be limited in its longitudinal extent by the channel closure element, the heating fluid tract would in turn connect downstream of the channel closure element.
  • the main flow channel and the heating fluid tract are made in one piece and the main flow channel thus forms a section of the heating fluid tract. A two-part or multi-part design is still possible.
  • the heat exchanger arrangement of the device in itself also has no channel closure element. This is arranged downstream of the heat exchanger arrangement, which on the one hand simplifies the structure of the heat exchanger arrangement and on the other can advantageously be used channel closure elements which, for. B. are already available on the market and thus susceptible special solutions with high manufacturing tolerances can be avoided.
  • the heat exchanger arrangement of the device should also preferably work on the countercurrent principle, i. H. the flow direction of the heating fluid and the working fluid are opposite to each other.
  • the direct current principle it is also conceivable to use the direct current principle.
  • the closure element should have at least two states, wherein the closure element should preferably also be able to assume further continuously or discretely changeable intermediate states between these two states.
  • One of the at least two states could be described here by a maximum opening rate, ie a counter pressure in the main flow channel of the heat exchanger arrangement caused by the closure element is minimal, so the heating fluid is only minimally prevented from flowing through the main flow channel. In such a state, no or essentially a minimal volume flow component of the heating fluid would flow through the secondary flow channel, as a result of which the main flow channel acts as a bypass of the secondary flow channel.
  • a second of the at least two states could correspondingly be described by a minimum opening rate of the closure element, which means that in this state the counterpressure in the main flow channel caused by the closure element would be maximum.
  • the heating fluid would thus be prevented to the maximum from flowing through the main flow channel, so that no or a minimal volume flow component of the heating fluid would flow through the main flow channel or a maximum volume flow component would flow through the secondary flow channel.
  • the necessary actuation of the closure element could be implemented, for example, via an electrical or pneumatic actuator.
  • the described opening rate is determined here from the ratio of the cross-sectional area of the main flow channel through which flow can flow to the total cross-sectional area of the main flow channel.
  • the thermal energy or heat present in the heating fluid is transferred into the working fluid via the heat transfer element.
  • the working fluid should at least be heated, but preferably evaporated.
  • the working fluid should also be part of a subsequent cycle in which it could be used in a gaseous state to drive a generator, for example.
  • the closure element can be designed as a flap, in particular as an exhaust flap, wherein the angular position of the flap or the exhaust flap should determine its opening rate.
  • the flap or exhaust flap in a first state of maximum opening rate, could be oriented at an angle of rotation of 0 degrees or 180 degrees to the flow direction of the heating fluid or correspondingly to the longitudinal direction of the main flow channel.
  • a second state i.e. in the state of minimum opening rate, there would be an angular position of the flap or exhaust flap with an angle of rotation of 90 degrees or 270 degrees to the flow direction of the heating fluid and / or to the longitudinal direction of the main flow channel.
  • the heating fluid can in particular be designed as an exhaust gas which flows through the exhaust gas tract, in particular the exhaust gas tract of an internal combustion engine, the internal combustion engine representing the corresponding heating fluid generator.
  • the heating fluid tract would consequently the exhaust gas tract, in particular the exhaust gas tract of the internal combustion engine, such as. B. correspond to an internal combustion engine of a motor vehicle.
  • the working fluid should be in the form of a fluid which, as a result of the heat transferred from the heating fluid through the heat transfer element, passes from the liquid into the gaseous phase, that is to say can be evaporated.
  • a fluid which, as a result of the heat transferred from the heating fluid through the heat transfer element, passes from the liquid into the gaseous phase, that is to say can be evaporated.
  • water but also alcohols such as ethanol, are suitable for such a working fluid.
  • refrigerants of various types could be used as the working fluid.
  • the secondary flow channel of the heat exchanger arrangement is connected in a fluid-permeable manner to the main flow channel of the heat exchanger arrangement exclusively via the inlet of the secondary flow channel. Accordingly, it is between the outlet of the secondary flow channel and the main flow channel have no or no direct fluid-permeable connection, which in particular leads to the fact that the structure of the heat exchanger arrangement is simplified and that it is therefore less susceptible to faults.
  • the fluid-permeable connection in this context means a substance-permeable connection which is permeable at least to fluids and gases. However, permeability for solid substances is not excluded. It is also to be taken for granted that energy can also be transmitted via this fluid-permeable connection.
  • the closure bypass channel is designed as at least one overflow pipe, which is arranged downstream of the heat exchanger arrangement on the housing of the heat exchanger arrangement and the heating fluid tract and thereby connects the secondary flow channel on the outlet side, bypassing the channel closure element, so that the heating fluid from the secondary flow channel into the Heating fluid tract can flow.
  • the overflow pipe should be arranged in such a way that a first end face of the overflow pipe is connected to the housing of the heat exchanger arrangement upstream and a second end of the overflow pipe is connected to the heating fluid tract downstream in a fluid-permeable manner.
  • the overflow pipe could also run in sections parallel to the main flow channel and / or to the heating fluid tract.
  • the closure bypass channel in the form of an overflow pipe arranged outside the main flow channel and / or the heating fluid tract advantageously offers a structurally and manufacturing-technically simpler structure than, for example, one inside the main flow channel and / or the heating fluid tract, e.g. B. in the form of a pipe-in-pipe design, arranged overflow pipe.
  • An embodiment of the invention is also to be regarded as advantageous when the secondary flow channel is connected in a fluid-permeable manner via the outlet of the secondary flow channel to a closure bypass channel having an inlet and an outlet.
  • Such a configuration beneficially makes it possible for the heating fluid not to build up in the secondary flow channel, which in a positive manner prevents possible overheating of the heat exchanger element and / or of the working fluid flowing in the heat exchanger element.
  • the closure bypass channel is connected in a fluid-permeable manner to the heating fluid tract via the outlet of the closure bypass channel downstream of the channel closure element, then it is possible that the heating fluid that has flowed over from the secondary flow channel into the closure bypass channel can be returned to the heating fluid tract, whereby profitably no counter pressure in the closure bypass channel and / or is generated in the secondary flow channel and the discharge of the heating fluid is made possible while bypassing the channel closure element.
  • This is of particular importance when the channel closure element is in a state in which it does not have its maximum opening rate and thus the main flow channel is partially or completely closed, whereby a corresponding volume flow portion of the heating fluid flows into the secondary flow channel.
  • the main flow channel is formed by a fluid pipe enclosed by a housing, the housing enclosing the fluid pipe orthogonally to the longitudinal direction of the fluid pipe.
  • a correspondingly coaxial arrangement of the housing and fluid pipe is conceivable here, with the fluid pipe in the simplest case being able to be designed as a cylinder pipe.
  • the fluid tube should not be completely enclosed by the housing, but only orthogonally to and in the longitudinal direction of the fluid tube, so that the end faces of the fluid tube forming the inlet and outlet of the skin flow channel are not enclosed by the housing.
  • such a configuration offers a basic structure of the heat exchanger arrangement that is less prone to faults.
  • the inlet of the secondary flow channel is formed by at least one opening formed in the wall of the fluid pipe, this opening being in a region of the fluid pipe which is enclosed by the housing and thereby the Main flow channel connects to the secondary flow channel in a fluid-permeable manner.
  • the opening can assume any shape, for example a circular, oval or elliptical shape. It is also conceivable that the opening is in the form of a slot. In addition to a single opening, however, an embodiment with a plurality of openings is preferred, wherein these can be arranged at a distance from one another in the circumferential direction of the fluid tube.
  • the secondary flow channel is formed by a fluid space which is formed between the fluid tube and the housing surrounding the fluid tube, then it can be assumed that this is an extremely less error-prone configuration of the secondary flow channel of the heat exchanger arrangement.
  • at least the two end regions of the housing should be connected to the fluid pipe in a fluid-impermeable manner, it being possible for the connection to be made cohesively and also non-positively and / or positively.
  • the length of the secondary flow channel would be determined by this configuration via the longitudinal extent of the housing, in particular by the spacing of the end regions of the housing.
  • the heat exchanger element is designed as a spiral tube through which the working fluid can flow and / or ribs formed on an outer surface of the spiral tube and in the longitudinal direction of the tube, at least in sections, in the opposite direction to the central axis of the tube is arranged.
  • a design of the heat exchanger element as a coiled tubing offers the advantage over a possible design variant with several individual tubes running in a straight line and essentially parallel to one another and parallel to the main and secondary flow channels that there is no uneven distribution of the volume flow of the heating fluid.
  • the raw coil in such a way that ribs are formed on its outer jacket surface increases the heat flow from the heating fluid into the working fluid, whereby the efficiency of the heat transfer can be increased.
  • the ribs are formed by applying an endless belt which is spirally wound in the longitudinal direction of the tube and which is cut to length according to the length of the section on the tube carrying the ribs at least in sections.
  • the connection between the endless belt forming the ribs and the tube can be formed with a material fit, whereby the material connection can be produced using a welding process, in particular a laser welding process.
  • such a described tube can for example have an outer diameter of eight millimeters with a wall thickness of 0.75 millimeters and the endless belt forming the ribs can have a width of five millimeters and a thickness of 0.5 millimeters.
  • a further advantageous embodiment of the device can be designed in that a deformable intermediate insert which surrounds the fluid pipe and / or the coiled pipe orthogonally to the longitudinal direction of the fluid pipe is arranged between the fluid pipe and the coiled pipe and / or between the coiled pipe and the housing which the fluid tube and the coiled tubing and / or the raw coil and the housing are in contact.
  • the intermediate insert is elastically and / or plastically deformable and is present, for example, as a woven, knitted and / or knitted fabric.
  • Felt mats and / or fiber mats such as. B. fiberglass mats and in particular silicate fiberglass mats.
  • the intermediate insert can also be generally flat and flat, with such an intermediate insert being folded over or applied around the fluid pipe and / or the inner jacket surface of the housing so that the intermediate layer adapts to the respective contour.
  • the intermediate insert could, however, also be in the form of a hollow cylinder, quasi in the form of a flexible pipe or a cuff, so that it can be pushed onto the fluid pipe and / or inserted between the coiled pipe and the housing.
  • the intermediate insert can also be present as a solid material.
  • the intermediate insert can be designed as an insulation element and / or a sealing element, whereby on the one hand the heat flow into the environment and possibly into the main flow channel, ie z. B. the fluid tube can be minimized.
  • the intermediate insert were laminated with a layer that reflects thermal radiation, such as a stainless steel foil, for example.
  • This lamination would also have the advantage that the volume flow of the heating fluid, due to its flow velocity, cannot entrain any parts of the intermediate layer.
  • B. should be prevented when using interlayers consisting of fibers in order to prevent a steady reduction in the interlining and thus a defect. Since the intermediate insert or the intermediate inserts are in contact with the fluid pipe, the coiled tubing and the housing, they can also fulfill the function of a sealing element.
  • the intermediate inserts is used to compensate for tolerances between the fluid pipe and the coiled pipe and / or the coiled pipe and the housing.
  • FIG. 1 shows a perspective view of a further development of the device 1 according to the invention for heat recovery from a heating fluid.
  • This heating fluid flows through the heating fluid tract 2 when a heating fluid generator is in operation.
  • the device 1 has the channel closure element 3 and the heat exchanger arrangement 4, which consists of the secondary flow channel 5, the main flow channel 6 and the heat exchanger element 11.
  • the heat exchanger element 11 is designed as a tube coil 22 from the spiral tube 23.
  • the volume flow of the heating fluid through the main flow channel 6 and / or the secondary flow channel 5 can be regulated as a function of the opening rate of the channel closure element 3 arranged downstream of the heat exchanger arrangement 4.
  • the secondary flow channel 5 is also connected to the main flow channel 6 in a fluid-permeable manner exclusively via the inlet 7 of the secondary flow channel 5.
  • the heating fluid flows via the inlet 7 into the secondary flow channel 5.
  • the working fluid flowing in the heat exchanger element 11 during operation of the heat exchanger arrangement 4 is heated into the working fluid due to the heat flow from the heating fluid via the heat exchanger element 11.
  • the heating fluid flows back into the heating fluid tract 2 via the locking bypass channel 14.
  • the channel locking element is open, the heating fluid flows through the main flow channel 6 by bypassing the secondary flow channel 5 and immediately returns to the heating fluid tract 2.
  • Figure 2 also shows a further development of the device 1, this being shown in section.
  • the device 1 again shows the channel closure element 3 and the heat exchanger arrangement 4.
  • the heat exchanger arrangement 4 has the from Main flow channel 6 surrounding secondary flow channel 5, main flow channel 6 having inlet 9 and outlet 10 and secondary flow channel 5 having inlets 7 and outlet 8.
  • the main flow channel 6 is formed by the fluid pipe 16 enclosed by the housing 15, the housing 15 enclosing the fluid pipe 16 orthogonally to the longitudinal direction 17 of the fluid pipe 16.
  • the secondary flow channel 5 is connected to the main flow channel 6 in a fluid-permeable manner exclusively via the inlets 7 of the secondary flow channel 5, the inlets 7 being formed by the openings 19 formed in the wall 18 of the fluid pipe 16.
  • the heat exchanger element 11 is also arranged in the secondary flow channel 5, which is formed by the fluid space 20 which is formed between the fluid pipe 16 and the housing 15, the heat exchanger element 11 is also arranged.
  • the heat exchanger element 11 is designed as a coiled tubing 22, which runs in a spiral around the fluid tube 16.
  • the deformable intermediate insert 27 enclosing the coiled tubing 22 orthogonally to the longitudinal direction 25 of the fluid pipe 16, with which the coiled tubing 22 and the housing 15 are also in contact.
  • the channel closure element 3 is arranged downstream of the outlets 10, 8 of the main flow channel 6 and the secondary flow channel 5, this being designed as a flap in this development and the angular position of the channel closing element 3 designed as a flap determining its opening rate.
  • the channel closure element 3 designed as a flap is in its second state, that is to say in the state of the minimum opening rate, the main flow channel 6 being quasi closed.
  • Figure 2 also shows that the secondary flow channel 5 is connected in a fluid-permeable manner via its outlet 8 to the inlet 12 of the closure bypass channel 14 and the closure bypass channel 14 is in turn connected to the heating fluid tract 2 via its outlet 13 downstream of the channel closure element 3.
  • the closure bypass channel 14 is designed as the overflow pipe 21, as shown.
  • This overflow pipe 21 is also arranged downstream of the heat exchanger arrangement 4 on the housing 15 and the heating fluid tract 2 in such a way that its first face end is connected in a fluid-permeable manner upstream to the housing 15 of the heat exchanger arrangement 4 and its second face end downstream is connected to the heating fluid tract 2.
  • the overflow pipe 21 runs in a section parallel to the main flow channel 6 and to the heating fluid tract 2.
  • Figure 3 is the device 1 in contrast to Figure 2 shown with the channel closure element 3 designed as a flap in its first state with a corresponding maximum opening rate.
  • the flow of the heating fluid through the main flow channel 6 is thus at a maximum.
  • Figure 4 describes a further development of the basically spiral-shaped tube 23, which the in Figures 1 to 3 shown coiled tubing 22 forms.
  • ribs 26 formed in opposite directions are arranged on the outer circumferential surface 24 of the tube 23 and in the longitudinal direction 25 of the tube 23 of the central axis 28 of the tube 23.
  • the ribs 26 are formed in that a cut-to-length endless belt is applied to the tube 23, spiraling around the tube 23 in the longitudinal direction 25 of the tube 23.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (8)

  1. Dispositif (1) de récupération de chaleur à partir d'un fluide de chauffage qui s'écoule à travers un conduit de fluide de chauffage (2) lorsqu'un générateur de fluide de chauffage est en fonctionnement, ledit dispositif comportant un élément de fermeture de canal (3) et un ensemble échangeur de chaleur (4), l'ensemble échangeur de chaleur (4) comportant un canal d'écoulement principal (6) entourant un canal d'écoulement secondaire (5), le canal d'écoulement principal (6) et le canal d'écoulement secondaire (5) comportant chacun au moins une entrée (7, 9) et au moins une sortie (8, 10), ménagée en aval de l'entrée (7, 9), qui sont destinées être traversées par le fluide de chauffage, un débit volumique du fluide de chauffage à travers le canal d'écoulement principal (6) et/ou le canal d'écoulement secondaire (5) pouvant être régulé en fonction d'un débit d'ouverture de l'élément de fermeture de canal (3), l'élément de fermeture de canal (3) étant disposé en aval des sorties (8, 10) du canal d'écoulement principal (6) et du canal d'écoulement secondaire (5) de l'ensemble échangeur de chaleur (4) et le canal d'écoulement secondaire (5) étant relié en communication fluidique, par le biais de la sortie (8) du canal d'écoulement secondaire (5), à un canal de dérivation de fermeture (14) comportant une entrée (12) et une sortie (13), caractérisé en ce qu'au moins un élément échangeur de chaleur (11), pouvant être traversé par un fluide de travail pendant le fonctionnement du dispositif (1), est disposé dans le canal d'écoulement secondaire (5), et le canal de dérivation de fermeture (14) est conçu sous la forme d'au moins un tube de trop-plein (21) qui est disposé en aval de l'ensemble échangeur de chaleur (4) au niveau du boîtier (15) de l'ensemble échangeur de chaleur (4) et du circuit de fluide de chauffage (2).
  2. Dispositif (1) selon la revendication 1, caractérisé en ce que le canal d'écoulement secondaire (5) de l'ensemble échangeur de chaleur (4) est relié en communication fluidique au canal d'écoulement principal (6) de l'ensemble échangeur de chaleur (4) exclusivement par le biais de l'entrée (7) du canal d'écoulement secondaire (5).
  3. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce que le canal de dérivation de fermeture (14) est relié en communication fluidique au conduit de fluide de chauffage (2) par le biais de la sortie (13) du canal de dérivation de fermeture (14) en aval de l'élément de fermeture de canal (3).
  4. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce que le canal d'écoulement principal (6) est formé par un tube de fluide (16) qui est entouré par un boîtier (15), le boîtier (15) entourant le tube de fluide (16) orthogonalement à la direction longitudinale (17) du tube de fluide (16).
  5. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce que l'entrée (7) du canal d'écoulement secondaire (5) est formée par au moins une ouverture (19) ménagée dans la paroi (18) du tube de fluide (16).
  6. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce que le canal d'écoulement secondaire (5) est formé par un espace de fluide (20) qui est ménagé entre le tube de fluide (16) et le boîtier (15) enfermant le tube de fluide (16).
  7. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce que l'élément échangeur de chaleur (11) est réalisé sous la forme d'un tube hélicoïdal (22), pouvant être traversé par le fluide de travail, à partir d'un tube (23) s'étendant en spirale et/ou des nervures (26) formées dans des directions opposées sont disposées sur une surface d'enveloppe extérieure (24) du tube (23) s'étendant en spirale et dans la direction longitudinale (25) du tube (23) au moins par portions de l'axe central (16) du tube (23).
  8. Dispositif (1) selon l'une au moins des revendications précédentes, caractérisé en ce qu'un insert intermédiaire déformable (27), qui enferme le tube de fluide (16) et/ou le tube hélicoïdal (22) orthogonalement à la direction longitudinale (25) du tube de fluide (16), est disposé entre le tube de fluide (16) et le tube hélicoïdal (22) et/ou entre le tube hélicoïdal (22) et le boîtier (15) et permet de mettre le tube de fluide (16) et le tube hélicoïdal (22) et/ou le tube hélicoïdal (22) et le boîtier (15) en contact l'un avec l'autre.
EP18728066.4A 2017-06-08 2018-05-22 Dispositif de récupération de chaleur d'un fluide chauffant Active EP3635320B1 (fr)

Applications Claiming Priority (2)

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DE102017209725.6A DE102017209725A1 (de) 2017-06-08 2017-06-08 Vorrichtung zur Wärmerückgewinnung aus einem Heizfluid
PCT/EP2018/063265 WO2018224295A1 (fr) 2017-06-08 2018-05-22 Dispositif de récupération de chaleur d'un fluide chauffant

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EP3635320B1 true EP3635320B1 (fr) 2021-07-07

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RU196876U1 (ru) * 2020-01-31 2020-03-18 Тамара Ивановна Носова Устройство для подогрева жидкостей двигателя внутреннего сгорания
CN112595146B (zh) * 2020-12-29 2023-09-12 乔治洛德方法研究和开发液化空气有限公司 管道壳体由换热设备构成的高温流体运输管道、适用的换热设备以及换热方法
CN112577338B (zh) 2020-12-30 2023-07-25 乔治洛德方法研究和开发液化空气有限公司 内部安置有换热设备的高温流体运输管道，适用的换热设备及换热方法

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US4371027A (en) * 1975-09-10 1983-02-01 Jacobsen Orval E Economizer with an integral gas bypass
JP4434401B2 (ja) * 2000-01-19 2010-03-17 本田技研工業株式会社 内燃機関の排気浄化装置
CA2466564A1 (fr) * 2001-11-09 2003-05-15 Aalborg Industries A/S Echangeur de chaleur, dispositif comprenant un echangeur de chaleur et procede de fabrication de cet echangeur de chaleur
US20050133202A1 (en) * 2001-11-09 2005-06-23 Aalborg Industries A/S Heat exchanger, combination with heat exchanger and method of manufacturing the heat exchanger
JP2006250524A (ja) * 2005-02-14 2006-09-21 Sango Co Ltd 多重管式熱回収器
JPWO2006090725A1 (ja) * 2005-02-23 2008-07-24 株式会社三五 排気熱回収装置
JP2008038723A (ja) * 2006-08-04 2008-02-21 Toyota Motor Corp 排気系熱交換器の支持構造
KR101241211B1 (ko) 2010-12-09 2013-03-13 현대자동차주식회사 차량의 배기열 회수장치
KR101317373B1 (ko) 2011-12-09 2013-10-10 현대자동차주식회사 열교환기
DE102012204126A1 (de) 2012-03-15 2013-09-19 Eberspächer Exhaust Technology GmbH & Co. KG Dampferzeuger für einen Rankine-Prozess
RU132877U1 (ru) * 2013-03-26 2013-09-27 Общество с ограниченной ответственностью "Краснодарский Компрессорный Завод" Вертикальный межступенчатый газоохладитель
DE102014106386B4 (de) * 2014-05-07 2016-08-11 Benteler Automobiltechnik Gmbh Abgaswärmetauscher mit Bypassrohr

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RU2727499C1 (ru) 2020-07-21
EP3635320A1 (fr) 2020-04-15
WO2018224295A1 (fr) 2018-12-13

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