EP2136160A2 - Unité de construction intégrée comprenant un collecteur et un échangeur thermique interne et procédé de fabrication de l'unité de construction - Google Patents

Unité de construction intégrée comprenant un collecteur et un échangeur thermique interne et procédé de fabrication de l'unité de construction Download PDF

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Publication number
EP2136160A2
EP2136160A2 EP20090007585 EP09007585A EP2136160A2 EP 2136160 A2 EP2136160 A2 EP 2136160A2 EP 20090007585 EP20090007585 EP 20090007585 EP 09007585 A EP09007585 A EP 09007585A EP 2136160 A2 EP2136160 A2 EP 2136160A2
Authority
EP
European Patent Office
Prior art keywords
coiled tubing
tube
container
collector
section
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.)
Withdrawn
Application number
EP20090007585
Other languages
German (de)
English (en)
Inventor
Alexander Satrapa
Karl-Heinz Staffa
Ulrich Vedder
Christoph Walter
Wolfgang Geiger
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2136160A2 publication Critical patent/EP2136160A2/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size

Definitions

  • the invention relates to an integrated, a collector and an internal heat exchanger comprehensive unit according to the preamble of claim 1 and a method for producing the structural unit according to the preamble of claim 10th
  • Integrated assemblies comprising a collector and an internal heat exchanger for a refrigerant circuit are known, especially in CO 2 air conditioners.
  • the collector which is arranged in the flow direction behind an evaporator of the refrigerant circuit, the task of separating the liquid and gaseous phase of the refrigerant vapor from each other and also act as a refrigerant reservoir.
  • the inner heat exchanger which is arranged in the flow direction behind a gas cooler of the refrigerant circuit, represents a thermal coupling of the high pressure side (gas cooler) and the low pressure side (evaporator) and thus enables heat transfer from the hot to the cold refrigerant side.
  • the Applicant has disclosed an integrated header heat exchanger assembly in which a high pressure tube formed as a coiled tubing is disposed in an annular gap between a header outer wall and a header housing inner wall and is fluid tight against both the inner and outer walls. This creates a helical channel through which the low pressure refrigerant flows in countercurrent to the high pressure refrigerant in the coiled tubing.
  • the problem with this design is the introduction of the coiled tubing in the annular gap between the two cylinder walls. During the axial insertion of the coiled tubing in the annular gap, there is a risk that the coiled tubing scratched against the cylinder walls and thereby chips can be formed, which would be very harmful for the refrigerant circuit.
  • the object of the invention is solved by the features of claim 1.
  • the coiled tubing with the inner and outer wall, which form the annular gap forms a frictional connection.
  • the coiled tubing is thus frictionally against the cylinder walls both inside and outside and forms a press fit with these.
  • the coiled tubing is frictionally fixed relative to the two cylinders of the housing shell and collector.
  • the adhesion is caused by radial forces, which result from an elastic tensile stress of the housing shell and a compressive stress of the collector wall.
  • By frictional engagement of the coiled tubing a defined helical flow channel between the turns of the coiled tubing is formed, so that there is a good efficiency for the internal heat exchanger.
  • ringing noises and signs of wear are reliably avoided. Additional constructive aids, for example, for fixing the collecting container are superfluous. The construction becomes lighter and easier.
  • the frictional connection between coiled tubing and the cylinder walls is achieved by a plastic deformation of the coiled tubing, d. H. by a deformation which lies outside the elastic range of the material of the coiled tubing and is not subject to re-deformation. This is a permanent adhesion, combined with a work hardening of the pipe material achieved.
  • the collector is made of a plastic material, in particular a polyamide with the commercial name PA66.
  • a plastic material in particular a polyamide with the commercial name PA66.
  • PA66 commercial name PA66
  • the collector may be double-walled, z. B. with a metallic cylinder, which is thermally insulated by an inner or outer plastic cylinder or other insulating layer.
  • a profiled tube cross-section can be used, for. B. a profiled on the outside extruded tube.
  • the profile on the outside can be rectangular, tooth-shaped, wavy or triangular.
  • the advantage thus achieved is that the contact surface of the high-pressure tube on the inner cylinder (the collecting container) and thus the heat transfer can be reduced.
  • the tube can also be provided with an asymmetrical profile, whereby the inner cylinder a minimal investment and on the outer cylinder (housing shell) an enlarged contact surface is achieved.
  • the outer profile of the high-pressure tube can be designed such that a constant distance is maintained between the tube turns.
  • the coiled tube on pipe ends which are guided by a lid and / or a bottom of the assembly and rolled or rolled in the lid or the floor.
  • This achieves the advantage of a heat-tight fluid-tight, in particular gas-tight connection between the tube coil and the housing of the structural unit.
  • a fixation of the coiled tubing is achieved by the rolling, ie a plastic deformation of the tube material.
  • single-roller rolling is particularly advantageous as a result of the lack of heat input when there are plastic parts in the structural unit or on the structural unit. It is particularly advantageous if the openings in the bottom and lid undercuts, z. B.
  • the tube material can be hineinverdrlindt during rolling or curling in the wells, so that In addition to the adhesion and a positive connection results.
  • the connection can be loaded more strongly in the axial direction, ie the pull-out force for the tube is increased.
  • spacers are arranged between the bottom of the collector (the intermediate bottom) and the bottom of the assembly, which may be formed as pronounced nubs or as a spring element. This ensures a flow-through option for the low-pressure refrigerant vapor below the sump, so that the refrigerant can be extracted on the low-pressure side.
  • a circumferential annular groove is formed in the bottom of the assembly, in which engage the spacers.
  • the object of the invention is also achieved by the features of claim 10, wherein according to the invention the following method steps are provided: first, the coiled tubing is inserted with radial play in the annular gap and then expanded radially against the inner and outer walls.
  • the advantage is achieved that when inserting the coiled tubing no material contact, d. H. no chip formation and no scratching take place, but the parts to be mounted remain clean on their surface.
  • By widening a frictional and fluid-tight connection between the tube coil and cylinder walls is achieved and formed a helical flow channel.
  • the expansion takes place by means of a compressible or incompressible pressure medium, which is filled into the tube spiral and pressurized.
  • the coiled tube is subjected to an internal pressure, the so-called expansion pressure, which leads to an expansion of the tube cross-section and thus to a contact with the cylinder walls of the annular gap.
  • the expansion pressure depends on the material (yield strength), on the geometry of the pipe cross-section and the pipe wall thickness selected such that there is a sufficient adhesion or interference fit.
  • the expansion pressure is selected as a function of the bursting pressure to which the coiled tubing is designed with regard to the operating pressure.
  • the bursting pressure is approximately 1.1 to 1.5 times the expansion pressure. Preference is given to the largest possible ratio between bursting and expansion pressure, d. H. the lowest possible expansion pressure.
  • the expansion method according to the invention for the coiled tubing can be carried out without difficulty in terms of production engineering, in particular if a non-compressible medium such as water or oil is used as the pressure medium.
  • the tube cross-section of the coiled tube - before insertion into the annular gap and before the expansion - in the radial direction, d. H. in planes perpendicular to the winding axis of the coiled tubing shortened by forming: there is a so-called grading process by which the tube cross-section is flattened, planed, ovalized or formed into an elliptical cross-section.
  • This grading process has the advantage that the tube on the one hand easily, d. H. with radial play can be inserted into the annular gap and that the tube cross-section is deformed during expansion in a predetermined direction, for. B. outwards or inwards or on both sides the same or different. This avoids an uncontrolled widening of the coiled tubing and achieves a targeted installation of the coiled tubing on the inner and outer cylinders.
  • a profiled, preferably extruded tube for the inventive method d. H. the expansion process can be used.
  • the tube ends of the tube helix are rolled or rolled into the lid and / or the bottom of the structural unit before the tube helix is widened.
  • a fluid-tight and firm connection of the pipe ends with the housing of the unit is fixed and positioned within the housing of the unit before the expansion process. Therefore, no further fixing or positioning measures are required for the subsequent expansion process. This results in the advantage of a simple, safe installation and attachment of the coiled tubing in the unit.
  • Fig. 1 shows - in a half section - an integrated unit 1 as a component of a refrigerant circuit, not shown, for an air conditioning system of a motor vehicle, wherein as refrigerant preferably CO 2 , also known under the name R744, is used.
  • the integrated assembly 1 represents a combination of a refrigerant collector 2, also called collector 2 or collector 2 for short, and an internal heat exchanger 3, which comprises a coiled tube 4 with an inlet-side tube end 4a and an outlet-side tube end 4b.
  • the structural unit 1 has a housing 5 which comprises a cylindrical housing jacket 5a, a bottom 5b and a cover 5c.
  • the collector 2 is arranged coaxially with a cylindrical container jacket 2 a to form an annular gap 6.
  • the coiled tube 4 is arranged in the annular gap 6 and forms in each case with the inner wall of the housing shell 5a and the outer wall of the container shell 2a a non-positive connection, ie a press fit, which causes a fixation of the parts 2, 4, 5a against each other.
  • This arrangement creates between the turns of the coiled tubing 4, a helical flow channel 7, bounded by the outer walls of the coiled tubing 4, the inner wall of the housing shell 5a and the outer wall of the container shell 2a.
  • the coiled tubing 4 is also referred to as a high-pressure tube.
  • an approximately U-shaped suction pipe 8 is arranged, which has a pipe bend 8a with an attached oil filter 9, the function of which is known from the aforementioned prior art.
  • the housing bottom 5b and the housing cover 5c which are preferably welded to the housing jacket 5a, have four through holes 10, 11 for the high pressure inlet and high pressure outlet of the refrigerant, and 12, 13 for the low pressure inlet and low pressure outlet of the refrigerant.
  • the unit 1 is connected to the refrigerant circuit, not shown, with the high pressure inlet 10 downstream of a gas cooler, not shown, and the low pressure inlet 12 downstream of an evaporator, not shown, of the refrigerant circuit and the associated air conditioning ,
  • the pipe ends 4a, 4b are partially inserted into the through holes 10, 11 and rolled or rolled into the bottom 5b and in the lid 5c.
  • a fluid, in particular gas-tight connection of the pipe ends 4a, 4b with respect to the bottom 5b and lid 5c is achieved.
  • a pipe section 8b is pressed or rolled in the lower part.
  • the pipe section 8b of the low pressure inlet 12 communicates with the interior of the container 2.
  • Fig. 2 shows the container 2, also called collector or collection container, as a single assembly, wherein the same reference numerals for the same parts we in Fig. 1 be used.
  • the container 2 is preferably made of plastic, such as PA66, and in addition to the cylindrical container shell 2a and the bottom 2b a lid 2c, which has two openings for the passage of an outlet end 8c of the suction tube 8 and the tube section 8b, which with the lid 2c is connected.
  • the suction pipe 8 has an inlet end 8d, which opens into a gas filter 14. Further, a liquid separator 15 is disposed in the uppermost region of the container 2, immediately below the inlet-side pipe section 8b.
  • the function of an integrated collector-heat exchanger assembly is basically known from the aforementioned prior art, yet the operation of the in the FIGS. 1 and 2
  • the under high pressure refrigerant preferably CO 2
  • enters the unit 1 at the high pressure inlet 10 flows through the coiled tubing 4 (the high pressure pipe) from bottom to top and exits through the high pressure outlet 11 again of the unit 1 from.
  • the low-pressure refrigerant enters the assembly 1 at the low-pressure inlet 12, flows through the pipe section 8b into the interior of the collecting container 2, where it strikes the liquid separator 15 and flows around first radially outwards and then in the axial and tangential direction.
  • the liquid separator 15 is the subject of a simultaneous application of the applicant.
  • liquid refrigerant collects at the bottom 2b, the gaseous refrigerant enters through the gas filter 14 in the suction pipe 8, from which it emerges again via the outlet end 8c.
  • the low-pressure refrigerant vapor flows radially outward and enters the helical flow channel 7 between the turns of the coiled tubing 4 and flows through the flow channel 7 - from top to bottom - in countercurrent to the high-pressure refrigerant in the coiled tubing 4th After exiting the helical flow channel 7, the low-pressure refrigerant vapor flows under the bottom 2 b, from where it is sucked off via the low-pressure outlet 13.
  • Fig. 3a shows a circular tube cross section 16 of a coiled tubing, which is arranged in an annular gap 17 formed by two cylinder walls 18, 19.
  • the pipe cross-section 16 When the circular pipe cross-section 16 is acted upon with an internal pressure p 1 , the pipe cross-section would (in the ideal case) expand uniformly radially and also come to bear against the two cylinder walls 18, 19. Due to tolerance-related deviations of the pipe wall thickness, however, it can sometimes lead to uncontrolled widening.
  • Fig. 3b shows an elliptical tube cross-section 20 which is arranged with clearance in the annular gap 17.
  • the elliptical tube cross-section 20 is made by forming, a so-called grading, of a circular tube cross-section.
  • p i an internal pressure
  • the expansion pressure the tube cross-section will increase in the direction of the minor axis and decrease in the direction of the major axis. This achieves a defined widening direction, perpendicular to the cylindrical walls 18, 19, for the coiled tubing.
  • the expansion pressure for the elliptical cross section 20 is less than for the circular cross section 16 (FIG. Fig. 3a ).
  • Fig. 3c shows a further embodiment of a planarized tube cross-section 21, which has a flattened, parallel to the outer cylinder wall 19 extending side 21a.
  • Fig. 3d shows a further embodiment, namely an oval cross-section 22, which was prepared by forming from a circular pipe cross-section and is arranged here before expansion with clearance in the annular gap 17.
  • the flat sides 22a, 22b will initially bulge out, while the length of the oval will be shortened.
  • a defined contact with the cylinder walls 18, 19 is achieved by widening here, too.
  • the forming process or the so-called leveling can be performed by a correspondingly shaped pair of rollers, and immediately before winding the tube coil.
  • Fig. 4 shows a dimension of the elliptical cross-section 20 (see. Fig. 3b ) and the annular gap 17 with the cylinder walls 17, 18.
  • the small axis of the ellipse 20 is indicated by d and the gap width of the annular gap 17 with S.
  • the dimension d is also referred to as leveling, ie as the measure to which the output cross-section is compressed.
  • a preferred ratio of gap width S to leveling d is in the range of 1.05 to 1.15.
  • Fig. 5 shows a circular output pipe cross section with the diameter D and a planed elliptical cross section with the minor axis or the leveling d.
  • a preferred ratio of the pipe diameter D to the planing height d for the leveling and expansion process is in the range of 1.10 to 1.25.
  • Fig. 6 shows a profiled tube 23, which has on its circumference in the tube longitudinal direction extending ridges or ribs 23a.
  • the profiled tube 23 can preferably be produced by extrusion.
  • Fig. 6a is shown as a detail, the wall thickness w and the web height s (radial extent) of the webs 23a.
  • a preferred ratio of land height s to wall thickness w is in the range of 1.30 to 1.60.
  • Fig. 7 shows the wall thickness w of a circular pipe cross-section and the leveling d of an elliptical pipe cross-section.
  • Preferred ratios for the planing height d to the wall thickness w are in the range of 6.50 to 10.50.
  • FIGS. 8a, 8b, 8c show various embodiments for the isolation of a container shell.
  • Fig. 8a shows a double-walled cylindrical container shell 24, which has on its inside an insulating layer 24a; the outside is replaced by a metallic cylinder, z. B. formed an aluminum tube.
  • Fig. 8b shows a double-walled container casing 25, on the outside of which an insulating layer 25a is arranged.
  • the insulating layers 24a or 25a may also be inner or outer cylinders of a plastic material, which are pushed into the metallic or over the metallic cylinder.
  • Fig. 8c shows a fully insulated container shell 26, in which an outer layer 26a and an inner layer 26b are formed as Isolations füren- or cylinder.
  • Fig. 9 shows a cross section 27 of a profiled tube for a coiled tubing, which in the annular gap 17 between an inner cylinder 18 and a outer cylinder 19 is arranged.
  • the profile 27 is asymmetrical and has a pointed on the inner cylinder 18 tapered web 27a, whereby the contact surface and thus the heat conduction are reduced. When widening, the tip 27a digs into the cylinder wall 18, thus improving the seal.
  • Fig. 10 shows a further cross-sectional shape 28 for a coiled tubing, wherein the tube cross-section on the side to the inner cylinder 18 is unaffected and provided on the side to the outer cylinder 19 with a plurality of ribs 28a, 28b.
  • the heat conduction is reduced inwardly to the cylinder wall 18 and reinforced to the outer cylinder 19 out.
  • Fig. 11 shows a further embodiment with two in the annular gap 17 superposed profiled pipe sections 29, 30, wherein the webs or ribs 29a, 30a of adjacent pipe turns serve as spacers and thus ensure a defined distance of the pipe turns, especially after the expansion process.
  • flow channels are created with a defined cross section and therefore with a defined pressure drop for the flow medium (low pressure refrigerant vapor).
  • Fig. 12 shows a profiled tube cross section 31, which shows a combination of the cross sections 27, 28, 29 (FIG. FIGS. 9, 10, 11 ).
  • Fig. 13 shows a lid 32, comparable to the lid 5c in Fig. 1 ,
  • the lid 32 has a through hole 33 into which a pipe end 34 of a pipe coil, not shown, is inserted.
  • annular groove 35 (undercut) is incorporated, in the region of the inserted pipe end 34.
  • the pipe end 34 is gas-tightly connected by rolling with the lid 32. This is an unrepresented Rolling or rolling tool inserted into the pipe end 34 and pushes the pipe material by means of circular movements radially outwards, which is indicated by a double arrow P. In this case, the pipe material also flows into the undercut opening 35, which leads to improved seating and tightness.
  • Fig. 14 shows a further embodiment, wherein two undercut openings in the form of annular grooves 36, 37 are provided.
  • the pipe material of the pipe end 34 is thus displaced in both undercut openings 36, 37, so that there is an improvement of the positive connection and also the tightness.
  • Fig. 15 shows a further embodiment of the rolling of the pipe end 34.
  • the wall of the through hole 33 is provided here with a thread 38.
  • the pipe material is displaced into the thread grooves, whereby a thread-like positive connection is achieved.
  • the advantage here is that the thread 38 can relatively easily bring into the through hole 33.
  • Fig. 16 shows a further embodiment of the rolling of the pipe end 34, wherein the through hole 33 has a shoulder or a narrowing 33a, so that the pipe end is additionally fixed in one direction.
  • a drainage possibility for the refrigerant vapor should exist under the container bottom 2b a drainage possibility for the refrigerant vapor.
  • a gap which can be formed by suitable spacers.
  • the FIGS. 17, 18 and 19 show possibilities for the formation of such spacers.
  • Fig. 17 shows an outline of an inner container 39, the container 2 in Fig. 1 respectively.
  • the inner container 39 has a Floor 40 from which nubs 40a, 40b, 40c outwardly pronounced, which act as spacers.
  • Fig. 18 shows a further embodiment in which a housing bottom 41 is indicated, which the bottom 5b in Fig. 1 equivalent. From the bottom 41 nubs 41 a, 41 b, 41 c are pronounced upward, which serve as a spacer to the overlying, not shown container bottom.
  • Fig. 19 shows a further embodiment of the invention, in which a bottom 42 of an inner container is indicated, which has a round receiving opening 43 for a spring element 44 in its center.
  • the spring element 44 which may be formed as a compression spring acts here as a spacer to the bottom of the outer cylinder, not shown.
  • the assembly and expansion method according to the invention for fixing and positioning the coiled tubing 4 will be explained below, reference being made to FIGS FIGS. 1 and 2 is taken.
  • the housing shell 5a and the housing bottom 5b are connected to each other.
  • the tube cross-section of the coiled tubing 4 is leveled, as explained above.
  • the starting material for the production of the coiled tubing 4 is a tube with a circular cross-section, preferably of an aluminum material.
  • the coiled tubing 4 is produced by winding, wherein the leveling takes place to the required leveling just before winding.
  • the pipe ends 4a, 4b retain their circular cross-section and are bent in the axial direction.
  • the leveled coiled tubing 4 is then inserted into the housing shell 5 a, wherein the tube end 4 a is inserted into the through hole 10. Then the collection container 2, (completed as in Fig. 2 shown) inserted into the tube coil 4, wherein sufficient radial clearance is present. Alternatively, the collecting container 2 can also be inserted into the housing jacket 5 a before the pipe helix 4 is inserted. Subsequently, the cover 5c is placed on the housing shell 5a and fastened, for example by welding. When placing the lid 5 c, the upper tube end 4 b is inserted into the through hole 11. The pipe ends 4a, 4b are then rolled into the bottom 5b and the lid 5c, so that a gas-tight and firm connection is created.
  • the coiled tubing 4 is fixed in the axial direction (and also in the circumferential direction).
  • the pressurization of the tube coil 4 is carried out with a pressure medium, which can be supplied via the through-holes 10 and / or 11. Due to the expansion process, a reduction in the inner diameter and an increase in the outer diameter of the coiled tubing 4 with the result that this applies to form a frictional connection to the container shell 2a and the housing shell 5a.
  • the expansion takes place according to the above-mentioned characteristics, ie, the expansion pressure, which prevails in the coiled tubing as internal pressure, causes a plastic, ie permanent deformation, which has a permanent interference fit result.
  • the tube coil 4 thus sits firmly in the assembly 1.
  • the fluid channel 7 is thus formed as a continuous helical flow channel, so that a defined helical flow is ensured.
  • a bypass flow around the pipe turns around does not take place because of the fluid-tight contact of the coiled tubing 4. This results in a high and defined efficiency for the inner heat exchanger 3, which is formed by the metallic tube coil 4, the housing shell 5 a and the insulated container shell 2 a.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20090007585 2008-06-19 2009-06-09 Unité de construction intégrée comprenant un collecteur et un échangeur thermique interne et procédé de fabrication de l'unité de construction Withdrawn EP2136160A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008028853A DE102008028853A1 (de) 2008-06-19 2008-06-19 Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit

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EP2136160A2 true EP2136160A2 (fr) 2009-12-23

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WO2016016143A1 (fr) * 2014-07-29 2016-02-04 Mahle International Gmbh Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur
WO2018088166A1 (fr) * 2016-11-08 2018-05-17 サンデンホールディングス株式会社 Accumulateur à échangeur de chaleur interne intégré, et cycle de réfrigération l'utilisant

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DE102014220403A1 (de) * 2014-10-08 2016-04-14 Mahle International Gmbh Verfahren zur Montage einer Wärmetauschereinrichtung und Wärmetauschereinrichtung
DE102014220401A1 (de) * 2014-10-08 2016-04-14 Mahle International Gmbh Kältemittelbehälter für eine Kälteanlage
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DE102015217634A1 (de) 2015-09-15 2017-05-11 Mahle International Gmbh Vorrichtung einer Klimaanlage mit einem inneren Wärmetauscher und einem integrierten Sammler
DE102016210015A1 (de) * 2016-06-07 2017-12-07 Mahle International Gmbh Kältemittelsammelbehälter zum Sammeln von Kältemittel und Wärmetauschereinrichtung mit einem solchen Kältemittelsammelbehälter
DE102017211857A1 (de) 2017-07-11 2019-01-17 Mahle International Gmbh Wärmetauschereinrichtung für eine Kälteanlage
DE102017212947A1 (de) 2017-07-27 2019-01-31 Mahle International Gmbh Innerer Wärmeübertrager
DE102017218973A1 (de) 2017-10-24 2019-04-25 Hanon Systems Gegenstrom-Wärmeübertrager

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DE10261886A1 (de) 2001-12-28 2003-07-17 Visteon Global Tech Inc Gegenstromwärmetauscher mit optimalem sekundärem Querstrom
DE102006017432A1 (de) 2006-04-06 2007-10-11 Visteon Global Technologies Inc., Van Buren Innerer Wärmeübertrager mit kalibriertem wendelförmigen Rippenrohr
DE102006031197A1 (de) 2006-07-03 2008-01-10 Visteon Global Technologies Inc., Van Buren Innerer Wärmeübertrager mit Akkumulator

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DE102010043398A1 (de) 2010-11-04 2012-05-10 Behr Gmbh & Co. Kg Kraftfahrzeugklimaanlage
DE102014207660A1 (de) * 2014-04-23 2015-10-29 Mahle International Gmbh Innerer Wärmeübertrager
WO2016016143A1 (fr) * 2014-07-29 2016-02-04 Mahle International Gmbh Échangeur de chaleur et procédé de fabrication de l'échangeur de chaleur
DE102014110718A1 (de) 2014-07-29 2016-02-04 Mahle International Gmbh Wärmeübertrager und Verfahren zur Herstellung des Wärmeübertragers
WO2018088166A1 (fr) * 2016-11-08 2018-05-17 サンデンホールディングス株式会社 Accumulateur à échangeur de chaleur interne intégré, et cycle de réfrigération l'utilisant

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