EP2425193A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur

Info

Publication number
EP2425193A2
EP2425193A2 EP10726891A EP10726891A EP2425193A2 EP 2425193 A2 EP2425193 A2 EP 2425193A2 EP 10726891 A EP10726891 A EP 10726891A EP 10726891 A EP10726891 A EP 10726891A EP 2425193 A2 EP2425193 A2 EP 2425193A2
Authority
EP
European Patent Office
Prior art keywords
conduit
refrigerant
heat exchanger
fluid flow
refrigerant conduit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP10726891A
Other languages
German (de)
English (en)
Other versions
EP2425193B1 (fr
Inventor
Andreas Richard Hilgert
Peter Tobias Klug
Thomas Zenon Zakrzewski
Leonid Walter
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.)
Eaton Industrial IP GmbH and Co KG
Original Assignee
Eaton Fluid Power 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=40902265&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2425193(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Eaton Fluid Power GmbH filed Critical Eaton Fluid Power GmbH
Priority to PL10726891T priority Critical patent/PL2425193T3/pl
Priority to EP10726891.4A priority patent/EP2425193B1/fr
Priority to SI201031564T priority patent/SI2425193T1/en
Publication of EP2425193A2 publication Critical patent/EP2425193A2/fr
Application granted granted Critical
Publication of EP2425193B1 publication Critical patent/EP2425193B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/06—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of metal tubes
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • the invention relates generally to the technical field of heat exchangers and particularly, but not exclusively, to internal heat exchangers and more particularly those used for use air- conditioning systems for automotive applications.
  • Air-conditioning systems of motor vehicles are frequently equipped with a so-called internal heat exchanger.
  • Such heat exchangers may be used to increase the operating efficiency of the system by pre-heating the refrigerant supplied to the suction side of a compressor of the air-conditioning system and at the same time cooling the refrigerant (liquid side) being conveyed to an expansion device.
  • An inner heat exchanger is disclosed in DElO 2006 017 816 B4. This document discloses a single piece extruded aluminium heat exchanger element. In this one extruded profile channels are formed for conveying both liquid side and suction side refrigerant.
  • extruded heat exchanger elements of this type offer high levels of heat exchange between the suction and the liquid sides, they suffer from certain drawbacks: they require machining and/or cleaning before they can be used; welding or brazing must be used in order to connect the suction line to the profile; and, the geometry of the heat exchanger is fixed by the extrusion tool, meaning that new tools must be developed for a new applications requiring different extrusion profiles.
  • the heat exchanger In order to achieve a desired heat transfer between the suction side and the liquid side the heat exchanger must have a given heat exchange area. Sometimes, space is at a premium, for example in automotive applications. In such cases it is desirable to be able to use heat exchangers of reduced outer dimensions. This often means that it is required to form or bend the heat exchanger as a U-shaped pipe or into other shapes so that it may be installed in a given space. This in turn requires that the heat exchanger pipe be designed in a sufficiently bendable manner so that it may be deformed without collapsing its fluid conveyance channels. Moreover, it may also mean that the outer diameter of the heat exchanger is limited or constrained.
  • Fig. 1 is a schematic diagram of an air conditioning system for an automotive application comprising an internal heat exchanger
  • Fig. 2 shows a schematic illustration of the internal heat exchanger shown in Fig. 1 in a U- shaped configuration
  • Fig. 3a shows a perspective view of an internal heat exchanger according to a first embodiment of the invention in its assembled state but prior to being bent into a U-shaped configuration
  • Fig. 3b shows a photograph of the exterior of an internal heat exchanger according to the first embodiment
  • Fig. 3c shows a photograph of the exterior of a section of the deformed portion of the inner tube of the internal heat exchanger according to the first embodiment
  • Fig. 3d shows a schematic illustration of the exterior of a section of the deformed portion of the inner tube of the internal heat exchanger according to the first embodiment, more clearly showing its helical structure
  • Fig. 4 is an image schematically illustrating part of the inner tube of the internal heat exchanger according to a first embodiment, which illustrates one exemplary method of creating a helical structure in a portion of the inner tube;
  • Fig. 5a to Fig. 5c show cross sectional views of the internal heat exchanger according to the first embodiment, illustrating exemplary alternative profiles for the internal heat exchanger inner tube;
  • Fig. 6 is a schematic illustration of the flow of refrigerant in the internal heat exchanger of the first embodiment
  • Fig. 7 shows part of an image of Fig. 4, showing how parameters of the inner tube may be varied to achieve different performance characteristics of the internal heat exchanger of the first embodiment
  • Fig. 8a shows a perspective view of an internal heat exchanger according to a second embodiment in its assembled state but prior to being bent into its final U-shaped configuration
  • Fig. 8b shows a cross sectional view of the internal heat exchanger according to the second embodiment
  • Fig. 9 shows an alternative design of the outer tube of the internal heat exchanger according to the second embodiment, with spiral routed refrigerant fluid flow channels.
  • the air conditioning system 1 includes a compressor 2, which may be driven, for example, by the engine of the vehicle or by a separate electric motor or the like.
  • the compressor 2 has an inlet 4, connected to a low pressure line 21, via which where the compressor 2 takes in refrigerant, or coolant, at low pressure.
  • the compressor 2 also has an outlet 3, via which pressurized refrigerant is output, into a high pressure line 5.
  • the high pressure line 5 leads to a cooling device 6 where the compressed and thus heated refrigerant is cooled and condensed. Therefore, the cooling device 6 is also referred to as a condenser.
  • the refrigerant used is R- 134a that works at low pressure.
  • the refrigerant is discharged to another high pressure line 8 that leads to a high-pressure inlet 9 of an internal heat exchanger 11.
  • the internal heat exchanger 11 has a high-pressure outlet 12 that is in turn connected to an expansion valve 15 via a high pressure line 14.
  • the expansion valve 15 relaxes the refrigerant that is introduced into an evaporator 16.
  • the refrigerant evaporates in the evaporator 16 and, as a result, absorbs thermal energy from the environment; in this example, cooling the air supplied to the interior of the motor vehicle.
  • the resultant refrigerant vapor is then transported from the evaporator 16, via a low-pressure line 17, to the low-pressure inlet 18 of the internal heat exchanger 11.
  • This refrigerant vapor flows through the internal heat exchanger 11 in a counter-current direction to the refrigerant that is being fed through the high-pressure inlet 9. In so doing, the refrigerant vapor cools the pressurized refrigerant, thus itself becoming heated.
  • the refrigerant vapor is discharged, having been heated, at the low-pressure outlet 19 of the internal heat exchanger 11. It is then conducted, via a low-pressure line 21, to the inlet 4 of the compressor 2.
  • the internal heat exchanger 11 allows the temperature of the refrigerant flowing to the compressor 2 to be increased, which in turn increases the temperature of the refrigerant at the outlet 3 of the compressor. Therefore, the cooling device 6 releases a greater amount of thermal energy. At the same time, the internal heat exchanger 11 lowers the temperature of the refrigerant fed to the evaporator 16, thus providing an improved heat transfer between the evaporator 16 and ambient air. In this manner, the internal heat exchanger 11 may be used to increase the efficiency of the air conditioning system.
  • Fig. 2 shows a further schematic illustration of the internal heat exchanger 11.
  • it is shown as a U-shaped bent pipe 22.
  • the bent pipe 22 has two legs 23, 24, that are bent away from each other at their upper ends.
  • the high-pressure inlet 9 and the high-pressure outlet 12 are in fluid connection with the remainder of the system 1 at position 26a.
  • the low-pressure inlet 18 and the low-pressure outlet 19 of the internal heat exchanger 11 are in fluid connection with the remainder of the system 1 at position 26b.
  • positions 26a and 26b are located at or relatively close to the terminations of at the upper ends of the bent pipe 22.
  • FIG. 3a shows a perspective view of the internal heat exchanger 11 of a first embodiment in its assembled state but prior to being bent into its final U-shaped configuration.
  • the internal heat exchanger 11 includes an outer tube 30, and inner tube 32, of which end portions 32a and 32b are visible from this figure Both the outer tube 30 and inner tube 32 being designed as refrigerant conduits.
  • the inner tube 32 is located inside and runs the entire length of the outer tube 30.
  • the internal and external diameters of the outer tube 30 are 18mm and 20mm, respectively.
  • the internal and external diameters of the parts of the inner tube 32 that extend beyond the outer tube 30 and can be seen in the figure are 12mm and 15mm, respectively. It will be understood that the dimensions of the outer tube 30 and inner tube 32 are selected for a given application and will therefore change in dependence upon application.
  • the inner diameter of the outer tube 30 may from range 9-19mm for automotive or car applications, 20-39mm for bus applications and, 23-50mm for train applications.
  • the outer tube is 24mm outer diameter with a 20mm inner diameter.
  • the starting material, or base tube, for the inner tube is 18mm outer diameter with an inner diameter of 15mm.
  • the high-pressure inlet 9 and the high-pressure outlet 12 of the internal heat exchanger 11 are connected to a suitable orifice in the outer tube 30 using a conventional process such as welding or brazing.
  • the weld points are referenced 34 in the figure.
  • a fluid connection is formed between the high-pressure inlet 9 and the high-pressure outlet 12 via the outer tube 30.
  • the connection orifices may be machined, or otherwise manufactured using any convenient process.
  • the outer tube 30 may be used as a connection sleeve which allows the system costs to be reduced.
  • the extreme end points 36 of the outer tube 30 are joined to inner tube 32 to ensure that the joint is effectively sealed against leakage of the refrigerant.
  • a conventional process may be used; for example o-rings, crimping and or welding or brazing.
  • Fig. 3b shows a photograph of an example of an internal heat exchanger 11 similar to that shown in Fig. 3a
  • the inner tube 32 has end portions 32a and 32b that are circular. These respectively form the low-pressure inlet 18 and the low-pressure outlet 19 of the internal heat exchanger 11.
  • the end portions 32a and 32b are unmodified base tube material. Therefore end portions 32a and 32b may be configured to be the required lengths to provide the function of low pressure tubes 21 and 17, shown in Fig. 1. This in turn means that no suction side connection tubes are needed; thus obviating the need for costly connection processes, such as welding and eliminating the risk of refrigerant leakage at such connection points.
  • a central portion 32c that has been deformed into a helical shape along its longitudinal axis.
  • a photograph of the exterior of a section of the deformed portion 32c of the inner tube of the internal heat exchanger 11 according to the first embodiment is shown in Fig. 3c.
  • the central portion 32c may be deformed using any convenient deforming procedure. In the present example it is deformed through a repeated clamping process. However, other deforming processes or apparatus, such as a press or hammer, may be used. In this example, the clamping process is implemented using shaped opposing clamping surfaces to achieve the desired exterior profile of the portion 38b.
  • the marks 38a left in the outer surface of the deformed portion 32c by the action of the clamping process may be seen in Fig. 3c. Furthermore, it can be seen from Fig. 3c that the deformed portion 32c has a helical profile. This helical profile can be more clearly seen from the schematic illustration of a section of portion 32c illustrated in Fig. 3d.
  • FIG. 4 shows an image schematically illustrating a part of the inner tube 32, including part of central portion 32c, arranged about its longitudinal axis 42.
  • the left hand end 32a of the inner tube 32 is not deformed and is circular is cross section.
  • portion 44a Adjacent the left hand end 32a end of the inner tube 32 is portion 44a that has been deformed to an approximate elliptical shape of predetermined dimensions. These dimensions may be controlled using the parameters of the deforming process; for example the linear extent of the clamping operation and the shape, dimensions and material properties of the clamping surfaces.
  • the major axis 46a of the elliptical portion 44a is shown orientated vertically.
  • the inner tube 32 When the clamp is removed from portion 44a of the inner tube 32, the inner tube 32 is advanced a fixed predetermined distance along its longitudinal axis 42 to bring the portion 44b of the tube adjacent the clamping surfaces and the inner tube 32 is rotated by a fixed angle in a given direction about its longitudinal axis; in this example 45 degrees. The clamping operation is then repeated. This process is then repeated along the desired length of central portion 32c of the inner tube 32, as is illustrated by deformed portions 44b - 44f. In this manner an approximate helical structure of approximately fixed helical pitch and approximately constant elliptical cross section may be formed.
  • the central portion 32c of the inner tube 32 is free or substantially free of projections and is relatively smooth in both its circumferential direction and its longitudinal direction.
  • the inventors have found that this process of manufacture may be largely automated by using a bending machine set to zero bend radius.
  • the creation of the helical structure of the central portion 32c of the inner tube 32 may be a relatively rapid and inexpensive process.
  • inner tube 32 is assembled with the outer tube 30, by inserting the inner tube 32 inside the outer tube 30.
  • the fit between the inner tube 32 and the outer tube 30 may be any convenient fit, such as a loose fit or a slight interference fit.
  • inner tube 32 and the outer tube 30 may be assembled by hand or be automated.
  • the welding or braising, including crimping if this is required, of the extreme end points 36 of the outer tube 30 to inner tube 32 may then be carried out. This may be done in the region where the non- deformed end sections 32a and 32b of the inner tube 32 transition into the adjacent deformed portion 32c.
  • Fig. 5c shows a cross sectional view, in the direction of arrows A-A shown in Fig. 3a, of the internal heat exchanger 11, and illustrates the inner tube 32 and the outer tube 30 once assembled.
  • the inner tube 32 forms an approximate ellipse, the major axis of which is approximately equal to the internal diameter of the outer tube 30; i.e. 18mm.
  • the cross sectional profile of the inner tube 32 could be varied either to meet heat exchange requirements or in order to meet manufacturing requirements.
  • an ellipse as is illustrated in Fig. 5a could be used.
  • Other examples could include a triangular or quadrilateral shape, such as an approximate square as is illustrated in Fig. 5b could also be used.
  • other cross sectional profiles may be contemplated, which have increased numbers of sides.
  • the inner tube 32 contacts the inner surface of outer tube 30 at points 56a and 56b, thus forming two substantially line contacts between the outer surface of the inner tube 32 and the inner surface of outer tube 30 which run the entire length of the helical structure of the central portion 32c of the inner tube 32.
  • two refrigerant fluid flow channels 52a and 52b are formed between the outer surface of the inner tube 32 and the inner surface of outer tube 30.
  • the fluid flow channels 52a and 52b carry liquid side refrigerant.
  • a certain degree of fluid connection between the fluid flow channels 52a and 52b may be permitted. The extent of this permitted fluid connection may be dependent upon the application.
  • a third refrigerant fluid flow channel 50 lies on the inside of the inner tube 32.
  • the third refrigerant fluid flow channel 50 carries refrigerant supplied to the suction side of the compressor.
  • the three refrigerant fluid flow channels run substantially the entire length of the helical structure of the central portion 32c of the inner tube 32.
  • the third refrigerant fluid flow channel 50 has a cross sectional area which is substantially equal to, or is only marginally reduced relative to the cross sectional area of the base circular tube from which it is formed, and from which the remainder of the suction side, low pressure lines of the air conditioning system 1, are made. This means that the pressure drop caused per unit length of the fluid flow channel 50 is substantially the same as, or not significantly increased relative to, that of the base circular tube from which it is formed, such as low pressure line 21.
  • the inventors have surprisingly discovered that the creation of the helical structure of the central portion 32c of the inner tube 32 does not cause a significant or measurable drop in pressure in the fluid flow channel 50 relative to a correspondingly profiled tube with no helical structure.
  • the surprising lack of pressure drop in the suction side of the internal heat exchanger 11 of the present embodiment may strongly contribute to the efficiency of the air conditioning system 1.
  • the suction side pressure drop per unit length of the internal heat exchanger 11 may be up to 30% higher than that of the normal suction side line. In other embodiments this figure may be 10% or 20%.
  • the area across which heat may be exchanged between fluid flow channel 50 and each of fluid flow channels 52a and 52b is large, being approximately equivalent to half of the external area of the inner tube 32.
  • the efficiency of heat exchange between the flow channel 50 and each of fluid flow channels 52a and 52b is increased.
  • the fluid flow channels 52a and 52b are approximately crescent shaped, having a relatively small height or thickness in the radial direction and a relatively high length of contact with the external circumference of the inner tube 32. This length of contact is illustrated, in the case of fluid flow channels 52a by line 58 in the figure.
  • this line of contact provides a convex heat transfer surface (the external surface of the inner tube 32) against which the fluid in fluid flow channels 52a and 52b flows; and thereby a large and efficient heat exchange surface over the length of the fluid flow channels 52a and 52b.
  • Fig. 6 illustrates the flow of refrigerant in the internal heat exchanger 11 according to the present embodiment.
  • the refrigerant flowing in refrigerant fluid flow channel 50 is referenced 60 and the refrigerant flowing in refrigerant fluid flow channels 52a and 52b is referenced 62a and 62b, respectively.
  • the refrigerant flowing in refrigerant fluid flow channels 52a and 52b follows a helical path along the internal heat exchanger 11 and completes three complete cycles around the fluid in fluid flow channel 50.
  • Fig. 7 illustrates part of the image of Fig. 4 illustrating several deformed portions 44 of the inner tube 32; where:
  • the efficiency of the internal heat exchanger 11 may be decreased by increasing "c" and "e”; i.e. by decreasing the number of deformations per unit length of the inner tube 32 and increasing the slope of the helix; this may be in the range of 45 to 90 degrees for example.
  • the internal heat exchanger 11 should have sufficient bending stability.
  • the bending stability of the internal heat exchanger 11 may be increased by decreasing the value of parameter "f '.
  • FIG. 8 a second embodiment of the internal heat exchanger 11 for use in the air conditioning system 1 will now be described. Structures and functions of the second embodiment that are similar to corresponding structures and functions of the first embodiment will not be described further. The same reference numerals will be used to refer to structures and functions of the second embodiment as were used to refer to corresponding structures and functions of the first embodiment.
  • Fig. 8a shows a perspective view of the internal heat exchanger 11 of the second embodiment in its assembled state but prior to being bent into its final U-shaped configuration.
  • the inner tube 32 is a plain tube of unmodified base tube material. This may be the same base tube material as was described with respect to the first embodiment.
  • the outer tube 30 however is formed or deformed to provide a predetermined cross sectional profile having longitudinal ridges 82, as is described in more detail below.
  • the outer tube 30 may be formed in any convenient manner; for example extrusion or through a rolling or other deformation process. In the case of the rolling process, circular cross section tube material may be used as the starting material.
  • Angularly spaced, longitudinal grooves may be created in the exterior surface of the tube, leaving ridges 82 between the grooves.
  • Other aspects of the internal heat exchanger 11, including the high-pressure inlet 9 and the high-pressure outlet 12 and their attachment to the outer tube may be the same as described with referenced to the first embodiment.
  • Fig. 8b shows a cross sectional view, in the direction of arrows A-A in Fig. 8a, of the internal heat exchanger 11.
  • the inner tube 32 has a circular cross section.
  • the internal volume of the inner tube 32 forms a fluid flow channel corresponding to fluid flow channel 50 of the first embodiment.
  • the outer tube 30 has a substantially circular cross sectional profile in which 8 ridges 82a - 82h are arranged.
  • the ridges 82a - 82h run parallel to the longitudinal axis of outer tube 30 and are arranged at regular angular spacing about the its longitudinal axis.
  • the outside diameter of the inner tube 32 is approximately equal to the minimum internal diameter of the formed outer tube 30; i.e. 18mm.
  • the inner tube 32 contacts the inner surface of outer tube 30 at points 80a to 8Oh. Between the points 80a to 8Oh, the ridges 82a - 82h in the outer tube 30 form spaces between the inner tube 32 and the outer tube 30. The spaces run along the length of the internal heat exchanger 11 and form refrigerant fluid flow channels 84a - 84h corresponding to refrigerant fluid flow channels 52a and 52b described with reference to the first embodiment.
  • the fluid flow channels 84a - 84h of the second embodiment are approximately crescent shaped, having a relatively small height in the radial direction and a relatively high length of contact with the external circumference of the inner tube 32.
  • This length is shown in an illustrative manner by line 86a in the figure, which lies along the outer circumference (on the outer surface) of inner tube 32 between points 80a and 80b. It will be appreciated that this line of contact provides a convex heat transfer surface (the external surface of the inner tube 32) against which the fluid in fluid flow channels 84a — 84h flows; and thereby a large and efficient heat exchange surface over the length of the fluid flow channels 84a - 84h.
  • the number, size and geometry of the refrigerant fluid flow channels 84a - 84h determines the heat transfer characteristics of the internal heat exchanger 11. These factors also influence the bending properties of the internal heat exchanger 11. In general:
  • the number of the refrigerant fluid flow channels 84a - 84h as well as the size of the channels is limited by the geometry, the physical properties of the starting material and the production process. In certain situations, it may be difficult to reach the desired heat transfer capacity of the internal heat exchanger 11 for a given application. Limitations on the number of and cross sectional area of the fluid flow channels 84a - 84h may be experienced due to manufacturing constraints. Also, the total length of the internal heat exchanger 11 may be fixed. In this situation, the contact length, and therefore area, can be enlarged by routing the fluid flow channels 84a - 84h around the central of the internal heat exchanger 11. This may be achieved creating an outer tube 30 with a suitable profile.
  • FIG. 9 An internal heat exchanger 11 according to the second embodiment with spiral routed refrigerant fluid flow channels 84a - 84h, created by a formed or deformed outer tube 30 is illustrated in Fig. 9.
  • the heat transfer capacity is a function of heat transfer coefficient and heat transfer surface (contact area)
  • the contact area or contact time can be adjusted over the length of the fluid flow channels 84a - 84h.
  • the contours of the inner tube 32 can be placed anywhere along, or even along only a part of, the length of the inner tube 32.
  • heat transfer may be adjusted by changing the geometry of the interface between the inner tube 32 and the outer tube 30, and this may be done without significantly changing the forming tool, such as a clamp, or process used. This provides considerable flexibility in terms or manufacturing. Heat exchanger applications with different performance criteria may be achieved without having to significantly modify the manufacturing process or tooling.
  • the inner tube may be made from standard tubing material, it is low cost. No expensive extrusions are required and no suction side connection tubes are needed, which may help to ensure that manufacturing is simplified and reliability of the system is increased.
  • Bending flexibility may be adjusted by altering the geometry of the deformed tube.
  • the outer tube 30 may be used as a connection sleeve which further allows the system costs to be reduced. Despite the fact that that low-pressure channel may be particularly large, reducing the tendency for suction side pressure drop, a relatively small outside diameter may be achieved.

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

Abstract

L'invention concerne un échangeur de chaleur doté d'un conduit externe et d'un conduit interne, disposé à l'intérieur et le long de l'axe longitudinal du conduit externe, le conduit interne et le conduit externe étant disposés de façon à former un canal d'écoulement de fluide entre la surface interne du conduit externe et la surface externe du conduit interne, le canal d'écoulement de fluide ayant une forme en coupe transversale, dans un plan sensiblement perpendiculaire à l'axe longitudinal du conduit externe, qui est allongé et sensiblement supérieur dans la direction circonférentielle du conduit externe que dans la direction radiale dudit conduit externe.
EP10726891.4A 2009-04-30 2010-04-30 Echangeur de chaleur Active EP2425193B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL10726891T PL2425193T3 (pl) 2009-04-30 2010-04-30 Wymiennik ciepła
EP10726891.4A EP2425193B1 (fr) 2009-04-30 2010-04-30 Echangeur de chaleur
SI201031564T SI2425193T1 (en) 2009-04-30 2010-04-30 Heat exchanger

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP09159260 2009-04-30
GBGB0909221.4A GB0909221D0 (en) 2009-04-30 2009-05-29 Heat exchanger
PCT/EP2010/002656 WO2010124871A2 (fr) 2009-04-30 2010-04-30 Echangeur de chaleur
EP10726891.4A EP2425193B1 (fr) 2009-04-30 2010-04-30 Echangeur de chaleur

Publications (2)

Publication Number Publication Date
EP2425193A2 true EP2425193A2 (fr) 2012-03-07
EP2425193B1 EP2425193B1 (fr) 2017-07-19

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10726891.4A Active EP2425193B1 (fr) 2009-04-30 2010-04-30 Echangeur de chaleur

Country Status (9)

Country Link
US (1) US20120097380A1 (fr)
EP (1) EP2425193B1 (fr)
CN (1) CN102460054B (fr)
ES (1) ES2643324T3 (fr)
GB (1) GB0909221D0 (fr)
HU (1) HUE034718T2 (fr)
PL (1) PL2425193T3 (fr)
SI (1) SI2425193T1 (fr)
WO (1) WO2010124871A2 (fr)

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DE102010034112A1 (de) * 2010-08-12 2012-02-16 Gm Global Technology Operations Llc (N.D.Ges.D. Staates Delaware) Interner Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
KR101600296B1 (ko) * 2010-08-18 2016-03-07 한온시스템 주식회사 이중관식 열교환기 및 그 제조방법
GB2523107A (en) * 2014-02-12 2015-08-19 Eaton Ind Ip Gmbh & Co Kg Heat exchanger
WO2016012664A1 (fr) * 2014-07-25 2016-01-28 Hutchinson Echangeur thermique tel qu'un echangeur interne pour circuit de climatisation de vehicule automobile et circuit l'incorporant
DE102014220403A1 (de) * 2014-10-08 2016-04-14 Mahle International Gmbh Verfahren zur Montage einer Wärmetauschereinrichtung und Wärmetauschereinrichtung
EP3306248B1 (fr) * 2016-10-05 2019-03-06 Hs R & A Co., Ltd. Échangeur de chaleur de type à double tuyau et son procédé de fabrication
CN107449147B (zh) * 2017-09-25 2019-11-15 江苏来德福汽车部件有限公司 一种油炸机热交换器
CN112437860B (zh) * 2019-10-15 2022-01-11 安美(北京)汽车工程技术有限公司 冷媒液化器及制冷循环装置

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JP2002318015A (ja) * 2001-04-17 2002-10-31 Orion Mach Co Ltd 冷凍装置
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DE102005063620B3 (de) * 2004-11-09 2017-03-09 Denso Corporation Doppelwandiges Rohr
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See references of WO2010124871A2 *

Also Published As

Publication number Publication date
GB0909221D0 (en) 2009-07-15
CN102460054B (zh) 2016-04-20
HUE034718T2 (hu) 2018-02-28
US20120097380A1 (en) 2012-04-26
EP2425193B1 (fr) 2017-07-19
SI2425193T1 (en) 2018-02-28
WO2010124871A3 (fr) 2011-02-17
PL2425193T3 (pl) 2018-01-31
WO2010124871A2 (fr) 2010-11-04
CN102460054A (zh) 2012-05-16
ES2643324T3 (es) 2017-11-22

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