WO1988006678A1 - A heat exchanger arrangement for cooling a machine - Google Patents

A heat exchanger arrangement for cooling a machine Download PDF

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Publication number
WO1988006678A1
WO1988006678A1 PCT/SE1988/000071 SE8800071W WO8806678A1 WO 1988006678 A1 WO1988006678 A1 WO 1988006678A1 SE 8800071 W SE8800071 W SE 8800071W WO 8806678 A1 WO8806678 A1 WO 8806678A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
housing
machine
liquid
heat exchanger
Prior art date
Application number
PCT/SE1988/000071
Other languages
French (fr)
Inventor
Stig Stenlund
Original Assignee
Metsafe Aktiebolag
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 Metsafe Aktiebolag filed Critical Metsafe Aktiebolag
Priority to HU881751A priority Critical patent/HU206533B/en
Priority to AT88901966T priority patent/ATE80698T1/en
Priority to BR888807379A priority patent/BR8807379A/en
Priority to DE8888901966T priority patent/DE3874730T2/en
Publication of WO1988006678A1 publication Critical patent/WO1988006678A1/en
Priority to US07/501,320 priority patent/US5072784A/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0412—Cooling or heating; Control of temperature
    • F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N39/00—Arrangements for conditioning of lubricants in the lubricating system
    • F16N39/02—Arrangements for conditioning of lubricants in the lubricating system by cooling
    • 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
    • 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/0004—Oilsumps
    • F01M2011/0058—Fastening to the transmission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0412—Cooling or heating; Control of temperature
    • F16H57/0415—Air cooling or ventilation; Heat exchangers; Thermal insulations
    • F16H57/0417—Heat exchangers adapted or integrated in the gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/916—Oil cooler
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2186—Gear casings
    • Y10T74/2189—Cooling

Definitions

  • a heat exchanger arrangement for cooling a machine is provided.
  • the present invention relates to a heat-exchange arrange ⁇ ment for cooling a machine.
  • the term machine is used in the present context as a collective designation for ma ⁇ chines or machine assemblies of the kind which include a housing in which movable components which are driven when the machine is working are housed and which encloses a liquid medium, normally a lubricant or hydraulic fluid.
  • machines of this kind include internal com ⁇ bustion engines, gear assemblies, automatic gear-boxes, mechanical and hydraulic clutches, other kinds of trans ⁇ mission elements, hydraulic pumps, hydraulic motors, compressors, etc.
  • machines lack the provision of a pump for driving the enclosed liquid medium to be cooled, or in those cases where a pump is fitted, the pump has other primary duties to fulfill and cannot therefore sat ⁇ isfy the requirements of the heat exchanger with regard to pressure and volumetric flew of the liquid concerned.
  • One example in this respect includes the automatic gear boxes of automotive vehicles, in which the primary purpose of the pump provided is to supply the hydraulic transmission system with the requisite pressure and the requisite flow of fluid.
  • the development of machines of the above-men ⁇ tioned kind is also directed towards machines ofprogressively- si ely higher power and of more compact construction, and consequently of smaller volume, or bulk, and smaller sur ⁇ face areas. As a result the machines will have low in ⁇ herent cooling abilities.
  • Examples of this are motor ve ⁇ hicle transmission components, where the need, e.g. of cooling simple mechanical gears and gear boxes has become progressively greater.
  • To supply such machines which either need no pump for their main function or which in ⁇ corporate a pump which produces only relatively limited pressure and only a relatively small volumetric flow, with a separate pump in order to satisfy the requirement of a conventional turbulent-flow heat exchanger to effect the desired cooling of the machine would cause consider ⁇ able technical complications and add greatly to the over ⁇ all costs. Because of this, machines of this kind have hitherto not normally been provided with separate cooling arrangements, and consequently it has been necessary to accept very high machine temperatures and the problems caused thereby.
  • the object of the present invention is therefore to pro ⁇ vide a heat exchanger arrangement for cooling machines of the aforementioned kind which is of simple and inexpen ⁇ sive construction and the function of which does not re ⁇ quire the provision of a separate pump for moving the liquid medium to be cooled through the heat exchanger, but which will nevertheless afford a very high heat ex ⁇ change effect and therewith effective cooling.
  • Figure 1 is a sectional view of a first embodiment of the invention
  • Figure 2 is a sectional view of a second embodiment of the invention.
  • Figure 3 is a sectional view taken on the line III-III in Figure 1;
  • Figure 4 is a sectional view of a further embodiment of the invention.
  • Figures 1 and 3 illustrate very schematically and by way of example one conceivable embodiment of the invention.
  • Figure 1 is a schematic sectional view of a machine of the aforedescribed kind which includes a housing 1 in which movable mechanical elements 2 are housed, these elements being driven when the machine is working, and which in ⁇ cludes a liquid medium 3, such as a lubricant or hydraulic fluid. Since the actual construction of the machine is not relevant to the present invention, there is no need to describe the machine in detail, and hence the machine is only illustrated schematically and in principle.
  • the ma ⁇ chine may, for instance, consist of a gear box or some other form of transmission component of an automotive ve ⁇ hicle, which gear box or transmission component includes rotating gears and shafts and also incorporates lubricat- ing oil.
  • the machine is cooled by means of an inventive heat exchanger arrangement, general ⁇ ly referenced 4, which is fitted in one of the external walls 5 of the machine housing 1.
  • the heat exchanger arrangement 4 includes two chambers 6 and 7 which are mu ⁇ tually separated by a liquid-impervious partition wall 8, which forms a part of the liquid-impervious wall of the machine housing 1.
  • the heat-exchange chamber 7, located inwardly of the partition wall 8, is intended to be through-passed by the liquid 3 enclosed by the housing 1 and for cooling the machine, whereas the chamber 6, lo ⁇ cated outwardly of the partition wall 8 is intended to be through-passed by a coolant, e.g. water, which is deliv ⁇ ered to the chamber 6 through an inlet 9 and leaves through an outlet 10.
  • a coolant e.g. water
  • the chamber 7 has an inlet 13 through which the liquid 3 enters the chamber and from which the liquid is conducted, via distribution or auxiliary channels 14 of relatively large flow area, to a very large number of nar ⁇ row flow channels 12 defined by mutually adjacent fins 11. Subsequent to passing through the narrow flow channels 12, the liquid 3 is conducted through auxiliary channels or collecting channels 15 of relatively large flow areas to an outlet 16, through which the liquid leaves the chamber 7.
  • the liquid flow through the channels 12 is laminar and the channels have a short length, for instance, a length of 5-20 mm. Because of the large number of flow channels present, each of which conducts a very small volumetric flow of liquid, this will afford only a small drop in pressure.
  • the requisite flow of liquid 3 through the chamber 7 of the heat ex ⁇ changer can be achieved in the manner illustrated in Fig ⁇ ure 1 , by arranging and positioning the heat exchanger so that the inlet 13 through which the liquid 3 enters the chamber 7 is located at a higher level than the chamber outlet 16, and so that when the machine is working,the liquid 3 is transported to thehigher level of the inlet 13 under the influence of the movement of the movable mechan ⁇ ical elements 2, e.g. as a result of the rotary movement of a rotating gear or like element.
  • the resultant hydro ⁇ static pressure differential obtained in this way between the inlet 13 and the outlet 16 is fully sufficient to drive the requisite volume of liquid through the chamber 7 of the heat exchanger. Movement of the liquid 3 through the heat exchanger is also assisted by the increase in density experienced by the liquid as it is gradually cooled during its passage through the chamber 7.
  • the outwardly located heat-exchange chamber 6 through which the cooling medium flows may be configured for tur ⁇ bulent flow in a conventional manner, since normally there is access to a pump which is capable of producing the pressure required to drive a sufficient volume of cooling medium in general through a turbulent-flow heat- exchange chamber. Consequently, the partition wall 8 of the heat exchanger 4 may be provided with a plurality of mutually parallel fins which extends from the inlet 9 to the outlet 10 and which define therebetween a plurality of cooling medium flow channels extending from the cooling medium inlet 9 to the cooling-medium outlet 10. This enhances the heat-exchange effect between the cooling me ⁇ dium and the partition wall 8 in a conventional fashion. It will be understood, however, that the outer heat-ex ⁇ change chamber 6 for cooling medium may also be configured for laminar flow of the cooling medium in accordance with the heat-exchange principle taught by the International Patent Application PCT/SE 84/00245.
  • the liquid medium to be cooled and enclosed in the machine housing may also be driven through the inwardly located heat-exchange chamber configured for laminar flow under the influence of a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working.
  • a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working.
  • auxiliary channels 14, 15 in the inner heat-exchange chamber 7 configured for laminar flow of the cooling me ⁇ dium 3 are placed within the chamber 7 in the form of interruptions in the fins 11 which define therebetween the laminar flow channels 12.
  • these auxiliary channels 14, 15, which serve as distribution and collection channels respectively may be placed in the housing wall 5 located inwardly of the chamber 7, in the manner illustrated schematically in Figure 4. This ob- viates the need for corresponding interruptions in the fins 11 defining the laminar flow channels 12, and hence there is obtained a greater fin length and therewith also a greater flow channel length, which results in a greater heat-exchange effect.
  • the fins 11 may be broken with short slot ⁇ like interruptions, referenced 17 in Figure 4, for the purpose described in said international patent application

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Motor Or Generator Cooling System (AREA)
  • General Details Of Gearings (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)

Abstract

A heat exchanger (4) for cooling a machine, such as a mechanical gear or some other transmission component, hydraulic pump, motor or clutch, compressor, internal combustion engine or like machine, which comprises a housing (1) in which movable, mechanical elements (2), which are driven when the machine is working, are housed and which encloses a liquid medium (3), such as a lubricating or hydraulic liquid. The heat exchanger is mounted in the outer wall (5) of the housing and comprises two chambers (6, 7) which are mutually separated by a liquid-impervious partition wall (8) wich comprises part of the housing wall. The inwardly located chamber (7) is through-passed by the liquid medium (3) enclosed in the housing, while the outwardly located chamber (6) is through-passed by a cooling medium. The heat exchanger (4) is so positioned that a pressure difference is created between the inlet (13) and the outlet (16) of the inwardly located chamber (7) under the influence of movement of the movable mechanical elements (2) therewith obviating the need of a separate pump for driving the medium (3) to be cooled through the heat exchanger.

Description

A heat exchanger arrangement for cooling a machine.
The present invention relates to a heat-exchange arrange¬ ment for cooling a machine. The term machine is used in the present context as a collective designation for ma¬ chines or machine assemblies of the kind which include a housing in which movable components which are driven when the machine is working are housed and which encloses a liquid medium, normally a lubricant or hydraulic fluid. Examples of machines of this kind include internal com¬ bustion engines, gear assemblies, automatic gear-boxes, mechanical and hydraulic clutches, other kinds of trans¬ mission elements, hydraulic pumps, hydraulic motors, compressors, etc.
In many of these machines there exists the need to cool the liquid working in the machine. Conventional heat ex¬ changers which might conceivably be considered for use to this end work with turbulent flow. When wishing to use a turbulent-flow heat exchanger which is light in weight and small in volume and yet exhibits a high heat-exchange ef¬ ficiency, the heat exchanger must operate at a relatively high pressure-drop and, in many cases, with a relatively high volumetric through-flow of the enclosed liquid edi- urn to be cooled. Consequently, a pump must be provided to produce the requisite high drop in pressure and a suffi¬ ciently large volumetric flow of medium. Many of the aforementioned machines, however, lack the provision of a pump for driving the enclosed liquid medium to be cooled, or in those cases where a pump is fitted, the pump has other primary duties to fulfill and cannot therefore sat¬ isfy the requirements of the heat exchanger with regard to pressure and volumetric flew of the liquid concerned. One example in this respect includes the automatic gear boxes of automotive vehicles, in which the primary purpose of the pump provided is to supply the hydraulic transmission system with the requisite pressure and the requisite flow of fluid. The development of machines of the above-men¬ tioned kind is also directed towards machines of progres- si ely higher power and of more compact construction, and consequently of smaller volume, or bulk, and smaller sur¬ face areas. As a result the machines will have low in¬ herent cooling abilities. Examples of this are motor ve¬ hicle transmission components, where the need, e.g. of cooling simple mechanical gears and gear boxes has become progressively greater. To supply such machines, which either need no pump for their main function or which in¬ corporate a pump which produces only relatively limited pressure and only a relatively small volumetric flow, with a separate pump in order to satisfy the requirement of a conventional turbulent-flow heat exchanger to effect the desired cooling of the machine would cause consider¬ able technical complications and add greatly to the over¬ all costs. Because of this, machines of this kind have hitherto not normally been provided with separate cooling arrangements, and consequently it has been necessary to accept very high machine temperatures and the problems caused thereby.
The object of the present invention is therefore to pro¬ vide a heat exchanger arrangement for cooling machines of the aforementioned kind which is of simple and inexpen¬ sive construction and the function of which does not re¬ quire the provision of a separate pump for moving the liquid medium to be cooled through the heat exchanger, but which will nevertheless afford a very high heat ex¬ change effect and therewith effective cooling.
The characteristic features of a heat exchanger arrange- ment constructed in accordance with the invention are set forth in the following claims.
The invention will now be described in more detail with reference to the accompanying schematic drawings, which illustrate a number of exemplifying embodiments of the invention and in which
Figure 1 is a sectional view of a first embodiment of the invention;
Figure 2 is a sectional view of a second embodiment of the invention;
Figure 3 is a sectional view taken on the line III-III in Figure 1; and
Figure 4 is a sectional view of a further embodiment of the invention.
Figures 1 and 3 illustrate very schematically and by way of example one conceivable embodiment of the invention. Figure 1 is a schematic sectional view of a machine of the aforedescribed kind which includes a housing 1 in which movable mechanical elements 2 are housed, these elements being driven when the machine is working, and which in¬ cludes a liquid medium 3, such as a lubricant or hydraulic fluid. Since the actual construction of the machine is not relevant to the present invention, there is no need to describe the machine in detail, and hence the machine is only illustrated schematically and in principle. The ma¬ chine may, for instance, consist of a gear box or some other form of transmission component of an automotive ve¬ hicle, which gear box or transmission component includes rotating gears and shafts and also incorporates lubricat- ing oil. In accordance with the invention, the machine is cooled by means of an inventive heat exchanger arrangement, general¬ ly referenced 4, which is fitted in one of the external walls 5 of the machine housing 1. The heat exchanger arrangement 4 includes two chambers 6 and 7 which are mu¬ tually separated by a liquid-impervious partition wall 8, which forms a part of the liquid-impervious wall of the machine housing 1. The heat-exchange chamber 7, located inwardly of the partition wall 8, is intended to be through-passed by the liquid 3 enclosed by the housing 1 and for cooling the machine, whereas the chamber 6, lo¬ cated outwardly of the partition wall 8 is intended to be through-passed by a coolant, e.g. water, which is deliv¬ ered to the chamber 6 through an inlet 9 and leaves through an outlet 10. The transfer of heat between the liquid 3 and the coolant thus takes place through the li¬ quid-impervious partition wall 8. The heat transfer from the liquid 3 when the liquid flows through the chamber 7 in the heat exchanger and past the partition wall 8 takes place in accordance with the heat-exchange principle taught by International Patent Application PCT/SE 84/00245, with laminar flow of the liquid 3 in the heat-exchange chamber 7. To this end, the inner surface of the partition wall facing the chamber 7 is provided with a large number of fins 11 which define therebetween a large number of flow channels 12 which present an elongated rectangular, slot-like cross section and which are connected in paral¬ lel with regard to the flow of liquid therethrough (c.f. Figure 3). The chamber 7 has an inlet 13 through which the liquid 3 enters the chamber and from which the liquid is conducted, via distribution or auxiliary channels 14 of relatively large flow area, to a very large number of nar¬ row flow channels 12 defined by mutually adjacent fins 11. Subsequent to passing through the narrow flow channels 12, the liquid 3 is conducted through auxiliary channels or collecting channels 15 of relatively large flow areas to an outlet 16, through which the liquid leaves the chamber 7. The liquid flow through the channels 12 is laminar and the channels have a short length, for instance, a length of 5-20 mm. Because of the large number of flow channels present, each of which conducts a very small volumetric flow of liquid, this will afford only a small drop in pressure. The relatively large auxiliary chan¬ nels 14, 15 do not give rise to any appreciable drop in pressure, and as a result of the very large number of narrow flow channels 12 provided there is obtained, rela¬ tively speaking, a very large total volumetric flow through the chamber 7 at a very low total pressure drop from the inlet 13 to the outlet 16. As a result of the relatively large total volumetric flow and the extremely good heat-exchange characteristics of a heat exchanger constructed in this manner, there is achieved a fully satisfactory heat-exchange effect without requiring the provision of a separate pump to drive the liquid 3 through the chamber 7 of the heat exchanger. Thus, the requisite flow of liquid 3 through the chamber 7 of the heat ex¬ changer can be achieved in the manner illustrated in Fig¬ ure 1 , by arranging and positioning the heat exchanger so that the inlet 13 through which the liquid 3 enters the chamber 7 is located at a higher level than the chamber outlet 16, and so that when the machine is working,the liquid 3 is transported to thehigher level of the inlet 13 under the influence of the movement of the movable mechan¬ ical elements 2, e.g. as a result of the rotary movement of a rotating gear or like element. The resultant hydro¬ static pressure differential obtained in this way between the inlet 13 and the outlet 16 is fully sufficient to drive the requisite volume of liquid through the chamber 7 of the heat exchanger. Movement of the liquid 3 through the heat exchanger is also assisted by the increase in density experienced by the liquid as it is gradually cooled during its passage through the chamber 7.
The outwardly located heat-exchange chamber 6 through which the cooling medium flows may be configured for tur¬ bulent flow in a conventional manner, since normally there is access to a pump which is capable of producing the pressure required to drive a sufficient volume of cooling medium in general through a turbulent-flow heat- exchange chamber. Consequently, the partition wall 8 of the heat exchanger 4 may be provided with a plurality of mutually parallel fins which extends from the inlet 9 to the outlet 10 and which define therebetween a plurality of cooling medium flow channels extending from the cooling medium inlet 9 to the cooling-medium outlet 10. This enhances the heat-exchange effect between the cooling me¬ dium and the partition wall 8 in a conventional fashion. It will be understood, however, that the outer heat-ex¬ change chamber 6 for cooling medium may also be configured for laminar flow of the cooling medium in accordance with the heat-exchange principle taught by the International Patent Application PCT/SE 84/00245.
The liquid medium to be cooled and enclosed in the machine housing may also be driven through the inwardly located heat-exchange chamber configured for laminar flow under the influence of a hydrodynamic pressure differential created by movement of the movable mechanical machine elements when the machine is working. One such embodiment of the invention is illustrated schematically and by way of example in Figure 2, in which the same references as those used in Figure 1 have been used to identify corre¬ sponding parts.
In the exemplifying embodiments illustrated in Figures 1-3, the auxiliary channels 14, 15 in the inner heat-exchange chamber 7 configured for laminar flow of the cooling me¬ dium 3 are placed within the chamber 7 in the form of interruptions in the fins 11 which define therebetween the laminar flow channels 12. Alternatively, however, these auxiliary channels 14, 15, which serve as distribution and collection channels respectively, may be placed in the housing wall 5 located inwardly of the chamber 7, in the manner illustrated schematically in Figure 4. This ob- viates the need for corresponding interruptions in the fins 11 defining the laminar flow channels 12, and hence there is obtained a greater fin length and therewith also a greater flow channel length, which results in a greater heat-exchange effect.
As described in the aforementioned international patent application, the fins 11 may be broken with short slot¬ like interruptions, referenced 17 in Figure 4, for the purpose described in said international patent application

Claims

Claims
1. An arrangement for cooling a machine which comprises a housing (1) in which movable, mechanical elements (2), which are driven when the machine is working, are housed, and which encloses a liquid medium (3), particularly a lubricant or hydraulic fluid, characterized in that the arrangement includes a heat exchanger (4) which is arranged in a part of one external wall (5) of the housing (1) and which includes two chambers (6, 7) which are mutu¬ ally separated by a liquid-impervious partition wall (8) which constitutes a part of the liquid-impervious wall of the housing (1); in that the chamber (6) located outwardly of the partition wall (8) is intended to be through-passed by a cooling medium, whereas the chamber (7) located in¬ wardly of the partition wall (8) is intended to be through-passed by the liquid medium (3) enclosed in the housing (1); in that the inwardly located chamber (7) in¬ corporates a large number of flow channels (12) which are connected in parallel with regard to the flow of the li¬ quid medium therethrough; in that the flow channels (12) have a narrow rectangular cross-sectional shape dimen¬ sioned for laminar flow of the liquid medium therethrough and are defined by fins (11) formed integrally with the partition wall (8); in that the one respective ends of the flow channels communicate with an inlet (13) to the cham¬ ber (7) via distribution channels (14), whereas the other respective ends of the flow channels communicate with an outlet (16) from the chamber (7) via collecting channels (15); and in that the heat exchanger (4) is so positioned in the housing (1) that the inlet (13) and the outlet (16) fo - the chamber (7) located inwardly of the partition wall (8) have a mutual position such that when the machine is working, the liquid medium (3) will flow through the cham- ber (7), from the chamber inlet (13) to the chamber outlet (16), under the influence of the movement of the mechani¬ cal elements (2) housed in said housing.
2. An arrangement according to claim 1, characterized in that the inlet (13) to the chamber (7) is located on a higher level than the outlet (16); and in that the liquid medium (3) is raised to the inlet (13) under the influence the movement of the mechanical element (2).
3. An arrangement according to claim 1, characterized in that movement of the mechanical elements (2) engenders a hydrodynamic pressure difference between the inlet (13) and the outlet (16) of said chamber (7).
PCT/SE1988/000071 1987-02-24 1988-02-18 A heat exchanger arrangement for cooling a machine WO1988006678A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
HU881751A HU206533B (en) 1987-02-24 1988-02-18 Heat-exchanging arrangement for cooling machines
AT88901966T ATE80698T1 (en) 1987-02-24 1988-02-18 HEAT EXCHANGE ARRANGEMENT FOR COOLING AN ENGINE.
BR888807379A BR8807379A (en) 1987-02-24 1988-02-18 SYSTEM FOR COOLING A MACHINE
DE8888901966T DE3874730T2 (en) 1987-02-24 1988-02-18 HEAT EXCHANGE ARRANGEMENT FOR COOLING A MACHINE.
US07/501,320 US5072784A (en) 1987-02-24 1990-03-29 Heat exchanger arrangement for cooling a machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8700774-6 1987-02-24
SE8700774A SE455716B (en) 1987-02-24 1987-02-24 REVOLUTION DEVICE FOR COOLING A MACHINE

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WO1988006678A1 true WO1988006678A1 (en) 1988-09-07

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PCT/SE1988/000071 WO1988006678A1 (en) 1987-02-24 1988-02-18 A heat exchanger arrangement for cooling a machine

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US (1) US5072784A (en)
EP (1) EP0346371B1 (en)
JP (1) JP2704283B2 (en)
AT (1) ATE80698T1 (en)
AU (1) AU621289B2 (en)
BR (1) BR8807379A (en)
CA (1) CA1305128C (en)
DE (1) DE3874730T2 (en)
HU (1) HU206533B (en)
SE (1) SE455716B (en)
WO (1) WO1988006678A1 (en)

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WO2011094151A1 (en) * 2010-01-27 2011-08-04 Rexnord Industries, Llc Transmission having a fluid cooling shroud
WO2014153662A1 (en) * 2013-03-28 2014-10-02 Dana Canada Corporation Heat exchanger and system for warming and cooling a fluid circulating in a housing
WO2021219364A1 (en) * 2020-04-30 2021-11-04 Renault S.A.S Thermal control method and device for a gearbox

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DE102006062729B4 (en) * 2006-05-03 2020-06-10 Sew-Eurodrive Gmbh & Co Kg Cooling module for a transmission and transmission with cooling device
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US8715127B2 (en) * 2008-01-04 2014-05-06 American Axle & Manufacturing, Inc. Axle assembly with axle housing assembly having air scoops for cooling
DE102008008585A1 (en) * 2008-02-12 2009-08-13 Bayerische Motoren Werke Aktiengesellschaft Vehicle has gear, which is accommodated in gear housing and has gear oil circulation system, and gear oil circulation system is thermally coupled with coolant circuit over heat exchanger
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DE102010004222A1 (en) * 2009-01-19 2010-07-29 Magna Powertrain Ag & Co Kg Gearbox with lubrication device
DE102009025027B3 (en) 2009-06-10 2011-02-10 Siemens Aktiengesellschaft industrial gear
EP2410210B1 (en) 2010-07-22 2013-03-27 Siemens Aktiengesellschaft Transmission for industrial applications
ES2404843T3 (en) 2010-07-22 2013-05-29 Siemens Aktiengesellschaft Cooling device for a transmission mechanism
US9151539B2 (en) * 2011-04-07 2015-10-06 Hamilton Sundstrand Corporation Heat exchanger having a core angled between two headers
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JP6288050B2 (en) * 2015-11-24 2018-03-07 マツダ株式会社 Case of structure and method of manufacturing the same
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DE102020211234A1 (en) * 2020-09-08 2022-03-10 Robert Bosch Gesellschaft mit beschränkter Haftung Transmission and a drive arrangement with a corresponding transmission
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DE102022203168A1 (en) 2022-03-31 2023-10-05 Zf Friedrichshafen Ag Multi-part oil pan for a drive train and drive train with the oil pan

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DE1193310B (en) * 1959-06-20 1965-05-20 Daimler Benz Ag Lube oil-coolant heat exchanger for internal combustion engines
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Publication number Priority date Publication date Assignee Title
WO2011094151A1 (en) * 2010-01-27 2011-08-04 Rexnord Industries, Llc Transmission having a fluid cooling shroud
CN102859254A (en) * 2010-01-27 2013-01-02 莱克斯诺工业有限公司 Transmission Having A Fluid Cooling Shroud
TWI561749B (en) * 2010-01-27 2016-12-11 Rexnord Ind Llc Transmission having a fluid cooling shroud
US9599406B2 (en) 2010-01-27 2017-03-21 Rexnord Industries, Llc Transmission having a fluid cooling shroud
WO2014153662A1 (en) * 2013-03-28 2014-10-02 Dana Canada Corporation Heat exchanger and system for warming and cooling a fluid circulating in a housing
US10125644B2 (en) 2013-03-28 2018-11-13 Dana Canada Corporation Heat exchanger and system for warming and cooling a fluid circulating in a housing
WO2021219364A1 (en) * 2020-04-30 2021-11-04 Renault S.A.S Thermal control method and device for a gearbox
FR3109799A1 (en) * 2020-04-30 2021-11-05 Renault GEARBOX THERMAL CONTROL METHOD AND DEVICE

Also Published As

Publication number Publication date
JPH01502520A (en) 1989-08-31
SE455716B (en) 1988-08-01
HUT50517A (en) 1990-02-28
BR8807379A (en) 1990-02-13
EP0346371A1 (en) 1989-12-20
EP0346371B1 (en) 1992-09-16
AU1390088A (en) 1988-09-26
CA1305128C (en) 1992-07-14
HU206533B (en) 1992-11-30
ATE80698T1 (en) 1992-10-15
DE3874730D1 (en) 1992-10-22
JP2704283B2 (en) 1998-01-26
US5072784A (en) 1991-12-17
AU621289B2 (en) 1992-03-12
SE8700774D0 (en) 1987-02-24
DE3874730T2 (en) 1993-02-04

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