EP1141645B1 - Radial flow annular heat exchangers - Google Patents

Radial flow annular heat exchangers Download PDF

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Publication number
EP1141645B1
EP1141645B1 EP99964346A EP99964346A EP1141645B1 EP 1141645 B1 EP1141645 B1 EP 1141645B1 EP 99964346 A EP99964346 A EP 99964346A EP 99964346 A EP99964346 A EP 99964346A EP 1141645 B1 EP1141645 B1 EP 1141645B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
flow
outer peripheral
plate pairs
plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99964346A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1141645A1 (en
Inventor
Alan K. Wu
Bruce L. Evans
Henri P. T. Van Helden
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.)
Dana Canada Corp
Original Assignee
Long Manufacturing Ltd
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 Long Manufacturing Ltd filed Critical Long Manufacturing Ltd
Publication of EP1141645A1 publication Critical patent/EP1141645A1/en
Application granted granted Critical
Publication of EP1141645B1 publication Critical patent/EP1141645B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form

Definitions

  • This invention relates to heat exchangers, and in particular, to oil coolers of the so called “doughnut” type that can be used separately or in conjunction with oil filters in automotive and other engine and transmission cooling applications.
  • Oil coolers have been made in the past out of a plurality of stacked plate pairs located in a housing or canister.
  • the canister usually has inlet and outlet fittings for the flow of engine coolant into and out of the canister circulating around the plate pairs.
  • the plate pairs themselves have inlet and outlet openings and these openings are usually aligned to form manifolds, so that the oil passes through all of the plate pairs simultaneously.
  • manifolds communicate with oil supply and return lines located externally of the canister.
  • An example of such an oil cooler is shown in Japanese Utility Model Laid Open Publication No. 63-23579 published February 16, 1988.
  • the plate pairs are usually in the form of an annulus and a conduit passes through the centre of the annulus delivering oil to or from the filter located above or below the oil cooler and connected to the conduit.
  • the oil can pass through the filter and then the oil cooler, or vice-versa. Examples of such oil coolers are shown in United States patents Nos. 4,967,835 issued to Thomas E. Lefeber and No. 5,406,910 issued to Charles M. Wallin.
  • United States Patent No. 5,014,775 issued May 14,1991 to Toyo Radiator Co. Ltd. describes an oil cooler for motor oil used in engines, this cooler having a core comprising a plurality of sets of annular plates.
  • the plates are arranged in pairs with a fin member or turbulator placed on each pair of plates.
  • the stack of plates is arranged in a casing of the oil cooler.
  • the cooling water enters and exits from the stack of plates by means of two relatively large holes formed in the intermediate area of each plate. These coolant holes are placed on opposite sides of a partition ridge and bosses are formed around the holes.
  • the coolant passes in a circumferential direction between the plates of each pair while the oil flows radially from a central opening formed by the stack to the outer circumference of the stack of plates, this oil flow occurring in the outer passages formed between the back-to-back plate pairs.
  • European Patent No. 0430752 published June 5, 1991 also describes a circumferential flow heat exchanger made from a stack of plate pairs and suitable for cooling the oil of an engine.
  • the stack of plates forms a hollow central passageway and permits a generally circular flow path of fluid from an inlet to an outlet.
  • Each of the opposing plates undulates in cross-structure to define a plurality of opposing valleys that extend to the central passageway. At least some of these valleys on each plate are disposed at an oblique angle to the circular flow path.
  • the apexes of valleys of a first plate are arranged to cross apexes of valleys of a second plate.
  • European Patent Application No. 0208957 which was published on January 21, 1987 also describes a cooler for engine lubricant oil, this cooler being formed by a stack of metal plates formed by modules comprising upper and lower plates.
  • the plates have a so-called tongue shape with a straight edge formed along three sides and each plate being arcuate at one end.
  • the plates are each provided with first and second circular openings located adjacent opposite corners at one end of each plate and they also have central circular openings which are aligned with one another.
  • Annular flanges are formed around these central openings and the plates are joined together by means of these flanges.
  • the plates are also formed with a plurality of generally C-shaped circumferential ridges arranged around the central openings.
  • the water or coolant in this heat exchanger flows both circumferentially and in a zig zag manner.
  • the oil flows through the heat exchanger both in an axial direction through axially aligned openings and it can also flow in a zig zag manner.
  • the heat exchanger of the present invention is very efficient with relatively low pressure drop.
  • a first exchange fluid travels circumferentially through ringlike plate pairs, and all of a second heat exchange fluid flows between the plate pairs transversely relative to the first heat exchange fluid.
  • a heat exchanger which comprises a plurality of stacked plate pairs consisting of face-to-face, mating ringlike plates.
  • Each plate has an outer peripheral flange, an annular inner boss having a portion thereof located in a common plane with the peripheral flange, and an intermediate area located between the peripheral flange and the inner boss.
  • the peripheral flanges and inner bosses in the mating plates are joined together.
  • the intermediate areas have spaced-apart portions to form an inner flow passage between the plates.
  • the plate intermediate areas have spaced-apart intermediate sections located between the outer peripheral flange and the inner boss and these intermediate sections define inlet and outlet openings and are arranged such that in back-to-back plate pairs, the intermediate sections are joined and the respective inlet and outlet openings communicate to define inlet and outlet manifolds for the flow of a first exchange fluid circumferentially through the inner flow passages from the inlet manifold to the outlet manifold.
  • the adjacent intermediate areas in back-to-back plate pairs define outer flow passages therebetween.
  • a header is provided and this header includes a flow port for the flow of a second heat exchange fluid therethrough to force the second heat exchange fluid to flow transversely through the outer flow passages.
  • Combination unit 10 includes a housing 12 containing an oil filter 14 and a preferred embodiment of a heat exchanger according to the present invention indicated by reference numeral 16.
  • Oil filter 14 is conventional and is not per se considered to be part of the present invention.
  • Oil filter 14 is of the annular type and in Figure 1, oil flows from inside the housing inwardly through the filter walls to a central axial chamber 15 and passes downwardly through a pipe or conduit 18 to exit from combination unit 10.
  • housing 12 has a bottom plate 19 containing openings 20 therein for the passage of oil therethrough into heat exchanger 16 depending upon which way it is desired to have the oil flow through filter 14.
  • Conduits 22 and 24 are also attached to bottom plate 19 for the entry and exit of coolant into and out of heat exchanger 16.
  • heat exchanger 16 is formed of a plurality of stacked plate pairs 30 consisting of face-to-face mating, annular or ringlike plates 32.
  • each plate 32 has an outer peripheral flange 34, an annular inner boss 36 having a portion 37 located in a common plane with outer peripheral flange 34, and an intermediate area 39 located between peripheral flange 34 and inner boss 36.
  • a plurality of alternating ribs and grooves 38,40 are formed in intermediate area 39 and extend between the inner boss 36 and the peripheral flange 34.
  • the ribs and grooves 38,40 are flow augmentation means and are angularly disposed and in the form of spiral or involute curves, so that the ribs and grooves in the respective plates that make up plate pairs 30 cross forming an undulating inner flow passage 42 between the plates of each plate pair 30.
  • the ribs and grooves 38,40 in adjacent back-to-back plate pairs cross forming undulating outer flow passages 44 between the plate pairs 30.
  • Outer flanges 34 contain optional alignment notches 45 to assist in the proper alignment of plates 32 during the assembly of heat exchanger 16. Such alignment notches could be used in all of the embodiments of the present invention, if desired.
  • Plates 32 have spaced-apart intermediate sections 46 located between the outer peripheral flange 34 and the inner boss 36. These intermediate sections 46 define inlet and outlet openings 48, 50.
  • the intermediate bosses 46 are arranged such that in back-to-back plate pairs, the respective inlet and outlet openings 48, 50 are joined around their peripheries to communicate and define inlet and outlet manifolds 52, 54 (see Figure 3) for the flow of a first heat exchange fluid, such as engine coolant, circumferentially inside or through the inner flow passages of the plate pairs from inlet manifold 52 to outlet manifold 54.
  • the adjacent intermediate areas 39 in back-to-back plate pairs 30 define outer flow passages 44 therebetween.
  • Heat exchanger 16 has top and bottom closure plates 56, 58.
  • Bottom closure plate 58 has openings 62, 64 which register with respective inlet and outlet manifolds 52, 54.
  • Conduits 22,24 (see Figure 1) pass through housing bottom plate 19 to communicate with openings 62,64.
  • Ribs 38 and grooves 40 have a predetermined height and intermediate sections or bosses 46 have a height, or depth as seen in Figure 4, that is at least as high as ribs 38, and preferably the same height as ribs 38, so that when the plate pairs are placed back-to-back as seen best in Figure 6, the ribs 38 on adjacent plates touch as do the outer surfaces of intermediate sections 46.
  • the height of inner annular bosses 36 and outer peripheral flanges 34 is greater than the height of the ribs and grooves, so that the adjacent ribs 38 on the inside of plate pairs 30 are slightly spaced apart. This reduces the water-side pressure drop for the coolant flowing through plate pairs 30.
  • a radial rib 66 extends between the intermediate sections 46 from the inner boss 36 to the outer peripheral flange 34.
  • Radial rib 66 is in the same plane as or has the same height as inner boss 36 and outer peripheral flange 34, so that when two plates are put together to form a plate pair 30, the respective radial ribs 66 engage one another to prevent by-pass flow from inlet opening 48 to outlet opening 50.
  • Radial ribs 66 also form radial grooves on the outside or oil side of the plate pairs. These radial grooves improve the radial or transverse flow between the plate pairs near and around intermediate bosses 46.
  • Inner peripheral flanges 68 are formed on annular inner bosses 36 and have mating flange portions 69 located in a common plane with the intermediate sections or bosses 46, so that the inner peripheral flanges 68 on back-to-back plate pairs are joined together to form, with the inner bosses 36, a header 70 (see Figure 6) to cause all of the entering inlet openings 71 to flow transversely or radially through the outer flow passages 44 between the back-to-back plate pairs 30.
  • Inner boss 36 includes a plurality of apertures 72 spaced around inner boss 36. When plate pairs 30 are stacked together, apertures 72 are aligned or in registration to form flow ports for supplying fluid to header 70.
  • Figure 7 is a view similar to Figure 6, but which shows another embodiment of a heat exchanger 79 according to the present invention having stacked plate pairs that are similar to the embodiment of Figures 1 to 6, but where the inner header 70 of Figure 6 has been eliminated.
  • Primed reference numerals are used in Figures 7 to 25 to indicate modified components of the embodiment shown in Figures 1 to 6.
  • Inner bosses 36' have 5 been truncated leaving annular slots 80 for the flow of fluid into or out of the outer flow passages 44 between the plate pairs.
  • outer distal flanges 74 form a header enclosing outer peripheral flanges 34' to cause all of the respective heat exchange fluid to pass transversely or radially between the plate pairs.
  • the inner annular boss 36' and outer peripheral flange 34' have a height that is equal to the height of the ribs and grooves, so that the adjacent ribs 38 in inner flow passages 42' are not spaced-apart as in the embodiment shown in Figures 1 and 6.
  • the adjacent ribs 38 in the inner flow passages 42' could be spaced-apart as in Figure 6, or the Figure 6 embodiment could be made like Figure 7 with ribs 38 not spaced-apart, if desired.
  • FIG 8 shows another embodiment of a heat exchanger 801 where a header 82 is formed by the annular space defined by top and bottom closure plates 56, 58 and conduit 18 sealingly engaged therein. Neither the inner bosses 36' nor the outer peripheral flanges 34 have additional flanges formed thereon to form headers.
  • Bottom closure plate 58 includes a flow port 84 for the flow of fluid into or out of header 82.
  • a ringlike plate 85 which is similar to plate 32 of Figures 4 and 5, but which has a plurality of spaced-apart dimples 87 and 89 formed in the intermediate area 39 as the flow augmentation means instead of ribs 38 and grooves 40.
  • Dimples 87 extend into the outer flow passages 44 and dimples 89 extend into the inner flow passages 42.
  • Dimples 87, 89 have a predetermined height which, in the case of dimples 87, is preferably equal to the height of intermediate sections or bosses 46. However, some or all of the dimples 87 could have a height that is less than intermediate bosses 46. It will be seen from Figures 9 and 10 that in this embodiment the bosses 46 extend in a direction from the intermediate area 39 opposite to the peripheral flange 34 and inner boss 36.
  • plates 85 could be formed with outer distal flanges like flanges 74 in the embodiment shown in Figure 7 to define headers 76 at the outer periphery of the plates, either in addition to or instead of the inner peripheral flanges 68 and headers 70 as shown in Figure 6.
  • Dimples 87 and 89 are shown arranged in respective circumferential rows and generally equi-spaced, but they could be mixed in orientation and spaced apart differently to achieve specific flow effects inside and between the plate pairs.
  • FIG 11 shows another preferred embodiment of a combination heat exchanger and filter 91 which is similar to combination unit 10 of Figure 1, but which employs a heat exchanger 28 as shown in detail in Figures 12 to 14.
  • Top plate 56'in heat exchanger 28 is the bottom wall of housing 12' that contains filter 14, and a removable lid 93 allows for the replacement of filter 14.
  • heat exchanger 28 could be considered to be a modification to heat exchanger 16 of Figures 2 to 6.
  • the plates 32' have outer peripheral flanges 34' that have been extended radially, and an outer distal flange 74 is formed on outer peripheral flange 34'having mating flange portions 75.
  • Mating flange portions 75 are located in a common plane with the intermediate sections 46, so that the distal flanges 74 on back-to-back plate pairs 30' are joined to form, with the outer peripheral flanges 34', a header 76.
  • Apertures 77 are formed in outer peripheral flanges 34' and are aligned in the stacked plate pairs to form flow ports to receive fluid flowing between the back-to-back plate pairs. However, it will be appreciated that the flow direction could be reversed, so that header 76 supplies fluid to flow radially inwardly toward the centre of heat exchanger 28, if desired.
  • top closure plate 56' is formed with a plurality of openings 78 that communicate with apertures 77 and form part of headers 76 and also communicate with the inside of housing 12'. It will also be appreciated that heat exchanger 28 has two headers 70 and 76 with aligned apertures forming flow ports for these headers.
  • Figure 15 shows a plate 95 that is a modification of plate 32' such that plate 95 is rectangular in shape or plan view.
  • Outer peripheral flange 34" is rectangular as well, and although inner boss 36 is shown to be circular or annular, inner boss 36 could be rectangular as well, if desired.
  • plate 95 is still considered to come within the term annular or ringlike, the flow from inlet opening 48 to outlet opening 50 is still considered to be circumferential, and the flow from inner apertures 72 to outer apertures 77 is still considered to be radial or transverse with respect to the circumferential flow inside the plate pairs.
  • FIG 16 shows a modified top plate 56' for use with plates 95.
  • Top plate 56' has peripheral openings 97 that vary in size to obtain uniform flow distribution in the radial or transverse direction. It will be noted that the corner openings 97 are particularly large to increase the flow to the corners of a heat exchanger made with these plates. Alternatively, uniformly sized openings 97 spaced closer or further apart could be used to give a desired flow distribution instead of differently sized apertures 97. These aperture size or shape differences could also be employed in connection with apertures 77 in the core plates 95 of Figure 15, if desired.
  • Figure 17 shows yet another embodiment of a plate 99 used to form a heat exchanger according to the present invention which, like the plate 85 shown in Figures 9 and 10, has another type of flow augmentation instead of ribs and grooves as shown in Figures 1 to 6 or dimples as shown in Figures 9 and 10.
  • an expanded metal turbulizer 101 is used as the flow augmentation means.
  • turbulizer 101 could be formed of other materials than expanded metal, such as plastic mesh.
  • Figure 17 is a view of plate 99 looking at the oil side or outside of a plate pair. The intermediate areas 39 are located under turbulizer 101 and are still spaced-apart to form inner flow passages inside the plate pairs.
  • Turbulizer 101 could be any type of turbulizer, and if it has a flow resistance that varies in a particular direction, apertures 72 and 77 could be arranged differently or varied in size to suit the turbulizer and maintain uniform radial or transverse flow between the plate pairs. Turbulizers 101 could be employed inside the plate pairs in the inner flow passages as well as, or instead of, the turbulizers 101 used in the outer flow passages as shown in Figure 17.
  • FIGs 18 and 19 show a heat exchanger 28' that is a modification to the heat exchanger 28 shown in Figures 11 and 12.
  • an annular filter seat 103 is mounted on top of top closure plate 56 to accommodate a conventional spin-on oil filter 107 that screws onto conduit 18.
  • Filter seat 103 has inner openings 105 to allow fluid emerging from headers 76 or openings 78 to be delivered to filter inlet openings 109.
  • Figure 20 shows the inside or water side surface of a plate 32' where the inner annular boss 36' and the outer peripheral flange 34' are the same height with respect to both the intermediate sections or bosses 46 and inner peripheral flange 68 as the height of the ribs and grooves 38,40.
  • a spacer 86 as shown in Figure 21 can be used between the plates of the plate pairs.
  • Spacer 86 has an outer annular portion 88 which is located between outer peripheral flanges 34' and an inner annular portion 90 which is located between inner annular bosses 36'.
  • Inner annular portion 90 has a plurality of apertures 92 therein to correspond with apertures 72 in inner boss 36'. Rotation of spacer 86 relative to plates 32' causes apertures 92 to act as valves to obtain a predetermined setting or adjustment of the flow through apertures 72 during manufacture of heat exchangers using this type of plate.
  • Figures 22 and 23 show a plate 94 that is similar to plate 32' of Figure 20, but which has a peripheral by-pass groove 96 located inside the plate pairs adjacent to the outer peripheral flange 34'.
  • By-pass groove 96 has a first end portion 98 located adjacent to and communicating with one of the intermediate sections 46 and extends just over half-way around the perimeter of plate 94 to a second end portion 100, so that when two plates 94 are arranged face-to-face, end portions 100 overlap and by-pass groove 96 forms a half-height groove extending all the way around the periphery of the plate pair from one intermediate sections 46 to the other.
  • By-pass groove 96 is used to reduce internal pressure drop inside the plate pairs, if desired.
  • Figure 24 shows a plate 102 similar to plate 94 of Figure 23, but having at least one by-pass groove 104 extending between intermediate sections 46. Actually, because the grooves between intermediate sections 46 overlap and cross each other, several half-height by-pass channels extend between intermediate sections 46. Again, these by-pass channels are provided to reduce pressure drop inside the plate pairs. If desired, the by-pass grooves 104 can be used instead of peripheral by-pass groove 96.
  • Figure 25 shows a plate 102' that is a modification of plate 102 of Figure 24.
  • the by-pass grooves 104 are formed with flow limiting indentations 106 to control or set a predetermined amount of by-pass flow between intermediate sections or bosses 46.
  • the intermediate sections or bosses containing the inlet and outlet openings could be made smaller, so that inner annular bosses 36 could be the same width all around their circumference allowing apertures 72 to extend around the full circumference of these bosses.
  • the various heat exchangers can be made using any number of plate pairs and the various plate pair embodiments could be mixed and matched to achieve a particular desired performance.
  • the top and bottom closure plates could be eliminated in certain applications where other means are used to close the various flow manifolds formed by openings in the plates.
  • end plates could be used that are similar to plates used to make the plate pairs, in which case, the various inlet and outlet openings and apertures in these end plates would not be punched out.
  • Other configurations for the ribs and grooves and dimples and turbulizers could also be employed in the plates, if desired.
  • the heat exchangers of the present invention can be used for cooling or heating other engine fluids, such as, fuel, transmission fluid, hydraulic steering fluid, refrigerant and even engine coolant itself. Either fluid can pass between the plate pairs or through the plate pairs, and the heat exchangers of the present invention can be used to heat fluids as well as cool them. Further, the heat exchangers of the present invention can be used in applications other than in the automotive industry.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP99964346A 1998-12-23 1999-12-23 Radial flow annular heat exchangers Expired - Lifetime EP1141645B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CA2257076 1998-12-23
CA002257076A CA2257076C (en) 1998-12-23 1998-12-23 Radial flow annular heat exchangers
PCT/CA1999/001246 WO2000039516A1 (en) 1998-12-23 1999-12-23 Radial flow annular heat exchangers

Publications (2)

Publication Number Publication Date
EP1141645A1 EP1141645A1 (en) 2001-10-10
EP1141645B1 true EP1141645B1 (en) 2002-10-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99964346A Expired - Lifetime EP1141645B1 (en) 1998-12-23 1999-12-23 Radial flow annular heat exchangers

Country Status (9)

Country Link
EP (1) EP1141645B1 (ko)
JP (1) JP3493519B2 (ko)
KR (1) KR100412278B1 (ko)
AT (1) ATE225491T1 (ko)
AU (1) AU755895B2 (ko)
CA (1) CA2257076C (ko)
DE (1) DE69903350T2 (ko)
ES (1) ES2186430T3 (ko)
WO (1) WO2000039516A1 (ko)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11162736B2 (en) 2017-03-10 2021-11-02 Alfa Laval Corporate Ab Plate package, plate and heat exchanger device
WO2023191313A1 (en) * 2022-03-31 2023-10-05 Hanon Systems Receiver drier and economizer integration for vapor injection system

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2257076C (en) * 1998-12-23 2005-03-22 Long Manufacturing Ltd. Radial flow annular heat exchangers
FI118391B (fi) * 2001-12-27 2007-10-31 Vahterus Oy Laite pyöreän levylämmönvaihtimen lämmönsiirron parantamiseksi
JP4559251B2 (ja) * 2005-02-17 2010-10-06 本田技研工業株式会社 蓄熱装置
KR100704106B1 (ko) * 2006-12-01 2007-04-09 서동숭 유압기계 작동오일의 조립형 오일냉각기
US20100193168A1 (en) * 2009-02-02 2010-08-05 Johnson Jr Alfred Leroy Heat exchanger
CN103175430A (zh) * 2012-06-28 2013-06-26 郑州大学 环形微通道换热板
CN105651084B (zh) * 2016-01-13 2018-01-26 宁波市哈雷换热设备有限公司 板式热交换器
CN112066600A (zh) * 2019-06-11 2020-12-11 广东美的制冷设备有限公司 换热器及空调设备

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BE794794A (fr) 1971-11-04 1973-05-16 Modine Mfg Cy Appareil echangeur de chaleur
JPH073315B2 (ja) * 1985-06-25 1995-01-18 日本電装株式会社 熱交換器
JPS6323579A (ja) * 1986-07-16 1988-01-30 Matsushita Seiko Co Ltd 電動機の速度調節装置
US4967835A (en) 1989-08-21 1990-11-06 Modine Manufacturing Company, Inc. Filter first donut oil cooler
US5203832A (en) * 1989-11-17 1993-04-20 Long Manufacturing Ltd. Circumferential flow heat exchanger
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JPH06323579A (ja) 1993-05-18 1994-11-25 Sharp Corp 加湿器
US5406910A (en) 1993-11-22 1995-04-18 Ford Motor Company Combination oil cooler and oil filter assembly for internal combustion engine
WO1998044305A1 (en) * 1997-04-02 1998-10-08 Creare Inc. Radial flow heat exchanger
CA2257076C (en) * 1998-12-23 2005-03-22 Long Manufacturing Ltd. Radial flow annular heat exchangers
CA2260890A1 (en) * 1999-02-05 2000-08-05 Long Manufacturing Ltd. Self-enclosing heat exchangers

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11162736B2 (en) 2017-03-10 2021-11-02 Alfa Laval Corporate Ab Plate package, plate and heat exchanger device
WO2023191313A1 (en) * 2022-03-31 2023-10-05 Hanon Systems Receiver drier and economizer integration for vapor injection system

Also Published As

Publication number Publication date
DE69903350D1 (de) 2002-11-07
CA2257076C (en) 2005-03-22
KR100412278B1 (ko) 2003-12-31
DE69903350T2 (de) 2003-07-10
JP2002533654A (ja) 2002-10-08
EP1141645A1 (en) 2001-10-10
ATE225491T1 (de) 2002-10-15
WO2000039516A1 (en) 2000-07-06
JP3493519B2 (ja) 2004-02-03
AU3027500A (en) 2000-07-31
AU755895B2 (en) 2003-01-02
ES2186430T3 (es) 2003-05-01
CA2257076A1 (en) 2000-06-23
KR20010083957A (ko) 2001-09-03

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