EP1167910B1 - Condenseur - Google Patents

Condenseur Download PDF

Info

Publication number
EP1167910B1
EP1167910B1 EP01115028A EP01115028A EP1167910B1 EP 1167910 B1 EP1167910 B1 EP 1167910B1 EP 01115028 A EP01115028 A EP 01115028A EP 01115028 A EP01115028 A EP 01115028A EP 1167910 B1 EP1167910 B1 EP 1167910B1
Authority
EP
European Patent Office
Prior art keywords
path
refrigerant
paths
headers
cross
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
EP01115028A
Other languages
German (de)
English (en)
Other versions
EP1167910A2 (fr
EP1167910A3 (fr
Inventor
Manaka Oyama Regional Office Hideaki
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.)
Resonac Holdings Corp
Original Assignee
Showa Denko KK
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 Showa Denko KK filed Critical Showa Denko KK
Publication of EP1167910A2 publication Critical patent/EP1167910A2/fr
Publication of EP1167910A3 publication Critical patent/EP1167910A3/fr
Application granted granted Critical
Publication of EP1167910B1 publication Critical patent/EP1167910B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F28F9/0212—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions the partitions being separate elements attached to header boxes
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a use of a condenser and to a refrigeration System for, for example, car air-conditioners.
  • a conventional multi-flow type condenser for use in car air-conditioners includes a pair of vertical headers 1 and 1 disposed apart from each other and a plurality of horizontal flat tubes 2 as heat exchanging tubes disposed between the headers at certain intervals in the direction of up-and-down with their opposite ends connected with the headers.
  • One of the headers 1 is provided with a refrigerant inlet 1a at the upper end portion thereof, and the other header 1 is provided with a refrigerant outlet 1b at the lower portion thereof.
  • the headers 1 are provided with partitions 5 each disposed at a predetermined portion for dividing the inside of the header to thereby group the aforementioned plurality of flat tubes 2 into a plurality of paths P1 to P3.
  • the refrigerant introduced from the refrigerant inlet 1a passes downwardly through each path P1 to P3 in sequence in a meandering manner, and then flows out of the refrigerant outlet 1b.
  • the refrigerant exchanges heat with the ambient air to be condensed into a liquefied refrigerant.
  • the inventors of the present application analyzed the stagnation of the liquefied refrigerant in the aforementioned condenser by using a thermography. According to the results of the analysis, as shown in Figs. 9 and 10, the liquefied refrigerant RL tends to stagnate at the downstream lower portion in each path P1-P3.
  • the liquefied refrigerant RL tends to stagnate at the downstream lower portion in each path P1-P3.
  • the liquefaction of refrigerant has already started at the end portion in the first path P1. Therefore, the liquefied refrigerant RL stays at the bottom of the header portion connecting the first and second paths P1 and P2, which may cause the so-called liquid stagnation.
  • the liquefied refrigerant RL impedes the refrigerant circulation, resulting in an increased refrigerant flow resistance.
  • US 6,021,846 discloses a duplex heat exchanger comprising: a plurality of unit heat exchangers; each of the unit heat exchangers having a circuit formed therethrough for a heat exchanging medium; and a connecting means for connecting the circuits in fluid communication with each other, each of the unit heat exchangers comprising: a plurality of tubes arranged in parallel with each other; and a pair of hollow headers to which both ends of each tube are connected in fluid communication, wherein the unit heat exchangers are arranged fore and aft in a direction of air flow so that one of said unit heat exchangers faces windward, with the other said unit exchangers lying leeward, wherein the circuits formed through the unit heat exchangers for the heat exchanging medium are connected in parallel with one another.
  • US 5,730,212 discloses a refrigerant condenser for use in a vehicle air-conditioner, comprising a pair of headers which form an inlet and an outlet for refrigerant and which are connected by a plurality of tubes, wherein the number of turns may be set to 2 by means of separators, wherein the tubes may be set to a combination of 11, 11, and 10 or 16, 12, and 4.
  • US 6,062,303 discloses a multiflow type condenser comprising a pair of header pipes disposed in parallel with each other and arranged to have an inlet and an outlet; a plurality of tubes each connected to said header pipes at opposite ends thereof, at least a pair of baffles disposed in said header pipes; and an area of a pass on the inlet side defined by the chamber on the inlet side of the chambers divided by the baffles, into which the refrigerant is introduced through said inlet and formed in one of the header pipes, the opposed chamber formed in the other of the header pipes, and a plurality of tubes extending between the chambers is about 30% to 65% of an overall area of all of the passes.
  • US 5,482,112 discloses a condenser comprising a plurality of tubular elements defining flow paths, and a pair of headers disposed at opposite ends of the tubular elements, the one/or the other header defining a coolant inlet and a coolant outlet, wherein both headers are divided in two sections by means of a partition to divide the whole coolant path into an inlet side group, an intermediate group and an outlet side group, and wherein the intermediate group has a cross-sectional area smaller that that of the inlet side group and greater than that of the outlet side group.
  • the gaseous refrigerant flowed out of the heat exchanging tubes constituting the upstream side path goes up vigorously in the refrigerant turning portion of the header connecting the adjacent paths, and the rising refrigerant flows into the heat exchanging tubes constituting the downstream side path (upper side path).
  • the liquefied refrigerant is pushed up by the blow-up effect of this rising refrigerant, and flows into the heat exchanging tubes constituting the downstream side path (upper side path) smoothly. This prevents a stagnation of the liquefied refrigerant, which keeps a large effective heat transferring area of the heat exchanging portion and enables an equally distributed smooth refrigerant flow in each path.
  • the plurality of paths includes three or more paths including a first path, a second path and a third path through which the refrigerant introduced from the refrigerant inlet passes in sequence, a reduction rate of a cross-sectional area of the second path to a cross-sectional area of the first path is 50% or more, and a reduction rate of a cross-sectional area of the third path to a cross-sectional area of the second path is 40% or more.
  • Fig. 1 is a front view showing a condenser for use in car air-conditioners according to an embodiment of the present invention
  • Fig. 2 is a schematic front view showing a refrigerant circuit arrangement of the condenser according to the embodiment:
  • Fig. 3 is an enlarged cross-sectional view showing a first refrigerant turning portion and therearound of the condenser according to the embodiment
  • Fig. 4 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a second embodiment of the present invention
  • Fig. 5 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a third embodiment of the present invention
  • Fig. 6 is a schematic cross-sectional view showing a refrigerant circuit arrangement of a condenser for use in car air-conditioners according to a comparative example
  • Fig. 7 is a graph showing a relationship between a refrigerant flow resistance and a refrigerant circulation amount of the inventive and comparative condensers;
  • Fig. 8 is a partially omitted front view showing a conventional condenser for use in car air-conditioners
  • Fig. 9 is a schematic front view showing a refrigerant circuit arrangement of the conventional condenser.
  • Fig. 10 is a schematic cross-sectional view showing a first refrigerant turning portion and therearound of the conventional condenser.
  • Figs. 1 and 2 show a multi-flow type condenser for use in car air-conditioners according to an embodiment of the present invention.
  • this condenser has a pair of right and left headers 11 and 11 disposed at a certain distance. Between these headers 11 and 11, a plurality of flat tubes 12 as heat exchanging tubes are horizontally disposed at certain intervals in the vertical direction with their opposites ends connected to the headers 11 and 11. Furthermore, corrugated fins 13 are arranged between adjacent flat tubes 12 and disposed on the outermost flat tubes 12. Furthermore, on the outside of each outermost corrugated fin 13, a belt-shaped side plate 14 is disposed for protecting the outermost corrugated fin 13.
  • a refrigerant inlet 11a is provided at the lower side of one of headers 11 (right header).
  • a refrigerant outlet 11b is provided at the upper side of the other header 11 (left header).
  • each header 11 a partition 16 which divides the interior of the header 11 in the longitudinal direction thereof is provided, to thereby group the aforementioned plurality of flat tubes 12 into three paths, the first path P1 (lowermost path), the second path P2 (middle path) and the third path P3 (uppermost path).
  • the header portion of the left header 11 which connects the first path P1 with the second paths P1 and P2 constitutes a first refrigerant turning portion T1
  • the header portion of the right header 11 which connects the second P2 with the third paths P3 constitutes a second refrigerant turning portion T2.
  • each header portion constituting the turning portion T1 and T2 may be formed by a separate individual header pipe.
  • each path P1-P3 is decreased in cross-sectional area stepwise towards the downstream side path (upper side path) for each path.
  • the reduction rate of the cross-sectional area of the downstream side path (upper side path) of the two adjacent paths to the upstream side path (lower side path) thereof should be set to 20% or more, and it is preferable that the reduction rate is set to 30% or more.
  • the aforementioned reduction rate (%) can be obtained by the following formula: (1-PL/PU) ⁇ 100(%), where "PU” is a cross-sectional area of the upstream side path and "PL" is that of the downstream side path.
  • the aforementioned reduction rate is set to 25% or more in any two adjacent paths. It is more preferable that the reduction rate of the cross-sectional area of the second path to the cross-sectional area of the first path is 50% or more and that the reduction rate of the cross-sectional area of the third path to the cross-sectional area of the second path is 40% or more.
  • the condenser of this embodiment all of the flat tubes 12 have the same structure, and therefore the cross-sectional area of each path P1-P3 is in proportion to the number of tubes of each path P1-P3. Therefore, the reduction rate of the cross-sectional area between adjacent paths corresponds to the reduction rate of the number of tubes between the adjacent paths.
  • the first path P1 includes 22 flat tubes
  • the second path P2 includes 9 flat tubes
  • the third path P3 includes 5 flat tubes. Accordingly, the reduction rate of the cross-sectional areas between the first and second paths P1 and P2 is 59.1%, and that between the second and third paths P2 and P3 is 44.4%.
  • the reduction rate of the cross-sectional areas between adjacent paths may be set such that each path is constituted by the same number of tubes having different cross-sectional area.
  • the total number of the paths is not especially limited, it is preferable that the total number is set to 2 to 5, more preferably 3 or 4. The most suitable total number is 3. If the total number of paths is set too much, the reduction rate of the cross-sectional areas between adjacent paths, i.e., the reduction rate of the tube number between the adjacent paths in the aforementioned embodiment, becomes too small, which causes a trouble in securing the aforementioned reduction rate. Thus, an effective refrigerant blow-up effect may not be obtained.
  • the cross-sectional area of each path is decreased stepwise for every path towards the downstream side (upper side).
  • the heat exchange core may include adjacent paths each having the same cross-sectional area. Therefore, it should be understood that the present invention covers such a condenser including adjacent paths each having the same cross-sectional area, unless otherwise clearly defined.
  • the refrigerant introduced from the refrigerant inlet 11a passes upwardly through the first to third paths P1-P3 in sequence in a meandering manner, and flows out of the refrigerant outlet 11b. While passing through these paths, the refrigerant exchanges heat with the ambient air to be gradually condensed and liquefied.
  • the liquefaction of the gaseous refrigerant introduced from the refrigerant inlet 11a starts at the end portion of the first path P1, for example, and the liquefied refrigerant RL flows out of the tube-outlets of the first path P1 and tends to flow downwards in the first refrigerant turning portion T1, as shown in Fig 3.
  • the gaseous refrigerant RG flows out of the tube-outlets of the first path P1, and goes up vigorously in the first turning portion T1. This rising gaseous refrigerant RG pushes up the aforementioned liquefied refrigerant RL.
  • the liquefied refrigerant RL goes up in the first refrigerant turning portion T1 together with the gaseous refrigerant RG, and this rising mixture of refrigerant will be evenly distributed into each flat tube 12 constituting the second path P2 smoothly.
  • the cross-sectional area of the second path P2 is set to the aforementioned specific reduction rate to that of the first path P1
  • the flow velocity of the gaseous refrigerant rising in the first refrigerant turning portion T1 between the first and second paths P1 and P2 can be secured enough. Therefore, a sufficient blow-up effect in the refrigerant turning portion T1 can be obtained by the rising refrigerant, which in turn can prevent assuredly the stagnation of the liquefied refrigerant RL in the bottom portion of the refrigerant turning portion T1.
  • the whole core surface can be used effectively as a heat exchanging portion, resulting in an improved cooling performance.
  • the refrigerant will not stagnate and will pass through the whole region of each path in an evenly distributed manner, the refrigerant flow resistance can be reduced, resulting in a further enhanced heat exchanging performance.
  • a condenser was manufactured in accordance with the aforementioned embodiment shown in Figs. 1 and 2.
  • This condenser has three paths, i.e., the lowermost first path P1, the middle second path P2 and the uppermost third path P3.
  • the first, second and third paths P1, P2 and P3 include twenty-two (22) tubes, nine (9) tubes and five (5) tubes, respectively.
  • the reduction rate of the cross-sectional area of the second path P2 to that of the first path P1 is 59.1%
  • the reduction rate of the cross-sectional area of the third path P3 to that of the second path P2 is 44.4%
  • a condenser having three paths i.e., the lowermost first path P1, the middle second path P2 and the uppermost third path P3, was manufactured.
  • the first, second and third paths P1, P2 and P3 include eighteen (18) tubes, nine (9) tubes and five (5) tubes, respectively.
  • Another structure is the same as the condenser of the first example. In this condenser, the reduction rate of the cross-sectional area of the second path P2 to that of the first path P1 is 50%, and the reduction rate of the cross-sectional area of the third path P3 to that of the second path P2 is 44.4%
  • a condenser having four paths i.e., the lowermost first path P1, the lower middle second path P2, the upper middle third path P3 and the uppermost fourth path P4, was manufactured.
  • the first, second, third and fourth paths P1, P2, P3 and P4 include thirteen (13) tubes, nine (9) tubes, six (6) tubes and four (4) tubes, respectively.
  • Another structure is the same as the condenser of the first example.
  • the reduction rate of the cross-sectional area of the second path P2 to that of the first path P1 is 30.8%
  • the reduction rate of the cross-sectional area of the third path P3 to that of the second path P2 is 33.3%
  • the reduction rate of the cross-sectional area of the fourth path P4 to that of the third path P3 is 33.3%.
  • the reference numeral T4 denotes a fourth refrigerant turning portion (the same numeral will be used in Fig. 6)
  • a condenser having four paths i.e., the uppermost first path P1, the upper middle second path P2, the lower middle third path P3 and the lowermost fourth path P4, was manufactured.
  • the first, second, third and fourth paths P1, P2, P3 and P4 include thirteen (13) tubes, nine (9) tubes, six (6) tubes and four (4) tubes, respectively.
  • Another structure is the same as the condenser of the first example.
  • This condenser according to the comparative example has a symmetrical configuration rotated by 180 degrees to the aforementioned condenser according to the third example.
  • the reduction rate of the cross-sectional area of the second path P2 to that of the first path P1 is 30.8%
  • the reduction rate of the cross-sectional area of the third path P3 to that of the second path P2 is 33.3%
  • the reduction rate of the cross-sectional area of the fourth path P4 to that of the third path P3 is 33.3%.
  • the first and second examples A1 and A2 were able to reduce flow resistance remarkably.
  • the reason is considered as follows: since the reduction rate of the cross-sectional area of the second path P2 to the cross-sectional area of the first path P1 is set to 50% or more and the reduction rate of the cross-sectional area of the third path P3 to the cross-sectional area of the second path P2 is set to 40% or more, the refrigerant blow-up effect between adjacent paths could fully be obtained and therefore the circulation of the refrigerant could be performed much more smoothly.

Landscapes

  • 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)
  • Air-Conditioning For Vehicles (AREA)
  • Valve Device For Special Equipments (AREA)
  • Oscillators With Electromechanical Resonators (AREA)

Claims (4)

  1. Utilisation d'un condenseur, lequel comprend :
    une paire de collecteurs gauche et droit (11, 11) ;
    une pluralité de tubes échangeurs de chaleur (12) disposés à intervalles prédéterminés entre lesdits collecteurs, les extrémités opposées de ceux-ci étant raccordées auxdits collecteurs ;
    au moins une séparation (16) prévue dans l'un respectif desdits collecteurs (11) permettant de grouper ladite pluralité de tubes échangeurs de chaleur (12) en une pluralité de voies (P1, P2, P3) ; et
    un orifice d'admission de fluide réfrigérant (11a) prévu au niveau d'une partie d'extrémité de l'un desdits collecteurs (11), et un orifice d'échappement de fluide réfrigérant (11b) prévu au niveau d'une partie d'extrémité opposée de l'un desdits collecteurs (11),
    dans lequel ladite pluralité de voies comprend trois voies ou plus comprenant une première voie (P1), une deuxième voie (P2) et une troisième voie (P3) à travers lesquelles ledit fluide réfrigérant introduit depuis ledit orifice d'admission de fluide réfrigérant (11a) passe en séquence, dans lequel une aire en coupe transversale de chacune desdites voies (P1, P2, P3) décroît successivement en direction d'un côté d'aval desdites voies (P1, P2, P3) pour chaque voie, dans lequel un taux de réduction d'une aire en coupe transversale de ladite deuxième voie (P2) par rapport à une aire en coupe transversale de ladite première voie (P1) est de 50 % ou plus, et dans lequel un taux de réduction d'une aire en coupe transversale de ladite troisième voie (P3) par rapport à une aire en coupe transversale de ladite deuxième voie (P2) est de 40 % ou plus,
    de manière à ce que
    le condenseur soit muni de ses collecteurs (11, 11) s'étendant verticalement et des tubes échangeurs de chaleur (12) s'étendant horizontalement, dans lequel ledit orifice d'admission de fluide réfrigérant (11a) est prévu au niveau d'une position inférieure et ledit orifice d'échappement de fluide réfrigérant (11b) est prévu au niveau d'une position supérieure de façon à ce qu'un fluide réfrigérant introduit depuis ledit orifice d'admission de fluide réfrigérant (11a) passe vers le haut à travers ladite pluralité de voies (P1, P2, P3) en séquence en décrivant des méandres, et s'écoule hors dudit orifice d'échappement de fluide réfrigérant (11b).
  2. Utilisation du condenseur selon la revendication 1, dans lequel chacun desdits taux de réduction est atteint en diminuant le nombre desdits tubes échangeurs de chaleur (12) constituant chacune desdites voies (P1, P2, P3).
  3. Système de réfrigération ayant un condenseur qui lui-même comprend une paire de collecteurs gauche et droit (11, 11) ; une pluralité de tubes échangeurs de chaleur (12) à intervalles prédéterminés entre lesdits collecteurs, les extrémités opposées de ceux-ci étant raccordées auxdits collecteurs, au moins une séparation (16) prévue dans l'un respectif desdits collecteurs (11) permettant de grouper ladite pluralité de tubes échangeurs de chaleur (12) en une pluralité de voies (P1, P2, P3) ; un orifice d'admission de fluide réfrigérant (11a) prévu au niveau d'une partie d'extrémité de l'un desdits collecteurs (11) ; et un orifice d'échappement de fluide réfrigérant (11b) prévu au niveau d'une partie d'extrémité opposée de l'un desdits collecteurs (11), dans lequel ladite pluralité de voies comprend trois voies ou plus comprenant une première voie (P1), une deuxième voie (P2) et une troisième voie (P3) à travers lesquelles ledit fluide réfrigérant introduit depuis ledit orifice d'admission de fluide réfrigérant (11a) passe en séquence, dans lequel une aire en coupe transversale de chacune desdites voies (P1, P2, P3) décroît successivement en direction d'un côté d'aval desdites voies (P1, P2, P3) pour chaque voie, dans lequel un taux de réduction d'une aire en coupe transversale de ladite deuxième voie (P2) par rapport à une aire en coupe transversale de ladite première voie (P1) est de 50 % ou plus, dans lequel un taux de réduction d'une aire en coupe transversale de ladite troisième voie (P3) par rapport à une aire en coupe transversale de ladite deuxième voie (P2) est de 40 % ou plus, et
    dans lequel le condenseur est agencé de façon à ce que ses collecteurs (11, 11) s'étendent verticalement avec les tubes échangeurs de chaleur (12) s'étendant horizontalement, dans lequel l'orifice d'admission de fluide réfrigérant (11a) est prévu au niveau d'une position inférieure et ledit orifice d'échappement de fluide réfrigérant (11b) est prévu au niveau d'une position supérieure de façon à ce qu'un fluide réfrigérant introduit depuis ledit orifice d'admission de fluide réfrigérant (11a) passe vers le haut à travers ladite pluralité de voies (P1, P2, P3) en séquence en décrivant des méandres, et s'écoule hors dudit orifice d'échappement de fluide réfrigérant (11b).
  4. Système de réfrigération selon la revendication 3, dans lequel chacun desdits taux de réduction est atteint en diminuant le nombre desdits tubes échangeurs de chaleur (12) constituant chacune desdites voies (P1, P2, P3).
EP01115028A 2000-06-20 2001-06-20 Condenseur Expired - Lifetime EP1167910B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000183966 2000-06-20
JP2000183966 2000-06-20

Publications (3)

Publication Number Publication Date
EP1167910A2 EP1167910A2 (fr) 2002-01-02
EP1167910A3 EP1167910A3 (fr) 2003-11-26
EP1167910B1 true EP1167910B1 (fr) 2006-02-01

Family

ID=18684466

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01115028A Expired - Lifetime EP1167910B1 (fr) 2000-06-20 2001-06-20 Condenseur

Country Status (5)

Country Link
US (1) US20020007646A1 (fr)
EP (1) EP1167910B1 (fr)
AT (1) ATE317100T1 (fr)
DE (1) DE60116922T2 (fr)
ES (1) ES2257360T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008038498A1 (de) * 2008-08-20 2010-02-25 Behr Gmbh & Co. Kg Wärmetauscher für ein Kraftfahrzeug
CN102221271A (zh) * 2010-04-16 2011-10-19 昭和电工株式会社 冷凝器
CN102221272A (zh) * 2010-04-16 2011-10-19 昭和电工株式会社 冷凝器

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7046514B2 (en) * 2003-03-19 2006-05-16 American Power Conversion Corporation Data center cooling
ES2355715T5 (es) * 2003-04-15 2019-10-22 Nestle Waters Management & Tech Recipiente de paredes delgadas
DE102004001786A1 (de) * 2004-01-12 2005-08-04 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere für überkritischen Kältekreislauf
EP1557630A1 (fr) 2004-01-23 2005-07-27 BEHR Lorraine S.A.R.L. Echangeur de chaleur
US20070044948A1 (en) * 2005-08-31 2007-03-01 Jing-Ron Lu Water-cooled cooler for CPU of PC
FR2915793B1 (fr) * 2007-05-03 2015-05-01 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile
FR2928448B1 (fr) * 2008-03-04 2015-05-01 Valeo Systemes Thermiques Refroidisseur de gaz ameliore
WO2010105170A2 (fr) * 2009-03-13 2010-09-16 Carrier Corporation Ensemble collecteur pour distribuer un fluide à un échangeur de chaleur
JP2011085368A (ja) * 2009-10-19 2011-04-28 Sharp Corp 熱交換器及びそれを搭載した空気調和機
US20110108259A1 (en) * 2009-11-06 2011-05-12 Twin Air B.V. Holland Oil Cooler For A Motorized Vehicle
JP5732258B2 (ja) * 2010-02-16 2015-06-10 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
DE102010039511A1 (de) * 2010-08-19 2012-02-23 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
DE102011007216A1 (de) * 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
JP2013002774A (ja) * 2011-06-20 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
FR2986316B1 (fr) * 2012-01-30 2014-01-10 Valeo Systemes Thermiques Ensemble comprenant un echangeur de chaleur et un support sur lequel ledit echangeur est monte
JP5609916B2 (ja) * 2012-04-27 2014-10-22 ダイキン工業株式会社 熱交換器
DE102013204294A1 (de) * 2013-03-12 2014-10-02 Behr Gmbh & Co. Kg Kondensatorbaugruppe für Kältemittel
JP6026956B2 (ja) * 2013-05-24 2016-11-16 サンデンホールディングス株式会社 室内熱交換器
KR20160131577A (ko) * 2015-05-08 2016-11-16 엘지전자 주식회사 공기조화기의 열교환기
WO2017064531A1 (fr) * 2015-10-12 2017-04-20 Carrier Corporation Échangeur de chaleur pour des applications résidentielles de chauffage, ventilation et climatisation (hvac)
CN105727683A (zh) * 2016-05-09 2016-07-06 洛阳瑞昌石油化工设备有限公司 一种烟气冷凝静电处理装置和处理工艺
EP3580505A4 (fr) * 2017-02-13 2020-12-16 Evapco, Inc. Condenseur de trajet de fluide à multiple sections transversales
US20180238644A1 (en) * 2017-02-13 2018-08-23 Evapco, Inc. Multi-cross sectional fluid path condenser
TWI738584B (zh) * 2020-03-27 2021-09-01 雙鴻科技股份有限公司 液冷排模組
CN113707969A (zh) * 2020-05-08 2021-11-26 恒大新能源技术(深圳)有限公司 液冷板、电池包及流量控制方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
US5529116A (en) * 1989-08-23 1996-06-25 Showa Aluminum Corporation Duplex heat exchanger
US5682944A (en) * 1992-11-25 1997-11-04 Nippondenso Co., Ltd. Refrigerant condenser
DE69626595T2 (de) * 1995-10-18 2003-09-18 Calsonic Kansei Corp Verflüssiger mit einem Flüssigkeitsbehälter
JP3131774B2 (ja) * 1997-09-26 2001-02-05 漢拏空調株式会社 車両エアコン用の多重流動型凝縮器

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008038498A1 (de) * 2008-08-20 2010-02-25 Behr Gmbh & Co. Kg Wärmetauscher für ein Kraftfahrzeug
CN102221271A (zh) * 2010-04-16 2011-10-19 昭和电工株式会社 冷凝器
CN102221272A (zh) * 2010-04-16 2011-10-19 昭和电工株式会社 冷凝器
CN102221271B (zh) * 2010-04-16 2015-11-25 株式会社京滨冷暖科技 冷凝器
CN102221272B (zh) * 2010-04-16 2015-11-25 株式会社京滨冷暖科技 冷凝器

Also Published As

Publication number Publication date
ATE317100T1 (de) 2006-02-15
DE60116922T2 (de) 2006-09-14
ES2257360T3 (es) 2006-08-01
EP1167910A2 (fr) 2002-01-02
EP1167910A3 (fr) 2003-11-26
DE60116922D1 (de) 2006-04-13
US20020007646A1 (en) 2002-01-24

Similar Documents

Publication Publication Date Title
EP1167910B1 (fr) Condenseur
EP0643278B1 (fr) Evaporateur pour refroidisseurs dans les véhicules automobiles
JP5486782B2 (ja) エバポレータ
US5988267A (en) Multistage gas and liquid phase separation type condenser
US7640970B2 (en) Evaporator using micro-channel tubes
CN103890532B (zh) 扁平管翅片式热交换器以及制造方法
KR20060086708A (ko) 열교환기
US20070131393A1 (en) Heat exchanger
US20060179876A1 (en) Evaporator for carbon dioxide air-conditioner
US20120080173A1 (en) Heat exchanger assembly having multiple heat exchangers
US20060060327A1 (en) Integrated condenser oil cooler with a receiver/dryer
US7013952B2 (en) Stack type heat exchanger
JP6842915B6 (ja) エバポレータ
US20070056718A1 (en) Heat exchanger and duplex type heat exchanger
JPH0626780A (ja) 熱交換器
JP2003166797A (ja) 熱交換器
KR20070102172A (ko) 응축기와 오일쿨러 일체형 열교환기
JP2018087646A (ja) エバポレータ
JP3044074B2 (ja) マルチパス蒸発器
US20070068665A1 (en) Heat exchanger comprising an integrated supply and discharge
CN107806723B (zh) 壳管式冷凝器
JPH085198A (ja) 空調用熱交換器
JP2002081797A (ja) 凝縮器
JP2001133076A (ja) 熱交換器
JP4328411B2 (ja) 熱交換器

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20040227

17Q First examination report despatched

Effective date: 20040421

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

Ref country code: LI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

Ref country code: CH

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 60116922

Country of ref document: DE

Date of ref document: 20060413

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060501

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060501

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060630

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060703

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2257360

Country of ref document: ES

Kind code of ref document: T3

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20061103

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20070614

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20070626

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20070620

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20070613

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060502

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20070608

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20060201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20080620

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20090228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080620

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080620

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20080621

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080620

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080621

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60116922

Country of ref document: DE

Representative=s name: VIERING, JENTSCHURA & PARTNER, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60116922

Country of ref document: DE

Representative=s name: VIERING, JENTSCHURA & PARTNER PATENT- UND RECH, DE

Effective date: 20121217

Ref country code: DE

Ref legal event code: R081

Ref document number: 60116922

Country of ref document: DE

Owner name: KEIHIN THERMAL TECHNOLOGY CORP., OYAMA-SHI, JP

Free format text: FORMER OWNER: SHOWA DENKO K.K., TOKIO/TOKYO, JP

Effective date: 20121217

Ref country code: DE

Ref legal event code: R082

Ref document number: 60116922

Country of ref document: DE

Representative=s name: VIERING, JENTSCHURA & PARTNER MBB PATENT- UND , DE

Effective date: 20121217

Ref country code: DE

Ref legal event code: R082

Ref document number: 60116922

Country of ref document: DE

Representative=s name: VIERING, JENTSCHURA & PARTNER, DE

Effective date: 20121217

Ref country code: DE

Ref legal event code: R081

Ref document number: 60116922

Country of ref document: DE

Owner name: KEIHIN THERMAL TECHNOLOGY CORP., JP

Free format text: FORMER OWNER: SHOWA DENKO K.K., TOKIO/TOKYO, JP

Effective date: 20121217

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20170613

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60116922

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190101