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EP0650024B1 - Rohrelement für einen Laminatwärmetauscher - Google Patents

Rohrelement für einen Laminatwärmetauscher Download PDF

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Publication number
EP0650024B1
EP0650024B1 EP19940307738 EP94307738A EP0650024B1 EP 0650024 B1 EP0650024 B1 EP 0650024B1 EP 19940307738 EP19940307738 EP 19940307738 EP 94307738 A EP94307738 A EP 94307738A EP 0650024 B1 EP0650024 B1 EP 0650024B1
Authority
EP
European Patent Office
Prior art keywords
tank
beads
passage
bead
tube element
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
EP19940307738
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English (en)
French (fr)
Other versions
EP0650024A1 (de
Inventor
Kunihiko C/O Zexel Co. Konan Factory Nishishita
Yoshihisa c/o Zexel Co. Konan Factory Eto
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.)
Bosch Corp
Original Assignee
Zexel Corp
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
Priority claimed from JP5300956A external-priority patent/JP3028452B2/ja
Priority claimed from JP5345389A external-priority patent/JPH07167581A/ja
Application filed by Zexel Corp filed Critical Zexel Corp
Publication of EP0650024A1 publication Critical patent/EP0650024A1/de
Application granted granted Critical
Publication of EP0650024B1 publication Critical patent/EP0650024B1/de
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
    • F28F3/042—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 in the form of local deformations of the element
    • F28F3/044—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 in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits

Definitions

  • the present invention relates to a laminated heat exchanger in the form of an evaporator according to the preamble of claim 1.
  • GB-A-2223091 discloses a heat exchanger for use as a condenser having a multiplicity of flat tubes each formed with baffles defining a flow path for a heat-exchange fluid.
  • Each tube has internal projections with defined dimensions for width and spacing, but does not provide U-shaped passages with first and second passage legs on opposite sides of a junction wall.
  • US-A-5111878 discloses an evaporator having a plurality of U-flow tubes therein arranged side by side. The tubes have a plurality of flow ribs indented and joined in a predetermined pattern therein, but the dimensions of the indentations are not defined.
  • US-A-4800954 and US-A-5125453 also disclose evaporators with U-flows. In view of the considerable prior art in evaporators with U-flows it is from that art that the present invention was developed and since condensers normally involve different conditions of coolant pressure and/or temperature and radiation or absorbtion of heat, no one would have been motivated to adapt the evaporator of US-A-5111878 in accordance with a condenser without U-flow.
  • beads are formed in the heat exchanging medium passages of the tube elements to distribute the flow of the heat exchanging medium and, at the same time, to increase the contact area with the heat exchanging medium as a means for improving the heat exchanging efficiency.
  • the applicant also uses tube elements in which a plurality of round beads are press-formed into the formed plates that constitute the tube elements, as disclosed in, for example, Japanese unexamined Patent Publication S63-153397.
  • the tube element products of the relevant prior art have typically a bead diameter of 3.8mm, a minimum bead spacing of 7.0mm, a tube element thickness of 2.9mm and a plate thickness of 0.57mm in the formed plates.
  • the bead diameter or the minor axis is within the range of 3.5mm - 4.8mm
  • the tube element thickness is within the range of 2.8mm - 3.4mm
  • the plate thickness of the formed plates is within the range of 0.40mm - 0.57mm. Except for the bead spacing, regarding which we do not have information, our tube element fits within those ranges.
  • the flow of heat exchanging medium tends to take the shortest path available and, in a tube element provided with a U-shaped heat exchanging medium passage 7, as in the tube element shown in Figure 2, the heat exchanging medium tends to run along the projection 10 at the center. Because the beads are formed over the entire passage at a consistent density in the tube element of the prior art, there is no difference in passage resistance over the entirety of the passage. As a result, the heat exchanging medium travels along the projection, leaving areas where the heat exchanging medium becomes stagnant, such as at the upper sides of the tube element.
  • An object of the present invention is to provide a tube element which realizes an improvement in efficiency and which also makes it possible to manufacture a smaller heat exchanger.
  • An additional object is to provide a tube element with an improved bead arrangement by taking into consideration the necessity to reduce the number of beads in dead water regions and the necessity to disperse the flow of fluid by adjusting the passage resistance, thus achieving an improvement in heat exchanging efficiency.
  • the heat exchanging medium passes through without performing sufficient heat exchange thus degrading the heat exchanging performance.
  • the heat transfer rate is improved by reducing the thickness of the formed plates but this results in reduced anticorrosion characteristics and reduced strength. If the thickness of the formed plates is increased and the thickness of the tube element remains the same, the heat exchanging medium passage becomes narrower, increasing the passage resistance.
  • the present invention is a tube element for an evaporator in which tube elements and fins are laminated alternately over a plurality of rows wherein the fluid passage for the heat exchanging medium is formed by butting two formed plates one to another with beads that are formed in the aforementioned tube element as projections within the aforementioned fluid passage, in such a manner that the width of the beads A and the spacing of the beads B are set at 2.0mm ⁇ A 3.0mm and 3.5 ⁇ B ⁇ 6.3mm respectively.
  • the tube element thickness H and the formed plate thickness T may be set within the ranges of 1.9mm ⁇ H ⁇ 2.7mm and 0.25mm ⁇ T ⁇ 0.47mm respectively.
  • a plurality of bead rows which cross the direction of the fluid passage of the aforementioned heat exchanging medium at a right angle may be provided with the bead rows that lie adjacent to one another having different intervals between the beads so that the beads in adjacent bead rows are arranged in such a manner that the low-pressure zone that is created behind each bead in the direction in which the fluid passage is formed does not impinge on the beads that follow.
  • the tube element may take a structure in which a plurality of bead rows which cross the fluid passage direction at a right angle are provided with the various bead rows that lie adjacent to one another being different in the areas where beads are not present and those areas where beads are not present in the aforementioned bead rows that lie adjacent to one another form a continuum.
  • the bead arrangement reduces the dead water regions and the passage resistance, thus eliminating stagnation by distributing the heat exchanging medium evenly over the entirety of the passage. As a result, heat exchanging efficiency is further improved due to the improvement in the area where beads are not formed.
  • the laminated heat exchanger 1 is an evaporator of, for example, the 4-pass type, in which fins 2 and tube elements 3 are alternately laminated over a plurality of rows.
  • Each tube element 3 is formed by bonding two formed plates 4, 4 at their peripheral edges and is provided with two tanks 5, 5 at one end on the upstream side of the airflow and the downstream side of the airflow. It is also provided with a heat exchanging medium passage 7 which lets heat exchanging medium travel from these tanks 5, 5 to the other end.
  • Each formed plate 4 is formed by press machining an aluminum plate with, as shown in Figure 2, two vessel-like distended portions for tank formation 8, 8 at one end and a distended portion for passage formation 9 formed as a continuation of the distended portions 8, 8.
  • the mounting indentation 11 for mounting the communicating pipe which is to be explained later, is provided between the distended portions for tank formation 8, 8 and at the other end of the formed plate 4 a projecting piece 12 (shown in Figure 1) is provided to prevent the fin 2 from falling off during assembly, before brazing.
  • Each distended portion for tank formation 8 swells out more than the distended portion for passage formation 9.
  • the projection 10 is bonded with its opposite projection when the formed plates 4 are bonded on their peripheral edges so that the projection 10 partitions the heat exchanging medium passage 7 except for the area close to the other end of the tube element 3, thus forming an overall U-
  • the tanks 5 of neighboring tube elements 3 are butted to one another at the distended portions for tank formation 8 of the respective formed plates 4 and they communicate with one another through the communicating holes 13 which are formed at the distended portions for tank formation 8, except for the blind-type tank 5a, which is located on one side at the approximate center in the direction of lamination.
  • the tube element 3a which is located at a specific position toward one side from the center, is not provided with the aforementioned mounting indentation 11 and one of its tank 5b on the side where the blind-type tank 5a is provided, is extended so that it will lie adjacent to the tank opposite.
  • This extended tank 5b is connected with the communicating pipe 15 that is mounted in the mounting indentation 11.
  • the intake/outlet port 16 is provided at one end of the heat exchanger in the direction of lamination which is furthest away from the extended tank 5b.
  • This intake/outlet port 16 is, in turn, provided with a connecting portion 17 for connecting an expansion valve, a communicating passage 18, which communicates between the connecting portion 17 and the tank on the side where the blind tank is provided, and a communicating passage 19 which is connected to the aforementioned communicating pipe 15.
  • heat exchanging medium flows in through one of the communicating passages, for example, communicating passage 19 connected to the intake/outlet port 16.
  • the heat exchanging medium that has flowed in travels into one portion of the tank 5, which is divided approximately half, on the side of the blind-type tank 5a via the communicating pipe 15 and the extended tank 5b, then it travels upwards through the heat exchanging medium passage 7 along the projection 10, makes a U-turn at the top of the projection 10 to make the trip downward and finally reaches the tank which is on the opposite side from the blind-type tank 5a. After that it moves horizontally to the another tank 5 which is divided approximately half.
  • the beads 20 are press formed as a part of the aforementioned formed plates 4.
  • a plurality of bead rows are formed in such a manner that they lie at a right angle to the direction of the flow of the heat exchanging medium which travels through the heat exchanging medium passage 7, and each bead row is provided with a plurality of beads 20 that are positioned at even intervals.
  • row n is constituted with four beads
  • row n+1 is constituted with five beads
  • the beads are positioned in bead rows that lie adjacent to one another in such a manner that the low-pressure zone that is created behind each bead in the direction in which the fluid passage is formed (the vertical direction in the figure) does not impinge on the following beads. All the beads in every other bead row are positioned in such a manner that they interleave with the low-pressure zones that are created behind the beads in the direction in which the fluid passage 7 is formed. Overall, the beads 20 are formed at a consistent density.
  • the beads 20 described above project out from the internal surface of the formed plate towards the inside of the fluid passage 7. They are bonded with beads of the adjacent formed plate to improve the heat exchanging efficiency of the heat exchanging medium which flows through the heat exchanging medium passage 7.
  • the tube element 3 if the area of the bottom portion of each bead, which is considered to begin at the point where the formed plate 4 starts to project out towards the inside of the fluid passage 7, (hereafter referred to as the bead size) is designated A, the spacing of the neighboring beads which are the closest to each other (hereafter referred to as the bead spacing) is designated B, the thickness of the portion of the tube element which constitutes the heat exchanging medium passage is designated H and the formed plate thickness is designated T, they fall within the following ranges; 2.0mm ⁇ A ⁇ 3.0mm, 3.5mm ⁇ B ⁇ 6.3mm, 1.9mm ⁇ H ⁇ 2.7mm, and 0.25mm ⁇ T ⁇ 0.47mm.
  • the passage resistance increases and as the bead size A decreases, the passage resistance also decreases.
  • the heat exchanging performance is relatively reduced.
  • the number of beads becomes high, increasing the passage resistance, and as the bead spacing B becomes large, the number of beads becomes smaller, relatively reducing the passage resistance but at the same time reducing the heat exchanging performance as well.
  • the wider the heat exchanging medium passage 7 can be made, which will improve the heat exchanging performance.
  • the plate thickness is made too small, problems related to strength and anti-corrosion characteristics will arise.
  • the heat exchanging medium passage 7 becomes narrower, increasing the passage resistance. All this means that, except for the formed plate thickness, the relationship between the heat exchanging performance and the passage resistance can be used as an index for evaluating the tube element 3.
  • This evaluation may be also made by assigning the heat exchanging performance/passage resistance as the axis of ordinates and each of the bead size, the bead spacing and the tube element thickness to the axis of abscissas, and these are shown in Figure 6.
  • the index heat exchanging performance/passage resistance
  • the index is set at 100 when the bead size is 2.5mm, the bead spacing is 4.8mm and the tube element thickness is 2.4mm.
  • the index becomes lower if the size is either smaller or larger than 2.5m, as shown in Figure 6 (a).
  • the bead size becomes larger, the passage resistance also becomes greater and if the bead size is increased to 3.8mm, which is common in the prior art, a good index cannot be achieved. Consequently, the upper limit of the bead size is set by using an index which is equivalent to the lower limit of the bead size or an index better than that, for reference, at A ⁇ 3.0mm.
  • the index becomes lower when the bead spacing is either smaller or larger than 4.8mm. All in all, a good index is achieved within the spacing range of 3.5mm - 6.3mm. Since the smaller B is, the more difficult machining becomes and, at the same time, the passage resistance is greatly increased, it is necessary to set B at 3.5mm or more. Preferably, it should be set at 3.8mm or more to allow some tolerance in machining. Also, although the larger B is, the smaller the passage resistance becomes, the heat exchanging performance will be reduced as well.
  • the upper limit for bead spacing is set by using an index which is equivalent to the lower limit value (3.5mm) of bead spacing or, an index better than that, at 6.3mm or less.
  • the upper limit for bead spacing is set by using an index which is equivalent to the lower limit value (3.8mm) of the bead spacing or, an index better than that, at 5.8mm or less.
  • the index for the tube element becomes lower if the thickness H is either smaller or larger than 2.4mm. Since the smaller H is, the more difficult machining becomes and, at the same time, the performance is reduced, it is necessary to set H at 1.9mm or more. Preferably, it should be set at 2.0mm or more, to allow some tolerance in machining. Also, it has been learned that the larger the thickness H is, the smaller the passage resistance becomes, and the heat exchanging efficiency will be reduced as well. Consequently, the upper limit for the thickness H is set by using the index which is equivalent to the lower limit value of the thickness or, an index better than that, at H ⁇ 2.7mm or, preferably H ⁇ 2.6.
  • the optimal plate thickness T it is necessary to set the optimal plate thickness T by taking into consideration the relationship between the strength and anticorrosion characteristics of the formed plate and the passage resistance. It is, therefore, necessary to set the lower limit at T ⁇ 0.25mm by taking into consideration the strength and anticorrosion and to set the upper limit at T ⁇ 0.47mm by taking into consideration the deterioration of heat exchanging performance caused by the increase in passage resistance.
  • a tube element in which the ranges stipulated above are obtained will be the best possible tube element considering and balancing the two requirements, i.e., an improvement in heat exchanging efficiency and a reduction in passage resistance. Furthermore, with such factors as strength and the like also taken into consideration, the tube element makes it possible to provide a more compact, light-weight heat exchanger compared to one which employs the tube elements of the prior art.
  • Figure 7 shows another example of the formed plate 4 (second embodiment) that constitutes the tube element 3.
  • the beads 20 are formed in a plurality of bead rows that cross the direction in which the heat exchanging medium passage is formed at a right angle, and the intervals at which beads are positioned are different between bead rows that lie adjacent to one another.
  • 3 beads are provided at equal intervals of L2 and in row n+2
  • in row n+3 three beads are provided at equal intervals L2 and so on.
  • bead rows in which beads are provided at equal intervals L1 and bead rows in which beads are provided at equal intervals L2 are formed alternately.
  • each interval L2 is twice the length of the interval L1.
  • All the beads in every other bead row are positioned in such a manner that they interleave with the low-pressure zones that are created behind the beads in the direction in which said fluid passage 7 is formed (the vertical direction in the figure).
  • they are positioned in such a manner that the bead which is closest to a given bead in an adjacent row lies at an angle of 30 degrees from that given bead to the direction in which the heat exchanging medium passage is formed.
  • a regular pattern of bead groups emerge when viewed in the direction of 30 degrees, in which beads are arranged at intervals a and intervals b alternately.
  • the formed plate 4 that constitutes the tube element 3 may take the structure shown in another embodiment (third embodiment) presented in Figure 8, in which areas with no beads 20 are present in different locations in bead rows that lie adjacent to one another that cross the direction in which the heat exchanging medium passage 7 is formed at a right angle. These areas in the bead rows that lie adjacent to one another where beads are not formed, connect to form a passage 21, in which beads are not present in a direction which is different from the direction in which the heat exchanging medium passage 7 is formed. In this embodiment, the areas in which the beads 20 are not formed connect with one another continuously in the direction which is at an angle of 30 degrees to the direction in which the heat exchanging medium passage 7 is formed, in contrast to the tube element in the prior art in which beads are formed consistently.
  • the number beads located in dead water regions is reduced, and areas where the passage resistance is small are created over the entirety of the heat exchanging medium passage 7 without reducing the heat exchanging efficiency.
  • the distribution of the heat exchanging medium to those areas with low passage resistance is promoted, thereby distributing the heat exchanging medium over the entirety of the tube element and avoiding stagnation.
  • an improvement in heat exchanging efficiency can be achieved.
  • the following tube elements were tested; the tube element of the type shown in Figure 2, in which beads are provided at a consistent density (hereafter referred to as type 1), the tube element in the second embodiment (hereafter referred to as type 2) and the tube element in the third embodiment (hereafter referred to as type 3).
  • a heating plate 22 was attached over the entirety of one of the surfaces of the distended portion for passage formation 9 with silicon adhesive, as shown in Figure 9.
  • adiabatic material 30 was placed over the whole assemblage and an AC power source was connected to the heating plate 22 to supply a consistent quantity of heat to the tube element evenly.
  • a specific quantity of tap water was supplied to the tube element via a 500mm-long intake pipe 23.
  • the tap water supplied via the intake pipe 23 was monitored on the flow meter 25 and the flow rate of the tap water was adjusted to 5cc/sec, 10cc/sec and 20cc/sec.
  • the surface temperature of the tube elements at those different flow rates was measured. The results are shown in the thermographic diagrams in Figs 10 - 12. Note that the values in Figures 10 - 12 indicate temperature readings (degrees Celsius).
  • the pressures at the intake and outlet are measured on the pressure gauge 33 through the intake static pressure hole 31 formed in the intake pipe 23 and the outlet static pressure hole 32 formed in the outlet pipe 24 to determine the water flow resistance (mmHg) in the tube element 4.
  • the results are shown in Table 2. 5 cc/sec 10 cc/sec 20 cc/sec Type 1 6.5 9.0 16.6 Type 2 7.5 8.5 13.0 Type 3 7.2 8.4 12.5
  • the average of the temperature differences (degrees Celsius) between the direction in which the fluid flows and the direction that crosses that direction at a right angle was measured with a group of thermocouples 29 provided at a plurality of specific locations (24 locations) on the surface of the tube element 4 (the surface on the opposite side from the side on which the heating plate is provided).
  • the temperature difference between the intake and the outlet indicates that the larger the difference is, the more actively heat exchange is performed and the results of our experiment show that the temperature difference is somewhat greater in type 2 and type 3 than in type 1, although not significantly. With type 1, the temperature difference is greater at flow rates of 5cc/sec and 20cc/sec compared with type 2.
  • water flow resistance As for water flow resistance, it was greater in both types 2 and 3 than in type 1 at 5cc/sec but it was smaller in both types 2 and 3 at 10 cc/sec and 20 cc/sec. Therefore, considering that the flow rate in an actual heat exchanger is normally approximately 10cc/sec, we can conclude that types 2 and 3 will have less water flow resistance. It was also noted that water flow resistance is smaller in type 3 than in type 2.
  • the data obtained through the experiments indicate that the heat exchanging characteristics of type 2 and type 3 are improved even though the number of beads in those types is smaller than that of type 1, and we can safely say that in the type 2 and type 3 tube elements, the number of beads in the dead water regions is reduced, thus realizing bead arrangements that make it possible to distribute heat exchanging medium over the entirety of the passage without stagnation more completely than in type 1.

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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)

Claims (9)

  1. Verdampfer (1), der eine Vielzahl von abwechselnd geschichteten Röhrenelementen (3) und Rippen (2) umfaßt, wobei jedes Röhrenelement aus einem Paar aneinanderstoßender, geformter Platten (4) besteht und jedes Röhrenelement umfaßt:
    einen Durchgangsabschnitt (9) mit einem ersten und einem zweiten Ende und einer Verbindungswand (10), die sich vom ersten Ende bis zu einer Position, die dem zweiten Ende benachbart ist, erstreckt, um einen U-förmigen Durchgang mit ersten bzw. zweiten Durchgangsschenkeln auf entgegengesetzten Seiten dieser Verbindungswand, und einen Verbindungsdurchgangsabschnitt zu definieren, der die ersten und zweiten Durchgangsschenkel verbindet und sich zwischen dem zweiten Ende des Durchgangsabschnitts und der Position der Verbindungswand befindet, die dem zweiten Ende des Durchgangsabschnitts benachbart ist,
    erste und zweite Reservoirabschnitte (5), die an dem ersten Ende des Durchgangsabschnitts bereitgestellt sind und mit den ersten bzw. zweiten Durchgangsschenkeln in Verbindung stehen, wobei die ersten und zweiten Reservoirabschnitte einen Abstand voneinander haben; wobei jede der geformten Platten (4) einer Vielzahl von Wülsten (20) aufweist, die in den U-förmigen Durchgang ragen, so daß die Wülste, die von einer der geformten Platten vorstehen, dem Ort der von der anderen geformten Platte vorstehenden Wülste entsprechen bzw. sie berühren, und wobei diese Wülste in eine Vielzahl von Wulstreihen angeordnet sind, die sich senkrecht zur Längsrichtung der Durchgangsschenkel erstrecken, wobei die Wülste in den Wulstreihen, die einander benachbart sind, so angeordnet sind, daß eine zueinander relative Überlappung in der Längsrichtung der Durchgangsschenkel vermieden wird, dadurch gekennzeichnet, daß die Breite A einer Basis jedes Wulstes und der Abstand B der Wülste die Beziehungen erfüllen:
       2,0 mm ≤ A ≤ 3,0 mm
       bzw. 3,5 mm ≤ B ≤ 6,3 mm.
  2. Verdampfer nach Anspruch 1, bei dem die Dicke H des Röhrenelements und die Plattendicke T jeder der geformten Platten (4) die Beziehungen erfüllen:
       1,9 mm ≤ H ≤ 2,7 mm
       bzw. 0,25 mm ≤ T ≤ 0,47 mm.
  3. Verdampfer nach Anspruch 1 oder 2, bei dem die Wülste (20) in jeder der Wulstreihen in gleichen Abständen angeordnet sind.
  4. Verdampfer nach Anspruch 1 oder 2, bei dem sich jeweils zwei einander in Längsrichtung der Durchgangsschenkel benachbart liegenden Wulstreihen bei verschiedenen Abständen befinden.
  5. Verdampfer nach einem der Ansprüche 1 bis 4 mit Abschnitten, die nicht mit den Wülsten (20) ausgebildet sind, und solche Abschnitte in jeweils zwei einander in Längsrichtung der Durchgangsschenkel benachbart liegenden Wulstreihen voneinander verschieden sind, wobei ein Abschnitt in einer der Wulstreihen und ein Abschnitt in einer anderen der Wulstreihen so ausgebildet sind, daß sie sich in der Längsrichtung teilweise überlappen.
  6. Verdampfer nach Anspruch 5, bei dem Abschnitte, in denen keine Wülste (20) bereitgestellt sind, ein Kontinuum in einer Richtung bilden, die einen Winkel von 30° zur Längsrichtung hat.
  7. Verdampfer nach einem der Ansprüche 1 bis 4, bei dem Wulstreihen, in denen Wülste (20) mit spezifischen Abständen bereitgestellt sind, und Wulstreihen, in denen Wülste (20) mit zweimal dem spezifischen Abstand bereitgestellt sind, abwechselnd ausgebildet sind.
  8. Verdampfer nach einem der Ansprüche 1 bis 4, bei dem ein Wulst (20) in einer Wulstreihe, die zu einem gegebenen Wulst (20) in einer benachbarten Reihe am nächsten ist, so angeordnet ist, daß er einen Winkel von 30° mit dem gegebenen Wulst zur Längsrichtung bildet.
  9. Verdampfer nach einem der Ansprüche 1 bis 8 mit einem Kühlmitteleinlaß (16) und einem Kühlmittelauslaß (16), bei dem ein Paar von Reservoirgruppen aus schichtenden Paaren von Reservoirabschnitten (5) des Röhrenelements (3) besteht, wobei eine Reservoirgruppe durch ein Blindreservoir (5a) in zwei Reservoiruntergruppen unterteilt ist, eine weitere der Reservoirgruppen mit zwei miteinander in Fluidverbindung stehenden Reservoiruntergruppen versehen ist, wobei die eine der Reservoiruntergruppen, die durch das Blindreservoir (5a) unterteilt ist, das weiter vom Kühlmitteleinlaß (16) und dem Kühlmittelauslaß (16) entfernt ist, ein Röhrenelement mit einem ausgedehnten Reservoir (5b) aufweist, der mit einem von Kühlmitteleinlaß und -auslaß (16) durch ein Verbindungsrohr (15) in Verbindung steht, das zwischen den Paaren von Reservoirabschnitten (5) der Röhrenelemente (3) zwischen dem Kühlmitteleinlaß und-auslaß (16) und dem Blindreservoir (5b) vorgesehen ist, und wobei einer von Kühlmitteleinlaß und -auslaß (16), das Verbindungsrohr (15), das ausgedehnte Reservoir (5b), die durch das Blindreservoir (5a), das sich vom Kühlmitteleinlaß und -auslaß (16) weiter entfernt befindet, unterteilte Reservoiruntergruppe, mit der Reservoiruntergruppe, die sich von dem Kühlmitteleinlaß und -auslaß (16) weiter entfernt befindet, in Verbindung stehende Durchgangsabschnitte (9) des Röhrenelements (3), die beiden miteinander in Fluidverbindung stehenden Reservoiruntergruppen, mit der Reservoiruntergruppe, die sich am nächsten beim Kühlmitteleinlaß und -auslaß (16) befindet, in Fluidverbindung stehende Durchgangsabschnitte (9) der Röhrenelemente (3), die sich am nächsten beim Kühlmitteleinlaß und -auslaß (16) befindende Reservoiruntergruppe und ein weiterer von Kühlmitteleinlaß und -auslaß (16) in Fluidverbindung in Serie verbunden sind.
EP19940307738 1993-10-22 1994-10-21 Rohrelement für einen Laminatwärmetauscher Expired - Lifetime EP0650024B1 (de)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP28763193 1993-10-22
JP287631/93 1993-10-22
JP300956/93 1993-11-05
JP5300956A JP3028452B2 (ja) 1993-11-05 1993-11-05 積層型熱交換器のチューブエレメント
JP5345389A JPH07167581A (ja) 1993-10-22 1993-12-21 積層型熱交換器のチューブエレメント
JP345389/93 1993-12-21

Publications (2)

Publication Number Publication Date
EP0650024A1 EP0650024A1 (de) 1995-04-26
EP0650024B1 true EP0650024B1 (de) 1998-09-09

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EP19940307738 Expired - Lifetime EP0650024B1 (de) 1993-10-22 1994-10-21 Rohrelement für einen Laminatwärmetauscher

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EP (1) EP0650024B1 (de)
KR (1) KR100228503B1 (de)
DE (1) DE69413173T2 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2783906B1 (fr) 1998-09-24 2000-12-15 Valeo Climatisation Echangeur de chaleur a plaques, notamment pour vehicule automobile
CN1121601C (zh) * 1998-10-15 2003-09-17 株式会社荏原制作所 板式热交换器
JP4175443B2 (ja) 1999-05-31 2008-11-05 三菱重工業株式会社 熱交換器
US6209629B1 (en) * 1999-07-09 2001-04-03 Visteon Global Technologies, Inc. Beaded plate for a heat exchanger and method of making same
JP3911574B2 (ja) * 2000-01-08 2007-05-09 漢拏空調株式会社 熱交換性能を向上させた積層型熱交換器用プレート及びこれを用いる熱交換器
KR100950714B1 (ko) * 2003-05-29 2010-03-31 한라공조주식회사 열교환기용 플레이트
FR2906020B1 (fr) * 2006-09-15 2008-11-14 Halla Climate Control Corp Plaque destinee a un echangeur de chaleur.
US7413003B2 (en) 2006-09-15 2008-08-19 Halla Climate Control Corporation Plate for heat exchanger
EP3015809B1 (de) * 2014-10-31 2019-07-31 Danfoss A/S Plattenwärmetauscher

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4800954A (en) * 1986-12-18 1989-01-31 Diesel Kiki Co., Ltd. Laminated heat exchanger
KR940010978B1 (ko) * 1988-08-12 1994-11-21 갈소니꾸 가부시끼가이샤 멀티플로우형의 열교환기
US5111878A (en) * 1991-07-01 1992-05-12 General Motors Corporation U-flow heat exchanger tubing with improved fluid flow distribution
US5125453A (en) * 1991-12-23 1992-06-30 Ford Motor Company Heat exchanger structure

Also Published As

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DE69413173T2 (de) 1999-06-02
KR100228503B1 (ko) 1999-11-01
EP0650024A1 (de) 1995-04-26
DE69413173D1 (de) 1998-10-15

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