EP0108377A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0108377A1
EP0108377A1 EP83110906A EP83110906A EP0108377A1 EP 0108377 A1 EP0108377 A1 EP 0108377A1 EP 83110906 A EP83110906 A EP 83110906A EP 83110906 A EP83110906 A EP 83110906A EP 0108377 A1 EP0108377 A1 EP 0108377A1
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EP
European Patent Office
Prior art keywords
flow path
communicating passage
plates
passage portions
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.)
Withdrawn
Application number
EP83110906A
Other languages
German (de)
English (en)
Inventor
Isao Takeshita
Yoshiaki Yamamoto
Seikan Ishigai
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co 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
Priority claimed from JP19410382A external-priority patent/JPS5984083A/ja
Priority claimed from JP21292182A external-priority patent/JPS59104095A/ja
Priority claimed from JP21435682A external-priority patent/JPS59104087A/ja
Priority claimed from JP2064183A external-priority patent/JPS59147990A/ja
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP0108377A1 publication Critical patent/EP0108377A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • F28D9/0031—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 conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media

Definitions

  • the present invention generally relates to heat exchangers for effecting heat exchange between two fluids and more particularly, to an improved construction of a heat exchanger for effecting heat exchange between two of gas, liquid, gas-liquid two-phase flow, etc.
  • the double pipe type heat exchangers have been most frequently used for effecting heat exchange between two liquids or between liquid and gas-liquid two-phase flow.
  • the known double pipe type heat exchanger provided with a double pipe including an outer pipe and an inner pipe inserted into the outer pipe, it has been generally so arranged that first and second fluids are caused to flow in the inner pipe and between the inner pipe and the outer pipe, respectively, and the double pipe is spirally wound so as to make the heat exchanger compact in size as shown in Fig. 1.
  • the know double pipe type heat exchanger has such inconveniences that, since portions associated with heat transfer are restricted to surfaces of the inner pipe but surfaces of the outer pipe are not associated with heat transfer, the heat exchanger becomes large in size and thus, requires a large amount of materials therefor.
  • a heat exchanger (referred to as a "spiral two-stack-pipe type heat exchanger", hereinbelow) having two pipes of a rectangular cross section stacked one on the other and wound spirally for effecting heat exchange between two fluids, it may be estimated that, if adjacent ones of the stacked pipes are thermally connected to each other completely, most of metallic wall surfaces of the stacked pipes are associated with heat transfer, so that heat is transferred form - upstream and downstream flow paths and thus, the spiral two-stack-pipe type heat exchanger can be made more compact and efficient than the double pipe type heat exchanger.
  • the double pipe is spirally wound only for ease of operation thereof.
  • the two pipes are required to be not only wound spirally but connected to each other thermally.
  • the two rectangular pipes stacked one on the other and wound spirally may provide improved heat transfer characteristics as described above, it is estimated that excellent heat transfer characteristics cannot be obtained as far as pipes are employed.
  • an essential object of the present invention is to provide an improved heat exchanger (referred to as a "spiral stack-plate type heat exchanger", hereinbelow) provided with two spiral passages and including a plurality of plates stacked integrally one on another and each formed with a flow path of a sufficiently flattened cross section, which is excellent in heat transfer characteristics, with substantial elimination of the disadvantages inherent in conventional heat exchangers of this kind.
  • a spiral stack-plate type heat exchanger hereinbelow
  • Another important object of the present invention is to provide an improved heat exchanger of the above described type which is simple in structure, highly reliable in actual use and suitable for mass production at low cost.
  • an improved heat exchanger including a plurality of plates of a substantially identical shape stacked one on another so as to effect heat exchange between at least first and second fluids, the improvement comprising: a plurality of flow paths for effecting the heat exchange, which are each formed on one flat face of each of said plates such that some of said flow paths and the other ones of said flow paths allow said first and second fluids to flow through said some of said flow paths in a first direction at corresponding positions of said some of said flow paths and through said other ones of said flow paths in a second direction at corresponding positions of said other ones of said flow paths, respectively; and at least first and second communicating passages for connecting, wholly or partially in series, said some of said flow paths to one another and said other ones of said flow paths to one another, respectively, which are formed on each of said plates, whereby at least first and second passages of spiral configurations for passing said first and second fluids therethrough, respectively are formed independently of each other in said heat exchanger.
  • a first flat plate having a first flow path formed therein and a second flat plate formed with a second flow path having a shape identical to that of the first flow path such that a communicating passage for connecting, in series, a terminal end of the first flow path to a starting end of the second flow path is formed on either one of the first and second plates and a third flat plate formed with a third flow path, which is interposed between the first and second plates, whereby first and second spiral passages for passing first and second fluids therethrough, respectively are formed.
  • the first and second fluids are caused to flow in first and second directions in the plates, respectively as viewed from a direction perpendicular to the plates, which is a characteristic of the spiral passages.
  • the plates are integrally stacked one on another as in the case of the known plate type heat exchanger such that the heat exchanger of the present invention has the above described structure, the passages can be flattened arbitrarily, it becomes possible to design the heat exchanger considerably unrestrictedly under given conditions such as its pressure loss, heat transfer characteristics, etc.
  • two kinds of plates are required to be prepared for each of fluids subjected to heat exchange.
  • first and second fluids are subjected to heat exchange
  • four kinds of first, second, third and fourth plates stacked one on another sequentially in this order and formed with first, second, third and fourth flow paths, respectively are employed such that the first and third flow paths allow the first fluid to flow therethrough, with the second and fourth flow paths allowing the second fluid to flow therethrough.
  • first and second, third and fourth plates stacked one on another sequentially in this order and formed with first, second, third and fourth flow paths, respectively are employed such that the first and third flow paths allow the first fluid to flow therethrough, with the second and fourth flow paths allowing the second fluid to flow therethrough.
  • the third plate relative positions of an inflow port and an outflow port of the third flow path are provided opposite to those of the first flow path of the first plate.
  • fourth plate relative positions of an inflow port and an outflow port of the fourth flow path are-provided opposite to those of the second flow path of the second plate.
  • first and second plates are stacked integrally one on the other alternately and formed with first and second flow paths, respectively are employed such that the first and second flow paths allow the first and second fluids to flow therethrough, respectively.
  • first and second flow paths allow the first and second fluids to flow therethrough, respectively.
  • an inlet and an outlet of the first flow paths are provided on the first plate, while an inlet and an outlet of the second flow paths are provided on the second plate.
  • a first communicating passage for the first fluid and a second communicating passage for the second fluid are, respectively, formed on the second and first plates, spiral first and second passages for the first and second fluid, respectively are formed.
  • Each of the plates is formed with a flow path and two communicating passages.
  • adjacent ones of the plates are sequentially deviated by an angle of (360/n) degrees, whereby spiral first and second passages for the first and second fluids, respectively are formed.
  • each of the plates is formed with a flow path for the first fluid and a bypass for the second fluid.
  • a shape of each of the plates, elongated portions of the flow path for effecting heat exchange between the first and second fluids, and inflow ports and outflow ports of the first and second fluids are so formed as to be diametrically symmetric with respect to an axis extending at right angles to a plane of each of the plates.
  • first plate A is formed with a groove or recess of a substantially circular shape acting as a first flow path 1A and with an elongated separating portion 6a for intercepting the first flow path lA, which radially extends from a central portion thereof to a peripheral circumferential wall 1A, thereof.
  • the separating portion 6A is formed with slots 2A and 3A extending into opposite side thereof in opposite directions parallel to each other such that the slot 2A is disposed radially outwardly of the slot 3A.
  • a through-hole 3A' is provided in the slot 3A, while a through-hole 4A is formed on the separating portion 6A so as to be disposed radially inwardly of the through-hole 3A' such that the through-hole 3A' is radially disposed between the slot 2A and the through-hole 4A.
  • the second plate B is formed with a second flow path 1B, a peripheral circumferential wall 1B I and a separating portion 6B.
  • a separating portion 6B On the separating portion 6B, two slots 5B and 4B and a through-hole 3B are formed so as to be disposed radially outwardly in this order.
  • a through-hole 5B' is provided in the slot 5B such that the slot 4B is radially disposed between the through-holes 3B and 5B'.
  • the third plate C is formed with a third flow path 1C, a peripheral circumferential wall 1C' and a separating portion 6C.
  • a through-hole 5C and two slots 3C and 2C are formed so as to be disposed radially outwardly in this order.
  • a through-hole 2C' is provided in the slot 2C such that the slot 3C is radially disposed between the through-holes 2C' and 5C.
  • the fourth plate D is formed with a fourth flow path 1D, a peripheral circumferential wall 1D' and a separating portion 6D.
  • a separating portion 6D On the separating portion 6D, two slots 5D and 4D and a through-hole 2D are formed so as to be disposed radially outwardly in this order.
  • a through-hole 4D' is provided in the slot 4D so as to be radially disposed between the through-hole 2D and the slot 5D.
  • first, second, third and fourth plates A, B, C and D are identical, in shape, to one another except for the separating portions 6A, 6B, 6C and 6D. It should be further noted that, when the first, second, third and fourth plates A, B, C and D are stacked one on another, the slot 2A and the through-holes 2C' and 2D are brought into alignment with one another, while the through-holes 3A' and 3B and the slot 3C are brought into alignment with one another.
  • first, second, third and fourth plates A, B, C and D i.e., a first set of first, second, third and fourth plates A 1 , B 1 , C 1 and D 1 and a second set of first, second, third and fourth plates A 2 , B 21 C 2 and D 2 are integrally stacked one on another sequentially in this order as shown in Fig. 5, the first plate A 1 , third plate C 1 , first plate A 2 and third plate C 2 are connected in series to one another so as to define a first passage Tl for the first fluid as shown in the solid lines in Fig. 5, while the second plate B 1 , fourth plate D 1 , second plate B 2 and fourth plate D 2 are connected in series to one another so as to define a second passage T2 for the second fluid as shown in the broken lines in Fig. 5.
  • the first passage Tl (solid lines 7 in Fig. 5) in the first plate A 2 extends from the slot 2A of the first plate A 2 to the through-hole 2D of the fourth plate D 1 and then, through the through-hole 2C' of the third plate C 1 into the third flow plate 1C (solid lines 9 in Fig. 5) of the third plate C 1 .
  • the first passage Tl extends from the slot 3C of the third plate C to the through-hole 3B of the second plate B and then, through the through-hole 3A' of the first plate A l into the first flow path 1A (solid lines 10 in Fig. 5) of the first plate A I .
  • the first passage Tl of a spiral configuration similar to that of the know spiral two-stack-pipe type heat exchanger shown in Fig. 2 is formed in the heat exchanger Kl.
  • the second passage T2 of a spiral configuration is formed in the heat exchanger Kl.
  • the heat exchanger Kl is of a counter flow type in which the first and second fluids flow in opposite directions at every location of the heat exchanger Kl.
  • FIGs. 6(a) to 6(c) there are shown two kinds of first and second plates a and b of a rectangular shape employed in a spiral stack-plate type heat exchanger K2 for effecting heat exchange between first and second fluids, according to a second embodiment of the present invention.
  • the first and second plates a and b are, respectively, formed with a first flow path lla for the first fluid and a second flow path llb for the second fluid.
  • the first plate a is formed with a groove of a substantially circular shape acting as the first flow path lla for the first fluid such that outer peripheral walls 11A, 11B, 11C and 11D are defined on the first plate a, with the outer peripheral walls 11A and 11C confronting the outer peripheral walls 11B and 11D, respectively. Since the first plate a is formed with a partition wall 12a for intercepting the first flow path lla, which extends from a central portion thereof to the outer peripheral wall 11B, the first flow path lla is formed into a C-shaped configuration.
  • communicating passage portions E 1 , E 2 , F 1 and F 2 for the first and second flow paths lla and llb are formed sequentially in this order in a direction extending from the outer peripheral wall 11C to the outer peripheral wall 11D such that the partition wall 12a is disposed between the communicating passage portions E 1 and E 2 .
  • through-holes El and F2 are provided in the communicating passage portions E 1 and F 2 , respectively such that the communicating passage portions E 1 and E 2 are brought into communication with the first flow path lla, with the communicating passage portions F 1 and F 2 in communication with each other being held out of communication with the first flow path lla.
  • the second plate b is formed with outer peripheral walls 11A', 11B', 11C' and 11D' and a partition wall 12b for intercepting the second flow path llb.
  • communicating passage portions E 1 ', E 2 ', F 1 ' and F 2 ' for the first and second flow paths lla and llb are formed sequentially in this order in a direction extending from the outer peripheral wall 11C' to the outer peripheral wall 11D' such that the partition wall 12b extends between the communicating passage portions F 1 ' and F 2 '.
  • through-holes E2' and F1' are provided in the communicating passage portions E 2 ' and F 1 ', respectively such that the communicating passage portions F 1 ' and F 2 ' are brought into communication with the second flow path llb, with the communicating passage portions E1' and E 2 ' in communication with each other being held out of communication with the second flow path llb.
  • the communicating passage portions E 1 , E 2 , F 1 and F 2 of the first plate a correspond, in position, to the communicating passage portions E 1 ', E 2 ', F 1 ' and F2' of the second plate b, respectively.
  • the first and second fluids flow in the first plate a in the clockwise direction as shown by the arrow in Fig. 6(a) and in the second plate b in the counterclockwise direction as shown by the arrow in Fig. 6(b), respectively.
  • the heat exchanger K2 functions in the same manner as the known spiral two-stack-pipe type heat exchanger shown in Fig. 2.
  • a first passage Ul of a spiral configuration for the first fluid extends in a downward direction shown by an arrow 13 and passes through the first flow path lla of an upper first plate a in the clockwise direction.
  • the first passage Ul extends from the through-hole El of the upper first plate a to the communicating passage portion E 1 ' of the second plate b interposed between the upper first plate a and a lower first plate a and then, through the through-hole E2' of the second plate b into the communicating passage portion E 2 of the lower first plate a disposed below the second plate b.
  • the first passage Ul extends through the through-hole E1 and further proceeds downwardly as shown by an arrow 14.
  • a second passage U2 of a spiral configuration for the second fluid extends in an upward direction shown by an arrow-15 and passes through the through-hole F2 to the communicating passage portion F 1 in the lower first plate a.
  • the second passage U2 passes through the second flow path llb in the counterclockwise direction.
  • the second passage U2 extends from the communicating passage portion F 2 ' of the second plate b into the through-hole F2 of the upper first plate a.
  • the second passage U2 proceeds from the communicating passage portion F1 of the upper first plate a upwardly as shown by an arrow 16.
  • the heat exchanger K2 is not necessarily required to be of such an arrangement.
  • the heat exchanger K2 By integrally stacking a plurality of the first and second plates a and b one on another, the heat exchanger K2 similar to the spiral two-stack-pipe type heat exchanger shown in Fig. 2 can be manufactured with much ease.
  • FIGs. 8(a) to 8(d) there are shown three kinds of first, second and third plates G, H and J of a rectangular shape employed in a spiral stack-plate type heat exchanger K3 for effecting heat exchanger among first, second and third fluids, according to a third embodiment of the present invention.
  • the first, second and third plates G, H and J are, respectively, formed with a first flow path 21G for the first fluid, a second flow path 21H for the second fluid and a third flow path 21J for the third fluid.
  • heat exchanger K3 correspond to the known spiral three-stack-pipe type heat exchanger shown in Fig. 3.
  • the first plate G is formed with a groove of a substantially circular shape acting as the first flow path 21G for the first fluid such that outer peripheral walls 21A, 21B, 21C and 21D are defined on the first plate G, with the outer peripheral walls 21A and 21C confronting the outer peripheral walls 21B and 21D, respectively.
  • communicating passage portions Gl, G2, Hl, H2, Jl and J2 for the first, second and third flow paths 21G, 21H and 21J are formed sequentially in this matter in a direction extending from the outer peripheral wall 21C to the outer peripheral wall 21D.
  • the first flow path 21G is formed into a C-shaped configuration. Furthermore, through-holes Gl, H2 and J2 are, respectively, provided in the communicating passage portions G 1 , H 2 and J 2 . Thus, the communicating passage portions G 1 and G 2 are brought into communication with the first flow path 21G as shown by the arrow in Fig. 8(a). Meanwhile, the communicating passage portions H 1 and H 2 in communication with each other and the communicating passage portions J and J 2 in communication with each other are held out of communication with each other and with the first flow path 21G.
  • the second plate H is formed with outer peripheral walls 21A', 21B', 21C' and 21D' and a partition wall 22H for intercepting the second flow path 21H.
  • communicating passage portions G 1 ', G 2 ', H 1 ', H 2 ' ' J 1 ' and J 2 ' for the first, second and third flow paths 21G, 21H and 21J are formed sequentially in this order in a direction extending from the outer peripheral wall 21C' to the outer peripheral wall 21D' such that the partition wall 22H extends between the communicating passage portions HI' and H2' up to the outer peripheral wall 21B'.
  • through-holes G2', H1' and J2' are provided in the communicating passage portions G 2 ', H 1 ' and J 2 ', respectively.
  • the communicating passage portions H1' and H2' are brought into communication with the second flow path 21H as shown by the arrow in Fig. 8(b).
  • the communicating passage portions G l ' and G 2 ' in communication with each other and the communicating passage portions J 1 ' and J 2 ' in communication with each other are held out of communication with each other and with the second flow path 21H.
  • the third plate J is formed with outer peripheral walls 21A' ', 21B' ', 21C' ' and 21D' ' and a partition wall 22J for intercepting the third flow path 21J.
  • communicating passage portions G 1 ' ', G 2 ' ' , H 1 ' ', H 2 ' ', J 1 ' ' and J 2 ' ' for the first, second and third flow paths 21G, 21H and 21J are formed sequentially in this order in a direction extending from the outer peripheral wall 21C' ' to the outer peripheral wall 21D' ' such that the partition wall 22J extends between the communicating passage portions J1' ' and J 2 " up to the outer peripheral wall 21B".
  • through-holes G2' ', H2' ' and J1' ' are provided in the communicating passage portions G 2 ' ', H 2 ' ' and J 1 ' ', respectively.
  • the communicating passage portions Jl" and J2" are brought into communication with the third flow path 21J as shown by the arrow in Fig. 8(c). Meanwhile, the communicating passage portions G 1 ' ' and G 2 " in communication with each other and the communicating passage portions H 1 ' ' and H 2 ' ' in communication with each other are held out of communication with each other and with the third flow path 21J.
  • the communicating passage portions G 1 , G 2 , H 1 , H 2 , J 1 and J 2 of the first plate G correspond, in position, to the communicating passage portions G 1 ', G 2 ', H 1 ', H 2 ', J 1 ' and J 2 ' of the second plate H and the communicating passage portions G 1 ' ', G 2 ' ', H 1 ' ', H 2 ' ', J l " and J 2 " of the third plate J, respectively.
  • the first flow path 21G of the first plate G of a first set is connected, through the communicating passage portions of the second and third plates H and J, in series to the first flow path 21G of the first plate G of a second set which is, in turn, connected in series to the first flow path 21G of the first plate G of a third set or more in the same manner as described above, whereby a first passage Vl of a spiral configuration for the first fluid is formed.
  • a second passage V2 of a spiral configuration for the second fluid is formed.
  • a third passage V3 of a spiral configuration for the third fluid is formed.
  • the first, second and third passages Vl, V2 and V3 can be formed variously.
  • a plate 30 of a circular shape employed in a spiral stack-plate type heat exchanger K4 for effecting heat exchange between first and second fluids according to a fourth embodiment of the present invention.
  • the plate 30 is formed with a groove of a substantially circular shape acting as a flow path 31.
  • the plate 30 further has communicating passage portions 32, 33 and 34 of an identical shape arranged circumferentially in this order and extending in radial directions thereof.
  • the communicating passage portion 32 is disposed at one end of the flow path 31. It is so arranged that the communicating passage portions 33 and 34 are, respectively, circumferentially deviated from the communicating passage portions 32 and 33 by a predetermined angle ⁇ . Furthermore, through-holes 33' and 34' are provided in the communicating passage portions 33 and 34, respectively.
  • first, second, third, fourth, fifth and sixth plates 30A, 30B, 30C, 30D, 30E and 30F which are, respectively, provided with flow paths 1M, 3N, 2M, 2N, 3M and 1N are stacked one on another sequentially in this order as shown in Fig. 13, the first fluid flows downwardly from an arrow 38 in solid lines into the flow path 1M of the first plate 30A and then, passes through the flow path 1M from the lefthand portion to the righthand portion. Subsequently, the first fluid flows through the communicating passage portion of the second plate 30B into the flow path 2M of the third plate 30C.
  • the first fluid After passing through the flow path 2M from the lefthand portion to the righthand portion, the first fluid flows through the communicating passage portion of the fourth plate 30D into the flow path 3M of the fifth plate 30 E . After passing through the flow path 3M from the lefthand portion to the righthand portion, the first fluid flows through the communicating passage portion of the sixth plate 30F and further proceeds downwardly as shown by an arrow 39 in sold lines, whereby a first passage Wl of a spiral shape for the first fluid is formed.
  • the second fluid flows upwardly from an arrow 40 in broken lines into the flow path 1N of the sixth plate 30F.
  • the second fluid flows through the communicating passage portion of the fifth plate 30E into the flow path 2N of the fourth plate 30D and then, passes through the flow path 2N from the righthand portion to the lefthand portion.
  • the second fluid flows through the communicating passage portion of the third plate 30C into the flow path 3N of the second plate 30B.
  • the second fluid After passing through the flow path 3N from the righthand portion to the lefthand portion, the second fluid flows through the communicating passage portion of the first plate 30A and further proceeds upwardly as shown by an arrow 41 in broken lines, whereby a second passage W2 of a spiral shape for the second fluid is formed.
  • the heat exchanger K4 corresponding to the known spiral two-stack-pipe type heat exchanger shown in Fig. 2 can be manufactured.
  • the plate 30 is of a circular shape, so that the positive integer n becomes infinity and thus, the angle e can be set at an arbitrary value.
  • the plate 60 of a rectangular shape is so formed as to be diametrically symmetric with respect to a point disposed at a center of the plate 60.
  • the plate 60 has a U-shaped heat exchange groove 48 extending sidewise in parallel with opposite sides thereof and an elongated bypass groove 47 extending in parallel with one end thereof between the one end and a base portion of the U-shaped heat exchange groove 48 such that two arm portions of the U-shaped heat exchange groove 48 extend towards the other end of the plate 60.
  • a through-hole 43 is formed at one end of the bypass groove 47 so as to be disposed adjacent to one side of the plate 60.
  • a through-hole 44 is formed at one end of one arm portion of the heat exchange groove 48 so as to be disposed adjacent to the other end of the plate 60 and the one side of the plate 60.
  • a point 45 which is symmetric to the point 43 with respect to the point 42 is provided at one end of the other arm portion of the heat exchange groove 48 so as to be disposed adjacent to the other end of the plate 60 and the other side of the plate 60, while a point 46 which is symmetric to the point 44 with respect to the point 42 is provided at the other end of the bypass groove 47.
  • the bypass groove 47 extends from the through-hole 43 to the point 46
  • the heat exchange groove 48 extends from the through-hole 44 to the point 45.
  • first, second, third and fourth plates 60P, 60Q, 60R and 60S are stacked one on another sequentially in this order by rotating the first, second, third and fourth plates 60P, 60Q, 60R and 60S about the point 42 through 180° relative to one another sequentially as shown in Fig.
  • the first fluid flows downwardly from an arrow 49 in chain lines to the point P45 of the first plate 60P and then, reaches the through-hole P44. After passing through the through-hole P44, the first fluid flows down to the point Q46 of the second plate 60Q and thereafter, reaches the through-hole Q43.
  • the first fluid After passing through the through-hole Q43, the first fluid flows down to the point R45 of the third plate 60R and subsequently, reaches the through-hole R 44. After passing through the through-hole R44, the first fluid flows down to the point S46 of the fourth plate 60S and then, reaches the through-hole S43. After passing through the through-hole S43, the first fluid further proceeds downwardly as shown by an arrow 50 in chain lines, whereby a downward first passage Xl of a counterclockwise spiral shape for the first fluid is formed.
  • the second fluid flows upwardly from an arrow 51 in chain lines into the through-hole S44 of the fourth plate 60S.
  • the second fluid After passing through the through-hole S44, the second fluid reaches the point S45 and then, passes through the through-hole R43 of the third plate 60R to the point R46.
  • the second fluid After passing through the through-hole Q44 of the second plate 60Q, the second fluid reaches the point Q45 and then, passes through the through-hole P43 of the first plate 60P to the point P45.
  • the second fluid further proceeds upwardly as shown by an arrow 52 in chain lines, whereby an upward second passage X2 of a clockwise spiral shape for the second fluid is formed.
  • the heat exchanger K5 is of a counter flow type in which the first and second passages Xl and X2 extend in opposite directions.
  • the heat exchanger for effecting heat exchange between two fluids can be manufactured with much ease.
  • the stack-plate type heat exchanger since a great portion of the metallic surfaces of the heat exchanger are used as the heat transfer area, a large heat transfer area can be obtained in a small space as compared with the double pipe type heat exchanger, so that the stack-plate type heat exchanger can be made compact in size and therefore, requires a small amount of materials for manufacture thereof.
  • a prior art double pipe type heat exchanger for effecting heat exchange between hot water and cold water is manufactured so as to have a flow rate of about 10 liters/min.
  • a length of an inner pipe of 5/8 inch in outside diameter and an outer pipe of 1 inch in outside diameter is set at 29.3 m on the assumption that the number of transfer unit (N.T.U.) of heat of the heat exchanger is 5.
  • the pressure losses in the inner pipe and the outer pipe reach 0.11 m aq./m and 0.13 m aq./m, respectively and, in overall length, 3.2 m aq. and 3.8 m aq., respectively.
  • the double pipe is spirally wound at a winding diameter of 300 mm
  • the double pipe is wound 31 times and is of 790 mm in height.
  • the flow passage is 3 mm deep and 100 mm wide, the pressure loss of the passage reaches 0.113 m aq./m.
  • the N.T.U. of heat of the heat exchanger is 5 as in the case of the above known double pipe type heat exchanger, the passage is of 10.6 m in length, which is equivalent to 36% of that of the double pipe of 29.3 m.
  • the total pressure loss of the heat exchanger reaches 1.2 m aq. lower than that of the above known double pipe type heat exchanger but may be substantially equal to that of the above known double pipe type heat exchanger in consideration of pressure losses of the communicating passage portions between adjacent ones of the stacked plates.
  • the heat exchanger is of 136 mm in overall height, which is only 17% of that of the double pipe. It will be readily seen from this example that the heat exchanger of the present invention is made remarkably compact in size.
  • the passages are formed in series with respect to the plates in that heat exchanger of the present invention, while the passages are usually formed in parallel with the plates in the prior art plate type heat exchanger. Accordingly, in the known plate type heat exchanger, since the flow velocity is small, the fluids are of laminar flow, so that the heat exchanger is required to be of a complicated structure for converting the laminar flow into turbulent flow or the depth of the flow paths is required to be reduced to an exceedingly small dimension smaller than 1 mm. Thus, the known plate type heat exchanger has such inconveniences that the heat exchanger is readily adversely affected by stain of the heat transfer areas and the passages are likely to be clogged.
  • the heat exchanger since the flow velocity is sufficiently large, the heat exchanger can be used in the range of turbulent flow.
  • the depth of the flow paths is not so excessively small, thus eliminating the possibility that the passages are clogged.
EP83110906A 1982-11-04 1983-11-02 Echangeur de chaleur Withdrawn EP0108377A1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP19410382A JPS5984083A (ja) 1982-11-04 1982-11-04 熱交換器
JP194103/82 1982-11-04
JP212921/82 1982-12-03
JP21292182A JPS59104095A (ja) 1982-12-03 1982-12-03 積層らせん状熱交換器
JP214356/82 1982-12-06
JP21435682A JPS59104087A (ja) 1982-12-06 1982-12-06 積層式熱交換器
JP20641/83 1983-02-10
JP2064183A JPS59147990A (ja) 1983-02-10 1983-02-10 積層式熱交換器

Publications (1)

Publication Number Publication Date
EP0108377A1 true EP0108377A1 (fr) 1984-05-16

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP83110906A Withdrawn EP0108377A1 (fr) 1982-11-04 1983-11-02 Echangeur de chaleur

Country Status (1)

Country Link
EP (1) EP0108377A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000253A (en) * 1988-03-31 1991-03-19 Roy Komarnicki Ventilating heat recovery system
WO1992013248A1 (fr) * 1991-01-18 1992-08-06 2S Airchangers Limited Echangeurs thermiques
WO2003093749A1 (fr) * 2002-05-03 2003-11-13 Dana Canada Corporation Echangeur de chaleur a passage forme par des brides emboitees
US7178581B2 (en) 2004-10-19 2007-02-20 Dana Canada Corporation Plate-type heat exchanger
US9746251B2 (en) 2012-10-22 2017-08-29 Alfa Laval Corporate Ab Plate heat exchanger plate and a plate heat exchanger
EP3438591A4 (fr) * 2016-03-31 2019-11-27 Sumitomo Precision Products Co., Ltd. Échangeur de chaleur de type à liaison par diffusion

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE78566C (de) * MASCHINENFABRIK GREVEN BROICH, Gn venbroich Wärmeaustauschapparat
FR995395A (fr) * 1945-02-23 1951-11-30 échangeur de température, pouvant être utilisé pour la pasteurisation du lait
US2677531A (en) * 1950-08-04 1954-05-04 Hock Sr Built-up, plate type heat exchanger having spiral flow
FR1529833A (fr) * 1967-05-08 1968-06-21 échangeur de chaleur du type à plaques empilées
FR2323119A1 (fr) * 1975-09-02 1977-04-01 Parca Norrahammar Ab Echangeurs de chaleur a plateaux, a circulation de fluide en spirale entre plateaux voisins
GB2019550A (en) * 1978-04-21 1979-10-31 Imi Marston Ltd Plate heat exchanger

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE78566C (de) * MASCHINENFABRIK GREVEN BROICH, Gn venbroich Wärmeaustauschapparat
FR995395A (fr) * 1945-02-23 1951-11-30 échangeur de température, pouvant être utilisé pour la pasteurisation du lait
US2677531A (en) * 1950-08-04 1954-05-04 Hock Sr Built-up, plate type heat exchanger having spiral flow
FR1529833A (fr) * 1967-05-08 1968-06-21 échangeur de chaleur du type à plaques empilées
FR2323119A1 (fr) * 1975-09-02 1977-04-01 Parca Norrahammar Ab Echangeurs de chaleur a plateaux, a circulation de fluide en spirale entre plateaux voisins
GB2019550A (en) * 1978-04-21 1979-10-31 Imi Marston Ltd Plate heat exchanger

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5000253A (en) * 1988-03-31 1991-03-19 Roy Komarnicki Ventilating heat recovery system
WO1992013248A1 (fr) * 1991-01-18 1992-08-06 2S Airchangers Limited Echangeurs thermiques
GB2269229A (en) * 1991-01-18 1994-02-02 2S Airchangers Limited Heat exchangers
GB2269229B (en) * 1991-01-18 1994-08-24 2S Airchangers Limited Heat exchangers
WO2003093749A1 (fr) * 2002-05-03 2003-11-13 Dana Canada Corporation Echangeur de chaleur a passage forme par des brides emboitees
US6863122B2 (en) 2002-05-03 2005-03-08 Dana Canada Corporation Heat exchanger with nested flange-formed passageway
CN100417906C (zh) * 2002-05-03 2008-09-10 达纳加拿大公司 带有嵌套凸缘形成的通道的热交换器
US7178581B2 (en) 2004-10-19 2007-02-20 Dana Canada Corporation Plate-type heat exchanger
US9746251B2 (en) 2012-10-22 2017-08-29 Alfa Laval Corporate Ab Plate heat exchanger plate and a plate heat exchanger
EP3438591A4 (fr) * 2016-03-31 2019-11-27 Sumitomo Precision Products Co., Ltd. Échangeur de chaleur de type à liaison par diffusion

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