JP2014222115A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent foreign substances from accumulating in a flow passage where a fluid flows in a heat exchanger.SOLUTION: In a heat exchanger 10, a first heat exchanger plate 16 and a second heat exchanger plate 18 are laminated and arranged, and gaps between layers are made to be a cooling medium flow passage 60 and a heating medium flow passage 62 alternately. At the first heat exchanger plate 16 and the second heat exchanger plate 18, a wave-type bent part is provided from an inlet end toward an outlet end of the flow passage, and a flow passage resistance is formed in the cooling medium flow passage 60 and a heating medium flow passage 62. Formation density of the bent part is sparse in the outlet end compared with the inlet end.

Description

  The present invention relates to a heat exchanger, and more particularly to a heat exchanger in which a plurality of heat transfer plates are stacked and a gap between each layer is alternately used as a heat medium channel and a refrigerant channel.

  Conventionally, a heat medium flow path through which a heat medium flows and a refrigerant flow path through which a refrigerant flows are alternately formed in gaps between layers of a plurality of stacked heat transfer plates, and the heat medium passes through the heat transfer plates. There is known a heat exchanger in which the refrigerant and the refrigerant exchange heat.

  As a technique related to the present invention, for example, in Patent Document 1, a plurality of first heat transfer plates and a plurality of second heat transfer plates are alternately stacked, and between the stacked heat transfer plates. The first flow path through which the first fluid flows and the second flow path through which the second fluid flow are alternately formed in the stacking direction so that the first fluid and the second fluid exchange heat via the heat transfer plate. A plate heat exchanger is disclosed.

JP 2011-137623 A

  In the heat exchanger, for example, when foreign matter such as rust caused by corrosion of a pipe through which the heat medium flows is mixed with the heat medium, the foreign material may accumulate on the downstream side of the heat medium flow path. In such a region where foreign matter is accumulated, the heat medium is excessively cooled by the retention of the heat medium. As a result, if the heat medium freezes and the volume of the heat medium increases, the heat transfer plate may crack.

  An object of the present invention is to provide a heat exchanger that can prevent the accumulation of foreign substances in a flow path through which a fluid flows.

  The heat exchanger according to the present invention is a heat exchanger in which a plurality of heat transfer plates are stacked and the gaps between the layers are alternately used as a heat medium flow path and a refrigerant flow path. Corrugated bent portions are provided from the inlet end to the outlet end of the road, and flow resistance is formed in each flow path. The formation density of the bent portions is sparser at the outlet end than at the inlet end. It is characterized by.

  Further, in the heat exchanger according to the present invention, the corrugated bent portion is a herringbone-shaped portion that is bent so that the ridgeline of the herringbone is axisymmetric on both sides of the symmetry axis. The herringbone-shaped part is preferably arranged so that the ridgeline of the herringbone is in point contact.

  Moreover, in the heat exchanger which concerns on this invention, it is preferable that the direction of the Sayaka along the surface direction of a herringbone shape part when a symmetrical axis | shaft is piled up becomes reverse direction in the laminated heat exchanger plate which opposes.

  According to the present invention, the heat transfer plate is formed such that the formation density of the bent portion is less sparse at the outlet end than at the inlet end. As a result, the flow path resistance is smaller on the downstream side than on the upstream side, so that foreign matter can easily flow on the downstream side. Therefore, it is possible to prevent the accumulation of foreign matters on the downstream side.

It is a figure which shows the heat exchanger of embodiment which concerns on this invention. It is a top view of the 1st heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention. It is a top view of the 2nd heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention. In the heat exchanger of the embodiment concerning the present invention, it is a fragmentary sectional view when the 1st heat exchanger plate and the 2nd heat exchanger plate are made to oppose. It is a top view of the 1st modification of the 1st heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention. It is a top view of the 1st modification of the 2nd heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention. It is a top view of the 2nd modification of the 1st heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention. It is a top view of the 2nd modification of the 2nd heat exchanger plate which constitutes a part of heat exchanger of an embodiment concerning the present invention.

  Embodiments according to the present invention will be described below in detail with reference to the drawings. Also, in the following, corresponding elements in all drawings are denoted by the same reference numerals, and redundant description is omitted.

  FIG. 1 is a diagram showing a plate-type heat exchanger 10. FIG. 2 is a plan view of the first heat transfer plate 16 constituting a part of the heat exchanger 10. FIG. 3 is a plan view of the second heat transfer plate 18 constituting a part of the heat exchanger 10. Fig.4 (a) is a fragmentary sectional view of the AA line (refer FIG. 2) when the 1st heat exchanger plate 16 and the 2nd heat exchanger plate 18 are made to oppose. FIG. 4B is a partial cross-sectional view taken along line BB (see FIG. 2) when the first heat transfer plate 16 and the second heat transfer plate 18 are opposed to each other.

  The heat exchanger 10 is configured by stacking and arranging the first heat transfer plate 16 and the second heat transfer plate 18 between the two frames 12 and 14 alternately. In the gap between the first heat transfer plate 16 and the second heat transfer plate 18, refrigerant flow paths 60 and heat medium flow paths 62 are alternately formed.

  In the first heat transfer plate 16, openings 28 to 34 for forming a refrigerant inlet passage 20 and outlet passage 22 and a heat medium inlet passage 24 and outlet passage 26 are formed at four corners. The second heat transfer plate 18 is also formed with openings 28 to 34 in the same manner as the first heat transfer plate 16.

  First, the arrangement relationship among the frames 12 and 14, the first heat transfer plate 16 and the second heat transfer plate 18 will be specifically described. A first plate 46 constituted by the first heat transfer plate 16 located on the most front side in FIG. 1 is joined to the frame 12 with seal members 47 sandwiched at four corners.

  Further, the second plate 48 constituted by the second heat transfer plate 18 is joined to the first plate 46 with the seal member 47 sandwiched between the opening 32 and the opening 34. Thereby, the ridge line of the cedar of the first plate 46 and the ridge line of the cedar of the second plate 48 are point-contacted at a plurality of locations, and the refrigerant flow path 60 is formed between the first plate 46 and the second plate 48, The refrigerant flowing in from the opening 28 can flow out of the opening 30 through the refrigerant flow path 60.

  Further, the third plate 50 constituted by the first heat transfer plate 16 is joined to the second plate 48 with the seal member 47 sandwiched between the opening 28 and the opening 30. As a result, the ridge line of the cedar of the second plate 48 and the ridge line of the cedar of the third plate 50 are in point contact at a plurality of locations, and the heat medium flow path 62 is formed between the second plate 48 and the third plate 50. The heat medium flowing in from the opening 32 can flow out of the opening 34 through the heat medium flow path 62.

  The fourth plate 52 configured by the second heat transfer plate 18 is joined to the third plate 50 with the seal member 47 interposed between the opening 32 and the opening 34. Thereby, the ridge line of the cedar of the third plate 50 and the ridge line of the cedar of the second plate 48 are point-contacted at a plurality of locations, and the refrigerant flow path 60 is formed between the third plate 50 and the fourth plate 52, The refrigerant flowing in from the opening 28 can flow out of the opening 30 through the refrigerant flow path 60.

  Thus, as shown in FIG. 1, each flow path in the order of the refrigerant flow path 60, the heat medium flow path 62, the refrigerant flow path 60, the heat medium flow path 62,... The first heat transfer plate 16 and the second heat transfer plate 18 are alternately overlapped so that 60 and 62 are formed, and these are integrally brazed.

  Pipes 64 to 70 are connected to the frame 12 on one side (the front side in FIG. 1) corresponding to the openings 28 to 34. A pipe 64 corresponding to the opening 28 is a refrigerant introduction pipe, a pipe 66 corresponding to the opening 30 is a refrigerant outlet pipe, a pipe 68 corresponding to the opening 32 is a heat medium introduction pipe, and a pipe 70 corresponding to the opening 34 is a heat medium outlet pipe. is there.

  Next, specific structures of the first heat transfer plate 16 and the second heat transfer plate 18 will be described. The first heat transfer plate 16 is formed with a bent portion from the inlet end toward the outlet end. This bent portion is bent so that peaks (thick line portions in FIG. 2) and valleys (thin line portions in FIG. 2) forming waves are alternately formed.

  The bent portion will be described in more detail. A downstream inclined portion 36 formed so that the extending direction of the peak portion and the valley portion is inclined downward as it goes in the right direction in FIG. 2, and the inclined portion is inclined upward. Thus, it forms a herringbone shape in which the upstream inclined portions 38 formed in this manner are alternately arranged.

  Here, when the 1st heat exchanger plate 16 is seen in the AA line cross section of FIG. 2, and the BB line cross section, the shape of the peak part and trough part shown by FIG. 4 (a) and FIG.4 (b) is shown. Is the wave shape of the first heat transfer plate 16. A V-shape or an inverted V-shape along the surface direction when the first heat transfer plate 16 is viewed on the plane shown in FIG. In this case, as shown in FIG. 2, the ridge line (thick line portion in FIG. 2) of the first heat transfer plate 16 is line symmetric on both sides of the symmetry axis 33.

  Also, as shown in FIG. 2, among the ridges of the cedars of the first heat transfer plate 16, the interval between the adjacent ridges is larger at the outlet end than the inlet end of the heat medium and the refrigerant. For example, the description will be made assuming that the interval between the ridge lines at the exit end is twice the interval between the ridge lines at the entrance end. As described above, when the interval between the ridge lines at the outlet end is larger than the interval between the ridge lines at the inlet end, the formation density of the bent portions of the first heat transfer plate 16 is sparser than that at the inlet end.

  On the other hand, as shown in FIG. 3, the second heat transfer plate 18 also has the refrigerant inlet passage 20 and the outlet passage 22 and the heat medium inlet passage 24 and the outlet passage 26 at the four corners, similarly to the first heat transfer plate 16. Are formed, and bent portions are formed from the inlet end toward the outlet end. The second heat transfer plate 18 is different from the first heat transfer plate 16 in the extending direction of the peaks and valleys.

  In the first heat transfer plate 16, as shown in FIG. 2, the herringbone shape is configured from the left end in the order of the downstream inclined portion 36 and the upstream inclined portion 38, whereas the second heat transfer plate 18. Then, as shown in FIG. 3, the herringbone shape is formed in the order of the upstream inclined portion 42 and the downstream inclined portion 44 from the left end.

  As shown in FIG. 3, among the ridges of the cedars of the second heat transfer plate 18 (thick line part in FIG. 3), the interval between the adjacent ridges is larger than that of the inlets of the heat medium and the refrigerant. In this example, it is assumed that the interval between the ridge lines at the outlet end is twice the interval between the ridge lines at the inlet end. Thus, also in the formation density of the bending part of the 2nd heat exchanger plate 18, an exit end is sparse compared with an entrance end.

  Here, the first heat transfer plate 16 and the second heat transfer plate 18 opposed to the first heat transfer plate 16 have the first heat transfer plate when the symmetry axis 33 and the symmetry axis 43 are overlapped. The direction of the cedar of the board 16 and the direction of the cedar of the second heat transfer board 18 are stacked so as to be opposite to each other.

  As described above, the formation density of the bent portions of the first heat transfer plate 16 and the second heat transfer plate 18 is sparse at the outlet end compared to the inlet end. Therefore, the number of grooves formed by overlapping the first heat transfer plate 16 and the second heat transfer plate 18 and constituting the refrigerant flow path 60 and the heat medium flow path 62 is the upstream side shown in FIG. Compared to FIG. 4, the downstream side shown in FIG.

And the height of the groove | channel formed by the 1st heat exchanger plate 16 and the 2nd heat exchanger plate 18 being piled up is set to the height of the upstream shown by Fig.4 (a), and FIG.4 (b). the downstream side of the height shown in When a _1, a relationship of a = a _1. The width of the groove, the width of the upstream and b shown in FIG. 4 (a), when the width of the downstream side shown in FIG. 4 (b) and b _1, spacing ridge adjacent as described above Since the downstream side is doubled compared to the upstream side, the relationship is 2 × b = b ₁ . As a result, the cross-sectional area of each groove is larger on the downstream side than on the upstream side. That is, the flow path resistance of the refrigerant flow path 60 and the heat medium flow path 62 is smaller on the downstream side than on the upstream side.

  Then, operation | movement of the heat exchanger 10 is demonstrated using FIGS. 1-4. The refrigerant flows through the refrigerant flow path 60 from the openings 28 through the refrigerant introduction pipes 64 and then is led out from the refrigerant outlet pipe 66 through the openings 30 as indicated by broken lines in FIG. On the other hand, the heat medium flows through the heat medium flow path 62 from each opening 32 through the heat medium introducing pipe 68 and then led out from the heat medium outlet pipe 70 through each opening 34 as indicated by the solid line in FIG. The

  In this way, the refrigerant and the heat medium flow through the refrigerant flow path 60 and the heat medium flow path 62, respectively, and heat exchange is performed between the refrigerant and the heat medium via the heat transfer plates 48 to 56. Since the refrigerant flow path 60 and the heat medium flow path 62 have flow path resistance as described above, and the refrigerant and the heat medium flow in a turbulent state, heat exchange between the refrigerant and the heat medium is performed. It is done efficiently.

  Here, it is assumed that foreign matter such as rust caused by corrosion of the piping of the heat medium introduction pipe 68 is mixed with the heat medium. Assume the problem of accumulating large foreign objects. In such a case, the heat exchanger 10 has an advantage that even if a large foreign substance flows easily because the flow path resistance is formed low on the downstream side of the heat medium flow path 62. Moreover, since the cross-sectional area of the groove | channel which comprises the heat-medium flow path 62 is larger on the downstream side compared with the upstream side, there exists an advantage that a foreign material cannot catch easily.

  In the heat exchanger 10, the bent portions of the first heat transfer plate 16 and the second heat transfer plate 18 have been described as having a herringbone shape. However, the formation density of the bent portions is larger at the outlet end than at the inlet end. Other shapes may be used as long as is sparse.

  For example, as shown in FIG. 5, the first heat transfer plate 16 a may have a stripe shape having an upstream inclined portion 65 formed to be inclined upward as it goes rightward. In this case, as shown in FIG. 6, the second heat transfer plate 18a facing the first heat transfer plate 16a has a downstream inclined portion 67 formed to be inclined downward as it goes to the right. It has a stripe shape. At this time, the interval between the ridge lines of the first heat transfer plate 16a and the second heat transfer plate 18a is larger on the downstream side than on the upstream side of the heat medium and the refrigerant, as shown in FIGS. As a result, the flow path resistance of the refrigerant flow path 60 and the heat medium flow path 62 is smaller on the downstream side than on the upstream side, so heat exchange using the first heat transfer plate 16 and the second heat transfer plate 18 is performed. The same effect as the container 10 is produced.

  In the above description, the first heat transfer plates 16 and 16a and the second heat transfer plates 18 and 18b have been described as increasing the interval between the ridge lines on the downstream side, but the inclination angle of the ridge lines with respect to the symmetry axes 33 and 43 is set. The downstream side may be larger than the upstream side. For example, as shown in FIG. 7, in the first heat transfer plate 16b, the acute angle formed by the ridge line with respect to the symmetry axis 33 is larger on the downstream side than on the upstream side. In the second heat transfer plate 18b facing the first heat transfer plate 16b, the acute angle formed by the ridge line with respect to the symmetry axis 43 is larger on the downstream side than on the upstream side, as shown in FIG. As a result, the flow path resistance of the refrigerant flow path 60 and the heat medium flow path 62 is smaller on the downstream side than on the upstream side, so heat exchange using the first heat transfer plate 16 and the second heat transfer plate 18 is performed. The same effect as the container 10 is produced.

  10 heat exchanger, 12, 14 frame, 16, 16a, 16b first heat transfer plate, 18, 18a, 18b second heat transfer plate, 20, 24 inlet passage, 22, 26 outlet passage, 28, 30, 32, 34 Opening, 33, 43 Axis of symmetry, 36 Downstream inclined portion, 38 Upstream inclined portion, 42 Upstream inclined portion, 44 Downstream inclined portion, 46 First plate, 47 Seal member, 48 Second plate, 50 Third Plate, 52 Fourth plate, 60 Refrigerant flow path, 62 Heat medium flow path, 64 Refrigerant introduction pipe, 65 Upstream inclined section, 66 Refrigerant outlet pipe, 67 Downstream inclined section, 68 Heat medium introduction pipe, 70 Heat medium outlet Plumbing.

Claims (3)

A heat exchanger in which a plurality of heat transfer plates are arranged in layers, and a gap between each layer is alternately used as a heat medium flow path and a refrigerant flow path,
Each heat transfer plate is provided with a corrugated bent portion from the inlet end to the outlet end of the flow path to form a flow resistance in each flow path,
The heat exchanger is characterized in that the formation density of the bent portion is sparser at the outlet end than at the inlet end. The heat exchanger according to claim 1,
The corrugated bent part is a herringbone-shaped part that is folded so that the ridgeline of Sayaka is line symmetric on both sides of the symmetry axis,
A heat exchanger characterized in that the herringbone-shaped portions of the opposed laminated heat transfer plates are arranged so that the ridgeline of Sayaka is in point contact. The heat exchanger according to claim 2,
A heat exchanger characterized in that, in the opposed laminated heat transfer plates, the direction of the herringbone along the surface direction of the herringbone shape portion when the symmetry axes are overlapped is reversed.

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