JP2013142485A - Plate type heat exchanger - Google Patents

Plate type heat exchanger Download PDF

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JP2013142485A
JP2013142485A JP2012001855A JP2012001855A JP2013142485A JP 2013142485 A JP2013142485 A JP 2013142485A JP 2012001855 A JP2012001855 A JP 2012001855A JP 2012001855 A JP2012001855 A JP 2012001855A JP 2013142485 A JP2013142485 A JP 2013142485A
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flow path
heat transfer
transfer plate
heat
plate
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JP5411304B2 (en
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Nobuo Tanaka
信雄 田中
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Hisaka Works Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a plate type heat exchanger which can be made compact without involving degradation in heat exchange performance.SOLUTION: The plate type heat exchanger is constructed in such a way that: first flow passages 1 causing a heating medium R to flow therethrough and second flow passages 2 causing a medium to be heat-exchanged H to flow therethrough are alternately formed, the first flow passages 1 and the second flow passages 2 being formed between each of a plurality of laminated heat transfer plates 10 and 20; inlets 13 and 23 and outlets 14 and 24 are formed in each of the heat transfer plates 10 and 20; and communication paths 31a and 31b for communicating the inlets 13 or the outlets 14 to cause the heating medium R to flow through the first flow passage 1, and communication paths 32a and 32b for communicating the inlets 23 or the outlets 24 to cause the medium to be heat-exchanged H to flow through the second flow passage 2 are provided. The heat transfer plate 10 includes a partition part 15 formed to change the flow passage width of the first flow passage so that the flow velocity of the heating medium R is higher on the outlet 14 side than on the inlet 13 side.

Description

本発明は、冷媒などの熱媒体と水などの被熱交換媒体とを熱交換するための蒸発器として用いられるプレート式熱交換器に関し、詳しくは、伝熱プレートを境にして熱媒体を流通させる第１流路と、被熱交換媒体を流通させる第２流路とが交互に形成されたプレート式熱交換器に関する。   The present invention relates to a plate heat exchanger used as an evaporator for exchanging heat between a heat medium such as a refrigerant and a heat exchange medium such as water, and more specifically, the heat medium is circulated with a heat transfer plate as a boundary. The present invention relates to a plate heat exchanger in which first flow paths to be performed and second flow paths for circulating a heat exchange medium are alternately formed.

例えば蒸発器として用いられるプレート式熱交換器にあっては、図３示すように、複数枚の長方形状の伝熱プレート１１０，１１０，…が鉛直姿勢で積層されている。そして、この伝熱プレート１１０と伝熱プレート１１０との間に第１流路１０１と第２流路１０２とが交互に形成されている。そして、第１流路１０１に液体状態又は気液混合状態の熱媒体（冷媒）Ｒが流通し、第２流路１０２に被熱交換媒体（被冷却流体）Ｈが流通することで、熱媒体Ｒと被熱交換媒体Ｈとが熱交換される。   For example, in a plate heat exchanger used as an evaporator, a plurality of rectangular heat transfer plates 110, 110,... Are stacked in a vertical posture as shown in FIG. The first flow path 101 and the second flow path 102 are alternately formed between the heat transfer plate 110 and the heat transfer plate 110. Then, a heat medium (refrigerant) R in a liquid state or a gas-liquid mixed state flows through the first flow path 101 and a heat exchange medium (cooled fluid) H flows through the second flow path 102, whereby the heat medium Heat exchange is performed between R and the heat exchange medium H.

そして、伝熱プレート１１０の四隅には、流体の出入口となる通路孔１１１〜１１４が設けられている。また、伝熱プレート１１０の中間部には、伝熱部（採番せず）が設けられている。また、各伝熱プレート１１０間にガスケット１２０が装着されることで、例えば一方側の上，下の通路孔１１１，１１３と第１流路１０１とが連通し、かつ、他方側の上，下の通路孔１１２，１１４が第１流路１０１に開口しないように、あるいは、その逆になるようにされている。   And in the four corners of the heat transfer plate 110, passage holes 111 to 114 serving as fluid inlets and outlets are provided. In addition, a heat transfer portion (not numbered) is provided at an intermediate portion of the heat transfer plate 110. Further, by mounting the gasket 120 between the heat transfer plates 110, for example, the upper and lower passage holes 111 and 113 on one side communicate with the first flow path 101, and the upper and lower sides on the other side. These passage holes 112 and 114 are configured not to open to the first flow path 101 or vice versa.

そして、各伝熱プレート１１０には、複数の凸条及び凹条（ともに採番せず）によって波板状に形成されている。また、隣り合う伝熱プレート１１０の凸条同士が交差衝合し、各凹条で第１流路１０１又は第２流路１０２が形成されている。   Each heat transfer plate 110 is formed in a corrugated shape by a plurality of ridges and ridges (both not numbered). Further, the ridges of the adjacent heat transfer plates 110 intersect each other, and the first flow path 101 or the second flow path 102 is formed by the respective ridges.

しかし、このようなプレート式熱交換器にあっては、熱交換率を向上させるため、第１流路１０１内の熱媒体Ｒの流速が高められると、特に第１流路１０１の下流（出口通路孔）側において、熱媒体Ｒの圧力損失が適正範囲外となるほど過大になる。逆に、第１流路１０１内で流通する熱媒体Ｒが低速で流通すると、熱媒体Ｒの流量が過少になることから熱交換効率の向上を図ることができない。   However, in such a plate-type heat exchanger, in order to improve the heat exchange rate, when the flow rate of the heat medium R in the first flow path 101 is increased, the downstream (outlet) of the first flow path 101 in particular. On the side of the passage hole), the pressure loss of the heat medium R becomes excessive as it falls outside the proper range. Conversely, when the heat medium R flowing in the first flow path 101 flows at a low speed, the flow rate of the heat medium R becomes too small to improve the heat exchange efficiency.

そこで、圧力損失を適正な範囲内に止めつつ熱媒体Ｒの流速を高めることで、熱交換性能を向上させることができるようにしたプレート式熱交換器が特許文献１に記載されている。   Therefore, Patent Document 1 discloses a plate heat exchanger that can improve the heat exchange performance by increasing the flow rate of the heat medium R while keeping the pressure loss within an appropriate range.

このプレート式熱交換器は、各第１流路の下流側の断面積及び第２流路の下流側の断面積が上流側の断面積よりも広くなるように、各伝熱プレートの凹条の所定箇所に膨出部が形成されている。こうすることにより、熱媒体Ｒは、上流側において流速の低下が抑制され、下流側において流速の増大が抑制される。したがって、このプレート式熱交換器にあっては、熱媒体Ｒの上流側では境界伝熱係数が大きくされ、下流側では圧力損失が大きくならないようにされていることで、熱交換性能を高めることができるものとなっている。   The plate-type heat exchanger is configured so that the downstream cross-sectional area of each first flow path and the downstream cross-sectional area of the second flow path are wider than the upstream cross-sectional area. A bulging portion is formed at a predetermined position. By doing so, the heat medium R is suppressed from decreasing in flow rate on the upstream side and suppressed in increasing flow rate on the downstream side. Therefore, in this plate heat exchanger, the heat transfer performance is improved by increasing the boundary heat transfer coefficient on the upstream side of the heat medium R and preventing the pressure loss from increasing on the downstream side. It is possible to do.

特開２００５−３２６０７４号公報JP 2005-326074 A

特許文献１に記載されたプレート式熱交換器は、熱媒体が冷媒Ｒである蒸発器として用いられる。冷媒Ｒは、第１流路の上流側において気液２相状態で流れ、被熱媒体と熱交換された第１流路の下流側で気体となる。このようなプレート式熱交換器にあっては、小型化を図るため、伝熱プレートが短くされると、所期の熱交換係数を維持すべく、伝熱面積の減少を伝熱プレートの増加によって補わなければならない。しかし、伝熱プレートが増加すると、熱媒体Ｒ及び被熱交換媒体Ｈの流路数が増え、流速が低下して熱交換性能が低下してしまうことがある。   The plate heat exchanger described in Patent Document 1 is used as an evaporator whose heat medium is the refrigerant R. The refrigerant R flows in a gas-liquid two-phase state on the upstream side of the first flow path, and becomes a gas on the downstream side of the first flow path that is heat-exchanged with the heat-receiving medium. In such a plate heat exchanger, if the heat transfer plate is shortened for the purpose of miniaturization, the heat transfer area is reduced by increasing the heat transfer plate in order to maintain the desired heat exchange coefficient. I have to make up. However, when the number of heat transfer plates increases, the number of flow paths of the heat medium R and the heat exchange medium H may increase, and the flow rate may decrease and the heat exchange performance may deteriorate.

そこで、本発明は、熱交換性能が低下することなく、小型化を図ることができるようにしたプレート式熱交換器を提供することを課題とする。   Then, this invention makes it a subject to provide the plate type heat exchanger which enabled it to achieve size reduction, without the heat exchange performance falling.

本発明に係るプレート式熱交換器は、積層された複数の伝熱プレートのそれぞれを境にして熱媒体を流通させる第１流路と被熱交換媒体を流通させる第２流路とが交互に形成され、各伝熱プレートに流入孔及び流出孔が形成され、熱媒体が第２流路内に流入することなく第１流路内を流通するように前記流入孔又は流出孔を連通させる連通路と、被熱交換媒体が第１流路内に流入することなく第２流路内を流通するように前記流入孔又は流出孔を連通させる連通路とが設けられたプレート式熱交換器において、前記第１流路の流路幅を前記流入孔側よりも流出孔側で広くなるようにする仕切部が伝熱プレートに設けられたことを特徴としている。   In the plate heat exchanger according to the present invention, the first flow path for circulating the heat medium and the second flow path for circulating the heat exchange medium alternately with each of the plurality of stacked heat transfer plates as a boundary. In each of the heat transfer plates, an inflow hole and an outflow hole are formed. In a plate heat exchanger provided with a passage and a communication passage that connects the inflow hole or the outflow hole so that the heat exchange medium flows through the second flow path without flowing into the first flow path The heat transfer plate is provided with a partitioning portion that makes the flow path width of the first flow path wider on the outflow hole side than on the inflow hole side.

このプレート式熱交換器によれば、第１流路内を流通する熱媒体が例えば冷媒であると、冷媒は気化して流出孔側で体積が増大するものの、伝熱プレートに設けられた仕切部によって第１流路の流路幅が流入孔側よりも流出孔側で広くされていることにより、流出孔側の流速は抑制され、圧力損失も抑制することができる。一方、流入孔側における冷媒は、流速の低下が抑制されるので、熱交換の効率が低下しにくいようにすることができる。したがって、このプレート式熱交換器は、小型化しても、熱交換性能が低下しないようにすることができる。   According to this plate heat exchanger, when the heat medium flowing through the first flow path is, for example, a refrigerant, the refrigerant evaporates and the volume increases on the outflow hole side, but the partition provided on the heat transfer plate By making the flow path width of the first flow path wider on the outflow hole side than on the inflow hole side by the portion, the flow velocity on the outflow hole side is suppressed, and the pressure loss can also be suppressed. On the other hand, the refrigerant on the inflow hole side is prevented from lowering the flow velocity, so that the efficiency of heat exchange can hardly be reduced. Therefore, even if this plate type heat exchanger is reduced in size, heat exchange performance can be prevented from deteriorating.

また、前記本発明に係るプレート式熱交換器において、前記伝熱プレートは一対の側部と一対の端部とを有する四角形状に形成され、前記第１流路の流入孔が伝熱プレートの一方の側部の中間部ないし前記一方の端部側に形成され、前記第１流路の流出孔が伝熱プレートの一方の側部と一方の端部との交点である隅部に形成され、前記仕切部が流入孔から伝熱プレートの他方の端部側に向けて設けられ、第１流路が伝熱プレートの他方の端部側で迂回するように形成されていることが好ましい。   In the plate heat exchanger according to the present invention, the heat transfer plate is formed in a quadrangular shape having a pair of side portions and a pair of end portions, and the inflow hole of the first flow path is formed of the heat transfer plate. An intermediate part of one side part or the one end part side is formed, and the outflow hole of the first flow path is formed at a corner which is an intersection of one side part and one end part of the heat transfer plate. Preferably, the partition portion is provided from the inflow hole toward the other end portion side of the heat transfer plate, and the first flow path is formed so as to bypass the other end portion side of the heat transfer plate.

このプレート式熱交換器によれば、伝熱プレートの中間部ないし一方の端部側に形成された流入孔から第１流路内に熱媒体が流れ込み、この熱媒体は、伝熱プレートの一方の側部と仕切部との間を他方の端部の方へ流れ、他方の端部側で迂回して、伝熱プレートの他方の側部と仕切部との間を一方の端部の方へ流れ、流出孔から排出される。   According to this plate type heat exchanger, the heat medium flows into the first flow path from the inflow hole formed in the middle part or one end side of the heat transfer plate. Between the side portion of the heat transfer plate and the partition portion toward the other end portion, bypassing the other end portion side, and between the other side portion of the heat transfer plate and the partition portion toward the one end portion. And discharged from the outflow hole.

また、前記本発明に係るプレート式熱交換器において、前記仕切部は、前記第１流路の流路幅が流入孔側から流出孔側へ次第に広くなるように、前記流入孔から伝熱プレートの他方の端部の中間部の方に向けられていることが好ましい。   Further, in the plate heat exchanger according to the present invention, the partition portion includes a heat transfer plate extending from the inflow hole so that the width of the first flow path gradually increases from the inflow hole side to the outflow hole side. It is preferable that it is directed toward the middle portion of the other end portion.

このプレート式熱交換器によれば、第１流路の流路幅が流入孔側から流出孔側へ次第に広くなるように、仕切部が流入孔から伝熱プレートの他方の端部の中間部の方に向けられていることにより、熱媒体が第１流路内をスムーズに流通するようにすることができる。   According to this plate-type heat exchanger, the partition portion is an intermediate portion between the inlet hole and the other end of the heat transfer plate so that the channel width of the first channel gradually increases from the inlet hole side to the outlet hole side. By being directed to this direction, the heat medium can smoothly flow through the first flow path.

また、前記本発明に係るプレート式熱交換器において、前記第２流路の流入孔が伝熱プレートの他方の側部と一方の端部との交点である隅部に形成され、前記第２流路の流出孔が伝熱プレートの他方の側部の中間部に形成され、被熱交換媒体が迂回して流通するように誘導する仕切部が第２流路の流出孔から伝熱プレートの他方の端部側に向けて設けられていることが好ましい。   In the plate heat exchanger according to the present invention, the inflow hole of the second flow path is formed at a corner that is an intersection of the other side portion and one end portion of the heat transfer plate, An outflow hole of the flow path is formed in an intermediate portion of the other side portion of the heat transfer plate, and a partition portion that guides the heat exchange medium to bypass and flows from the outflow hole of the second flow path to the heat transfer plate. It is preferable that it is provided toward the other end side.

このプレート式熱交換器によれば、第１流路の流入孔が伝熱プレートの一方の側部の中間部ないし一方の端部寄りに形成され、第２の流路の流入孔が伝熱プレートの他方の側部と一方の端部との交点である隅部に形成されていることにより、熱媒体と被熱交換媒体とは伝熱プレートの一方の側部側で並向流となるため、圧力損失によって熱媒体が流入孔側で温度上昇したとしても、大きな温度差を確保して、効率的に熱交換することができる。   According to this plate heat exchanger, the inflow hole of the first flow path is formed near the middle part or one end of one side of the heat transfer plate, and the inflow hole of the second flow path is heat transfer. By being formed at the corner that is the intersection of the other side of the plate and the one end, the heat medium and the heat exchange medium become parallel flow on one side of the heat transfer plate. For this reason, even if the temperature of the heat medium rises on the inflow hole side due to pressure loss, a large temperature difference can be secured and heat exchange can be performed efficiently.

そして、第１流路内の熱媒体は、仕切部によって伝熱プレートの他方の端部側で迂回して伝熱プレートの一方の端部の方に流れ、第２流路内の被熱交換媒体は、伝熱プレートの一方の端部に設けられた流入孔から他方の端部の方へ仕切部に誘導されて流通するため、両媒体は伝熱プレートの他方の側部側で対向流となり、温度差を確保することができる。したがって、熱媒体が冷媒であれば、完全に蒸発させた上で、過熱度を得ることができる。   Then, the heat medium in the first flow path is detoured on the other end side of the heat transfer plate by the partition and flows toward one end of the heat transfer plate, and heat exchange in the second flow path is performed. Since the medium is guided and circulated by the partition from the inflow hole provided at one end of the heat transfer plate toward the other end, the two media face each other on the other side of the heat transfer plate. Thus, a temperature difference can be secured. Therefore, if the heat medium is a refrigerant, the degree of superheat can be obtained after completely evaporating.

また、第１伝熱プレートと第２伝熱プレートとが交互に積層され、前記第１流路の流路幅を変化させる仕切部が第１伝熱プレートの表面から突出するように設けられ、前記第２の流路を迂回させる仕切部が同じく第１伝熱プレートの裏面から突出するように設けられていることが好ましい。   Further, the first heat transfer plate and the second heat transfer plate are alternately stacked, and a partition portion that changes the flow path width of the first flow path is provided so as to protrude from the surface of the first heat transfer plate, It is preferable that a partition portion for bypassing the second flow path is also provided so as to protrude from the back surface of the first heat transfer plate.

このプレート式熱交換器によれば、２種類の伝熱プレートによって前記のように作用機能するプレート式熱交換器を組み立てることができるため、プレート式熱交換器自体が小型化、簡素化され、したがって、製造設備も小型化、簡素化することができる。   According to this plate type heat exchanger, since the plate type heat exchanger that functions as described above can be assembled by two types of heat transfer plates, the plate type heat exchanger itself is downsized and simplified, Therefore, the manufacturing equipment can also be reduced in size and simplified.

本発明によれば、第１流路の流路幅を流入孔側よりも流出孔側で広くなるようにする仕切部を設けたプレート式熱交換器を提供することができ、このプレート式熱交換器は、熱交換性能が低下することなく、小型化を図ることができる。   According to the present invention, it is possible to provide a plate-type heat exchanger provided with a partition portion that makes the flow path width of the first flow path wider on the outflow hole side than on the inflow hole side. The exchanger can be reduced in size without deteriorating the heat exchange performance.

本発明に係るプレート式熱交換器の一実施形態であって、要部を示す概略分解斜視図である。It is one Embodiment of the plate type heat exchanger which concerns on this invention, Comprising: It is a schematic exploded perspective view which shows the principal part. 本発明に係るプレート式熱交換器の一実施形態であって、（ａ）は一方の伝熱プレートを示す正面図、（ｂ）は他方の伝熱プレートを示す正面図である。It is one Embodiment of the plate type heat exchanger which concerns on this invention, Comprising: (a) is a front view which shows one heat-transfer plate, (b) is a front view which shows the other heat-transfer plate. 従来のプレート式熱交換器の要部を示す概略分解斜視図である。It is a general | schematic disassembled perspective view which shows the principal part of the conventional plate type heat exchanger.

本発明に係るプレート式熱交換器の一実施形態について図１及び図２を参照しながら説明する。このプレート式熱交換器は、熱媒体として冷媒Ｒを使用し、被熱交換媒体として被冷却流体Ｈを使用する蒸発器として用いられる場合を例にして説明する。   An embodiment of a plate heat exchanger according to the present invention will be described with reference to FIGS. 1 and 2. This plate-type heat exchanger will be described by taking as an example a case where the refrigerant R is used as a heat medium and a cooled fluid H is used as a heat exchange medium.

この実施形態のプレート式熱交換器は、図１及び図２に示すように、四角形状、さらに具体的には長方形状の第１伝熱プレート１０と第２伝熱プレート２０とが鉛直姿勢で交互積層されている。各伝熱プレート１０，２０を境にして、両伝熱プレート１０，２０の外周縁を囲むガスケット（図示せず）によって第１流路１と第２流路２とが交互に形成されている。第１流路１内には冷媒Ｒが流され、第２流路２内には被冷却流体Ｈが流される。   As shown in FIGS. 1 and 2, the plate type heat exchanger of this embodiment has a rectangular shape, more specifically, a rectangular first heat transfer plate 10 and a second heat transfer plate 20 in a vertical posture. They are stacked alternately. The first flow path 1 and the second flow path 2 are alternately formed by gaskets (not shown) surrounding the outer peripheral edges of the heat transfer plates 10 and 20 with the heat transfer plates 10 and 20 as a boundary. . The refrigerant R flows in the first flow path 1, and the cooled fluid H flows in the second flow path 2.

各伝熱プレート１０，２０は、複数の凸条１１，２１及び凹条１２，２２（図１には図示せず）よって波板状に形成されている。そして、隣り合う第１，第２伝熱プレート１０，２０の凸条１１，２１同士が交差衝合し、各凹条１２，２２内を冷媒Ｒ又は被冷却流体Ｈが流通する。また、凸条１１，２１及び凹条１２，２２は、いわゆるヘリンボーンタイプと称される形状で基本的に形成されている。   Each of the heat transfer plates 10 and 20 is formed in a corrugated plate shape by a plurality of ridges 11 and 21 and ridges 12 and 22 (not shown in FIG. 1). Then, the ridges 11 and 21 of the adjacent first and second heat transfer plates 10 and 20 cross each other, and the refrigerant R or the fluid to be cooled H flows through the respective ridges 12 and 22. The ridges 11 and 21 and the ridges 12 and 22 are basically formed in a so-called herringbone type shape.

すなわち、第１伝熱プレート１０の凸条１１及び凹条１２は、頂部が一方の端部（ここでは上端部）を向くようにΛ字状に形成されている。ただし、一方の端部では、端部と平行に凸条１１，２１及び凹条１２，２２が形成されている。また、第２伝熱プレート２０の凸条２１及び凹条２２は、頂部が他方の端部（ここでは下端部）２０ｄを向くようにＶ字状に形成されている。ただし、他方の端部２０ｄでは、端部と平行に凸条２１及び凹条２２が形成されている。   In other words, the ridges 11 and the ridges 12 of the first heat transfer plate 10 are formed in a Λ shape so that the top faces one end (here, the upper end). However, at one end, ridges 11 and 21 and recesses 12 and 22 are formed in parallel with the end. Further, the ridges 21 and the ridges 22 of the second heat transfer plate 20 are formed in a V shape so that the top part faces the other end part (here, the lower end part) 20d. However, in the other end portion 20d, the ridges 21 and the ridges 22 are formed in parallel with the end portions.

そして、第１伝熱プレート１０と第２伝熱プレート２０とには、流入孔１３，２３及び流出孔１４，２４が形成され、この流入孔１３，２３及び流出孔１４，２４を囲むようにガスケット３０が両伝熱プレート１０，２０に装着され、あるいは、装着されないことで、隣り合っている第１流路１の流入孔１３，１３，…同士を連通させ、また、流出孔１４，１４，…同士を連通させる連通路３１ａ，３１ｂが設けられ、そして、隣り合っている第２流路２の流入孔２３，２３，…同士を連通させ、また、流出孔２４，２４，…同士を連通させる連通路３２ａ，３２ｂが設けられている。   The first heat transfer plate 10 and the second heat transfer plate 20 are formed with inflow holes 13 and 23 and outflow holes 14 and 24 so as to surround the inflow holes 13 and 23 and the outflow holes 14 and 24. The gasket 30 is attached to the heat transfer plates 10 and 20 or is not attached so that the inflow holes 13, 13,... Of the adjacent first flow paths 1 are communicated with each other. ,... Are provided to communicate with each other, and the inflow holes 23, 23,... Of the adjacent second flow path 2 are communicated with each other, and the outflow holes 24, 24,. Communication passages 32a and 32b for communication are provided.

詳しく説明すると、第１流路１に冷媒Ｒを流入させる流入孔（以下、「冷媒流入孔」という。）１３が、第１伝熱プレート１０の一方の側部１０ａの中間部ないし一方の端部１０ｂ側に形成されている。また、第１流路１から冷媒Ｒを流出させる流出孔（以下、「冷媒流出孔」という。）１４が、第１伝熱プレート１０の一方の側部１０ａと一方の端部１０ｂとの交点である隅部に形成されている。   More specifically, an inflow hole (hereinafter referred to as “refrigerant inflow hole”) 13 through which the refrigerant R flows into the first flow path 1 is an intermediate portion or one end of one side portion 10 a of the first heat transfer plate 10. It is formed on the part 10b side. Further, an outflow hole (hereinafter referred to as “refrigerant outflow hole”) 14 through which the refrigerant R flows out from the first flow path 1 is an intersection of one side portion 10a and one end portion 10b of the first heat transfer plate 10. Is formed at the corner.

そして、第２流路２に被冷却流体Ｈを流入させる流入孔（以下、「被冷却流体流入孔」という。）２３が、第２伝熱プレート２０の他方の側部２０ｃと一方の端部（ここでは上端部）２０ｂとの交点である隅部に形成されている。また、第２流路２から被冷却流体Ｈを流出させる流出孔（以下、「被冷却流体流出孔」という。）２４が、第２伝熱プレート２０の他方の側部２０ｃの中間部、好ましくは他方の端部２０ｄ寄りの中間部に形成されている。   An inflow hole (hereinafter referred to as a “cooled fluid inflow hole”) 23 through which the fluid H to be cooled flows into the second flow path 2 is formed on the other side 20c and one end of the second heat transfer plate 20. (Here, the upper end portion) It is formed at the corner that is the intersection with 20b. In addition, an outflow hole (hereinafter referred to as “cooled fluid outflow hole”) 24 through which the fluid H to be cooled flows out from the second flow path 2 is an intermediate portion of the other side portion 20c of the second heat transfer plate 20, preferably. Is formed in an intermediate portion near the other end portion 20d.

そして、当然ながら、第１伝熱プレート１０にも被冷却流体流入孔２３及び被冷却流体流出孔２４が形成されているが、両孔２３，２４がガスケット３０，３０で囲まれることで、被冷却流体Ｈが第１流路１内を流れないようにされている。また、第２伝熱プレート２０にも冷媒流入孔１３及び冷媒流出孔１４が形成されているが、両孔１３，１４がガスケット３０，３０で囲まれることで、冷媒Ｒが第２流路２内を流れないようにされている。   Of course, the first heat transfer plate 10 also has a cooled fluid inflow hole 23 and a cooled fluid outflow hole 24, but both holes 23, 24 are surrounded by gaskets 30, 30, The cooling fluid H is prevented from flowing through the first flow path 1. In addition, the refrigerant inflow hole 13 and the refrigerant outflow hole 14 are also formed in the second heat transfer plate 20, but the refrigerant R is transferred to the second flow path 2 by surrounding the holes 13 and 14 with the gaskets 30 and 30. It is prevented from flowing inside.

そして、このプレート式熱交換器には、第１流路１の流路幅を、冷媒流入孔１３側よりも冷媒流出孔１４側で広くなるようにする仕切部（以下、「第１仕切部」という。）１５が第１伝熱プレート１０に設けられている。この第１仕切部１５は、第１伝熱プレート１０の表面から突出して設けられている。   In this plate heat exchanger, a partition portion (hereinafter referred to as “first partition portion”) that makes the flow passage width of the first flow passage 1 wider on the refrigerant outflow hole 14 side than on the refrigerant inflow hole 13 side. 15) is provided on the first heat transfer plate 10. The first partition 15 is provided so as to protrude from the surface of the first heat transfer plate 10.

すなわち、第１仕切部１５は、冷媒流入孔１３から第１伝熱プレート１０の他方の端部１０ｄに向けて、流路幅が漸増するように直線状に設けられている。また、この第１仕切部１５は、当然ながら、凸条１１と同じ高さに設けられ、第１伝熱プレート１０の他方の端部１０ｄまで到達しておらず、この他方の端部１０ｄに冷媒Ｒの迂回路が設けられている。   That is, the first partition 15 is linearly provided so that the flow path width gradually increases from the refrigerant inflow hole 13 toward the other end 10 d of the first heat transfer plate 10. Moreover, this 1st partition part 15 is naturally provided in the same height as the protruding item | line 11, and has not reached | attained the other edge part 10d of the 1st heat-transfer plate 10, but this other edge part 10d is reached. A bypass for the refrigerant R is provided.

そして、第２伝熱プレート２０にも、前記第１伝熱プレート１０の第１仕切部１５と衝合する直線状の第１仕切部２５が裏面から突出するように設けられている。したがって、第１伝熱プレート１０と第２伝熱プレート２０と積層されたときに、第１仕切部１５，２５によって、第１流路１が伝熱プレート１０，２０の一方の側部側１０ａ，２０ａと他方の側部側１０ｃ，２０ｃとに隔絶される。以下、第１仕切部１５によって仕切られた第１流路１の冷媒流入孔１３側を「上流側パス」１ａといい、冷媒流出孔１４側を「下流側パス」１ｂという。   The second heat transfer plate 20 is also provided with a linear first partition portion 25 that abuts the first partition portion 15 of the first heat transfer plate 10 so as to protrude from the back surface. Therefore, when the first heat transfer plate 10 and the second heat transfer plate 20 are stacked, the first partition 15 and 25 causes the first flow path 1 to be on one side 10a of the heat transfer plates 10 and 20. , 20a and the other side 10c, 20c. Hereinafter, the refrigerant inflow hole 13 side of the first flow path 1 partitioned by the first partition 15 is referred to as “upstream path” 1a, and the refrigerant outflow hole 14 side is referred to as “downstream path” 1b.

また、冷媒流入孔１３の周囲には、環状凸部１６が第１伝熱プレート１０の表面に突出するように設けられている。この環状凸部１６は、凸条１１及び第１仕切部１５と同じ高さとされている。ただし、冷媒Ｒが冷媒流入孔１３から第１仕切部１５の方に向いて流入するように、環状凸部１６には、切れ目のような流入部１６ａが形成されている。   Further, an annular convex portion 16 is provided around the refrigerant inflow hole 13 so as to protrude from the surface of the first heat transfer plate 10. The annular convex portion 16 has the same height as the convex strip 11 and the first partition portion 15. However, an inflow portion 16 a like a cut is formed in the annular convex portion 16 so that the refrigerant R flows from the refrigerant inflow hole 13 toward the first partition portion 15.

そして、第２流路２内の被冷却流体Ｈの流れを誘導する直線状の仕切部（以下、「第２仕切部」という。）１７が第１伝熱プレート１０の裏面から突出するように設けられている。第２仕切部１７は、被冷却流体流入孔２３から流入した被冷却流体Ｈを迂回させて被冷却流体流出孔２４へ流通するように設けられている。したがって、第２仕切部１７は、被冷却流体流出孔２４の被冷却流体流入孔２３側から、第２伝熱プレート２０の凸条２１と同一方向（角度）で第１伝熱プレート１０の他方の端部の中心に向かうように設けられている。   And the linear partition part (henceforth "the 2nd partition part") 17 which induces the flow of the to-be-cooled fluid H in the 2nd flow path 2 protrudes from the back surface of the 1st heat exchanger plate 10. FIG. Is provided. The second partition portion 17 is provided so as to bypass the cooled fluid H flowing from the cooled fluid inflow hole 23 and circulate to the cooled fluid outflow hole 24. Therefore, the second partition portion 17 extends from the cooled fluid inflow hole 23 side of the cooled fluid outflow hole 24 to the other side of the first heat transfer plate 10 in the same direction (angle) as the protrusions 21 of the second heat transfer plate 20. It is provided so that it may go to the center of the edge part.

第２伝熱プレート２０には、別途、仕切部が設けられず、凸条２１が仕切部を兼ねる。すなわち、第１伝熱プレート１０に設けられた第２仕切部１７と第２伝熱プレート２０の凸条２１とが衝合することで、第２流路２が第２伝熱プレート２０の一方の端部２０ｂ側と他方の端部２０ｄ側とに隔絶される。以下、第２仕切部１７によって仕切られた第２流の被冷却流体流入孔２３側を「上流側パス」２ａといい、被冷却流体流出孔２４側を「下流側パス」２ｂという。なお、第２伝熱プレート２０の表面に、第２仕切部１７と衝合する仕切部を別途、設けてもよい。   The second heat transfer plate 20 is not provided with a separate partition, and the ridges 21 also serve as the partition. That is, the second partition 2 provided on the first heat transfer plate 10 abuts with the ridges 21 of the second heat transfer plate 20, so that the second flow path 2 is one of the second heat transfer plates 20. The end portion 20b is separated from the other end portion 20d. Hereinafter, the cooled fluid inflow hole 23 side of the second flow partitioned by the second partitioning portion 17 is referred to as an “upstream path” 2a, and the cooled fluid outflow hole 24 side is referred to as a “downstream path” 2b. In addition, you may provide the partition part which collides with the 2nd partition part 17 on the surface of the 2nd heat-transfer plate 20 separately.

そして、第１，第２伝熱プレート１０，２０の他方の端部の中心には、ドレイン孔１８，２８が設けられている。このドレイン孔１８，２８は、第１伝熱プレート１０のΛ字状の凸条１１及び凹条１２に合わせて、三角形状に形成されている。さらに、第１，第２伝熱プレート１０，２０の他方の端部１０ｄ，２０ｄの両端には、第１，第２伝熱プレート１０，２０を鉛直姿勢で支持するための支持部１９，２９が設けられている。   Then, drain holes 18 and 28 are provided at the center of the other end of the first and second heat transfer plates 10 and 20. The drain holes 18 and 28 are formed in a triangular shape in accordance with the Λ-shaped convex stripes 11 and the concave stripes 12 of the first heat transfer plate 10. Further, support portions 19 and 29 for supporting the first and second heat transfer plates 10 and 20 in a vertical posture are provided at both ends of the other end portions 10d and 20d of the first and second heat transfer plates 10 and 20, respectively. Is provided.

このプレート式熱交換器は、以上のように構成され、次に、冷媒Ｒと被冷却流体Ｈとを熱交換する作用について説明する。   This plate heat exchanger is configured as described above. Next, the operation of exchanging heat between the refrigerant R and the fluid H to be cooled will be described.

冷媒Ｒが連通路３１ａから冷媒流入孔１３を通過して第１流路１内に流入する。この冷媒Ｒは、第１流路１の上流側パス１ａから迂回して、下流側パス１ｂへ流れ、冷媒流出孔１４から連通路３１ｂ内へ排出される。また、被冷却流体Ｈが連通路３２ａから被冷却流体流入孔２３を通過して第２流路２内に流入する。この被冷却流体Ｈは、第２流路２の上流側パス２ａから迂回して下流側パス２ｂへ流れ、被冷却流体流出孔２４から連通路３２ｂ内へ排出される。   The refrigerant R flows from the communication path 31a through the refrigerant inflow hole 13 into the first flow path 1. The refrigerant R bypasses the upstream path 1a of the first flow path 1, flows to the downstream path 1b, and is discharged from the refrigerant outflow hole 14 into the communication path 31b. In addition, the fluid H to be cooled flows from the communication passage 32 a through the fluid inflow hole 23 and flows into the second flow path 2. The cooled fluid H flows from the upstream path 2a of the second flow path 2 to the downstream path 2b, and is discharged from the cooled fluid outflow hole 24 into the communication path 32b.

圧力損失によって、第１流路１の上流側パス１ａ内を流れている冷媒Ｒの温度が上昇したとしても、第１流路１の上流側パス１ａ内を流れている冷媒Ｒと第２流路２の上流側パス２ａ内を流れている被冷却流体Ｈは、並向流となっているため、大きな温度差を確保することができる。   Even if the temperature of the refrigerant R flowing in the upstream path 1a of the first flow path 1 rises due to the pressure loss, the refrigerant R and the second flow flowing in the upstream path 1a of the first flow path 1 Since the to-be-cooled fluid H flowing in the upstream path 2a of the path 2 is a parallel flow, a large temperature difference can be secured.

また、第１流路１内の下流側パス１ｂ内を流れている冷媒Ｒは、冷媒流出孔１４に近づくにつれて、蒸発し、気化するものの、第２流路２の下流側パス２ｂ内を流れている被冷却流体Ｈと対向流となっているため、温度差を確保することで、過熱度を得ることができる。   Further, the refrigerant R flowing in the downstream path 1b in the first flow path 1 evaporates and vaporizes as it approaches the refrigerant outflow hole 14, but flows in the downstream path 2b of the second flow path 2. Therefore, the degree of superheat can be obtained by ensuring a temperature difference.

さらに、第１流路１に設けられた第１仕切部１５，２５によって、第１流路１の流路幅が漸増することで、プレートの特性が高伝熱係数−高圧力損失の特性から低伝熱係数−低圧力損失の特性に無段階に変化する。したがって、冷媒Ｒは、被熱交換媒体Ｈと効果的に熱交換される。   Further, the first partition portions 15 and 25 provided in the first flow path 1 gradually increase the flow path width of the first flow path 1, so that the characteristics of the plate are from the characteristics of high heat transfer coefficient-high pressure loss. Low heat transfer coefficient-Low pressure loss characteristics change steplessly. Therefore, the refrigerant R is effectively heat exchanged with the heat exchange medium H.

このようにして、このプレート式熱交換器は、第１伝熱プレート１０と第２伝熱プレート２０とによって交互に形成された第１流路１と第２流路２内を冷媒Ｒと被冷却流体Ｈとが流通することで、両者Ｒ，Ｈが効果的に熱交換される。   In this way, the plate heat exchanger has the first flow path 1 and the second flow path 2 formed alternately by the first heat transfer plate 10 and the second heat transfer plate 20 in the refrigerant R and the covered flow path. As the cooling fluid H circulates, both R and H are effectively heat-exchanged.

なお、本発明は、前記実施形態に限定することなく種々変更することができる。例えば、本発明は、蒸発器に限定することなく、熱媒体は、冷媒Ｒでなく油などを使用してもよい。特に熱媒体として、冷媒Ｒを使用しない場合は、冷媒流入孔１３や被冷却流体流入孔２３は、伝熱プレート１０，２０の他方の端部１０ｄ，２０ｄ側に設けるなど、各孔１３，１４，２３，２４の位置は適宜変更することができる。   In addition, this invention can be variously changed without being limited to the said embodiment. For example, the present invention is not limited to the evaporator, and the heat medium may be oil or the like instead of the refrigerant R. In particular, when the refrigerant R is not used as the heat medium, the refrigerant inflow holes 13 and the cooled fluid inflow holes 23 are provided on the other end portions 10d and 20d side of the heat transfer plates 10 and 20, respectively. , 23, 24 can be appropriately changed.

また、前記第１仕切部１５は、第１流路の流路幅を前記流入孔側よりも流出孔側で広くなるように設けられれば、直線状でなく、曲線状に設けてもよく、さらに、第１伝熱プレート１０の一方の側部１０ａと平行に設けてもよい。また、伝熱プレート１０，２０が波板状に形成されない場合は、第２伝熱プレート２０の裏面に第１仕切部２５を設けなくてもよい。また、被熱交換媒体の種類によっては、第２流路２には、必ずしも、仕切部を設けなくてもよい。   In addition, the first partition 15 may be provided in a curved shape instead of a straight line as long as the flow width of the first flow channel is wider on the outflow hole side than the inflow hole side. Furthermore, you may provide in parallel with one side part 10a of the 1st heat-transfer plate 10. FIG. Moreover, when the heat transfer plates 10 and 20 are not formed in a corrugated plate shape, the first partition portion 25 may not be provided on the back surface of the second heat transfer plate 20. Further, depending on the type of heat exchange medium, the second flow path 2 may not necessarily be provided with a partition.

さらに、このプレート式熱交換器は、第１伝熱プレート１０と第２伝熱プレート２０との外周縁及び流入孔１３，２３及び流出孔１４，２４をガスケット３０が囲むことなく、熱的に融着させたものとしてもよい。   Furthermore, this plate type heat exchanger is thermally formed without the gasket 30 surrounding the outer peripheral edge of the first heat transfer plate 10 and the second heat transfer plate 20, the inflow holes 13 and 23, and the outflow holes 14 and 24. It may be fused.

１………第１流路
２………第２流路
１０……伝熱プレート（第１伝熱プレート）
１０ａ…一方の側部
１０ｂ…一方の端部
１３……流入孔（冷媒流入孔）
１４……流出孔（襟倍流出孔）
１５……仕切部（第１仕切部）
１７……仕切部（第２仕切部）
２０……伝熱プレート（第２伝熱プレート）
２０ｂ…一方の端部
２０ｃ…他方の側部
２０ｄ…他方の端部
２３……流入孔（冷却流体流入孔）
２４……流出孔（冷却流体流出孔）
３１ａ，３１ｂ，３２ａ，３２ｂ…連通路
Ｈ………被熱交換媒体（被冷却流体）
Ｒ………熱媒体（冷媒） DESCRIPTION OF SYMBOLS 1 ......... First flow path 2 ......... Second flow path 10 ... Heat transfer plate (first heat transfer plate)
10a ... One side 10b ... One end 13 ... Inflow hole (refrigerant inflow hole)
14 …… Outflow hole (collar double outflow hole)
15 …… Partition (first partition)
17 …… Partition (second partition)
20 ... Heat transfer plate (second heat transfer plate)
20b ... one end 20c ... the other side 20d ... the other end 23 ... inflow hole (cooling fluid inflow hole)
24 …… Outflow hole (cooling fluid outflow hole)
31a, 31b, 32a, 32b ... Communication path H ... Heat exchange medium (cooled fluid)
R ... Heat medium (refrigerant)

本発明に係るプレート式熱交換器は、積層された複数の伝熱プレートのそれぞれを境にして熱媒体を流通させる第１流路と被熱交換媒体を流通させる第２流路とが交互に形成され、各伝熱プレートに流入孔及び流出孔が形成され、熱媒体が第２流路内に流入することなく第１流路内を流通するように前記流入孔又は流出孔を連通させる連通路と、被熱交換媒体が第１流路内に流入することなく第２流路内を流通するように前記流入孔又は流出孔を連通させる連通路とが設けられたプレート式熱交換器において、前記第１流路の流路幅を前記流入孔側よりも流出孔側で広くなるようにする仕切部が伝熱プレートに設けられ、前記伝熱プレートは一対の側部と一対の端部とを有する四角形状に形成され、前記第１流路の流入孔が伝熱プレートの一方の側部の中間部ないし前記一方の端部側に形成され、前記第１流路の流出孔が伝熱プレートの一方の側部と一方の端部との交点である隅部に形成され、前記仕切部が流入孔から伝熱プレートの他方の端部側に向けて設けられ、第１流路が伝熱プレートの他方の端部側で迂回するように形成されていることを特徴とする。
In the plate heat exchanger according to the present invention, the first flow path for circulating the heat medium and the second flow path for circulating the heat exchange medium alternately with each of the plurality of stacked heat transfer plates as a boundary. The inflow hole and the outflow hole are formed in each heat transfer plate, and the inflow hole or the outflow hole is communicated so that the heat medium flows through the first flow path without flowing into the second flow path. In a plate heat exchanger provided with a passage and a communication passage that connects the inflow hole or the outflow hole so that the heat exchange medium flows through the second flow path without flowing into the first flow path A partition portion is provided on the heat transfer plate so that the flow path width of the first flow path is wider on the outflow hole side than the inflow hole side , and the heat transfer plate has a pair of side portions and a pair of end portions. The inflow hole of the first flow path is one of the heat transfer plates. An intermediate portion of the side portion or the one end portion side, and an outflow hole of the first flow path is formed at a corner which is an intersection of one side portion and one end portion of the heat transfer plate, The partition portion is provided from the inflow hole toward the other end portion side of the heat transfer plate, and the first flow path is formed to bypass the other end portion side of the heat transfer plate. .

Claims (5)

積層された複数の伝熱プレートのそれぞれを境にして熱媒体を流通させる第１流路と被熱交換媒体を流通させる第２流路とが交互に形成され、各伝熱プレートに流入孔及び流出孔が形成され、熱媒体が第２流路内に流入することなく第１流路内を流通するように前記流入孔又は流出孔を連通させる連通路と、被熱交換媒体が第１流路内に流入することなく第２流路内を流通するように前記流入孔又は流出孔を連通させる連通路とが設けられたプレート式熱交換器において、
前記第１流路の流路幅を前記流入孔側よりも流出孔側で広くなるようにする仕切部が伝熱プレートに設けられたことを特徴とするプレート式熱交換器。 A first flow path for circulating the heat medium and a second flow path for circulating the heat exchange medium are alternately formed with each of the plurality of stacked heat transfer plates as a boundary. An outflow hole is formed, a communication path that communicates the inflow hole or the outflow hole so that the heat medium flows through the first flow path without flowing into the second flow path, and the heat exchange medium flows through the first flow path. In the plate-type heat exchanger provided with a communication path that communicates the inflow hole or the outflow hole so as to circulate in the second flow path without flowing into the path,
A plate-type heat exchanger, wherein the heat transfer plate is provided with a partition portion that makes the flow path width of the first flow path wider on the outflow hole side than on the inflow hole side. 前記伝熱プレートは一対の側部と一対の端部とを有する四角形状に形成され、前記第１流路の流入孔が伝熱プレートの一方の側部の中間部ないし前記一方の端部側に形成され、前記第１流路の流出孔が伝熱プレートの一方の側部と一方の端部との交点である隅部に形成され、前記仕切部が流入孔から伝熱プレートの他方の端部側に向けて設けられ、第１流路が伝熱プレートの他方の端部側で迂回するように形成されていることを特徴とする請求項１に記載のプレート式熱交換器。   The heat transfer plate is formed in a quadrangular shape having a pair of side portions and a pair of end portions, and the inflow hole of the first flow path is an intermediate portion of one side portion of the heat transfer plate to the one end portion side. And the outlet of the first flow path is formed at a corner that is the intersection of one side and one end of the heat transfer plate, and the partition is formed from the inflow hole to the other of the heat transfer plate. 2. The plate heat exchanger according to claim 1, wherein the plate heat exchanger is provided toward the end portion, and the first flow path is formed to bypass the other end portion side of the heat transfer plate. 前記仕切部は、前記第１流路の流路幅が流入孔側から流出孔側へ次第に広くなるように、前記流入孔から伝熱プレートの他方の端部の中間部の方に向けられていることを特徴とする請求項２に記載のプレート式熱交換器。   The partition portion is directed from the inflow hole toward an intermediate portion of the other end of the heat transfer plate so that a flow path width of the first flow path gradually increases from the inflow hole side to the outflow hole side. The plate-type heat exchanger according to claim 2, wherein 前記第２流路の流入孔が伝熱プレートの他方の側部と一方の端部との交点である隅部に形成され、前記第２流路の流出孔が伝熱プレートの他方の側部の中間部に形成され、被熱交換媒体が迂回して流通するように誘導する仕切部が第２流路の流出孔から伝熱プレートの他方の端部側に向けて設けられていることを特徴とする請求項２又は３に記載のプレート式熱交換器。   The inflow hole of the second flow path is formed at a corner that is the intersection of the other side of the heat transfer plate and one end, and the outflow hole of the second flow path is the other side of the heat transfer plate A partition portion that is formed in the middle portion of the heat transfer medium and guides the heat exchange medium to bypass and flow from the outflow hole of the second flow path toward the other end portion side of the heat transfer plate. The plate heat exchanger according to claim 2 or 3, characterized in that 第１伝熱プレートと第２伝熱プレートとが交互に積層され、前記第１流路の流路幅を変化させる仕切部が第１伝熱プレートの表面から突出するように設けられ、前記第２の流路を迂回させる仕切部が同じく第１伝熱プレートの裏面から突出するように設けられていることを特徴とする請求項４に記載のプレート式熱交換器。   The first heat transfer plate and the second heat transfer plate are alternately stacked, and a partition portion that changes the flow path width of the first flow path is provided so as to protrude from the surface of the first heat transfer plate. 5. The plate heat exchanger according to claim 4, wherein a partition portion for bypassing the second flow path is provided so as to protrude from the back surface of the first heat transfer plate.
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