WO2020136863A1 - Plate-type heat exchanger and heat pump device - Google Patents

Plate-type heat exchanger and heat pump device Download PDF

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Publication number
WO2020136863A1
WO2020136863A1 PCT/JP2018/048446 JP2018048446W WO2020136863A1 WO 2020136863 A1 WO2020136863 A1 WO 2020136863A1 JP 2018048446 W JP2018048446 W JP 2018048446W WO 2020136863 A1 WO2020136863 A1 WO 2020136863A1
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WO
WIPO (PCT)
Prior art keywords
plate
heat transfer
main plate
heat exchanger
transfer plate
Prior art date
Application number
PCT/JP2018/048446
Other languages
French (fr)
Japanese (ja)
Inventor
進一 内野
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020562264A priority Critical patent/JP6947314B2/en
Priority to PCT/JP2018/048446 priority patent/WO2020136863A1/en
Publication of WO2020136863A1 publication Critical patent/WO2020136863A1/en

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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
    • F28D9/02—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 heat-exchange media travelling at an angle to one another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element

Definitions

  • the present invention relates to a plate heat exchanger that performs heat exchange between a first fluid and a second fluid, and a heat pump device including the plate heat exchanger.
  • the plate heat exchanger is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forming a flow path between adjacent heat transfer plates, and forming a first fluid in the flow path. By alternately flowing the second fluid in the stacking direction, heat exchange is performed between the first fluid and the second fluid.
  • this plate heat exchanger in the related art, there is one that measures the temperature of the second fluid circulating in the refrigeration cycle by a temperature sensor provided on the side surface of the heat transfer plate (see, for example, Patent Document 1).
  • the contact area of the first fluid and the contact area of the second fluid on the side surface of the plate-type heat exchanger have substantially the same ratio. Therefore, even if the temperature sensor is provided at the position of the side surface facing the second fluid, there is a problem that the temperature of the first fluid is easily affected and the detection accuracy of the second fluid deteriorates.
  • the present invention has been made to solve the above-mentioned problems, and an object of the present invention is to obtain a plate heat exchanger and a heat pump device capable of increasing the detection accuracy of the temperature of the second fluid in the plate heat exchanger. To aim.
  • the heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately formed on the main plate.
  • the main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface from which the wall portion protrudes, and the convex portion is ,
  • the main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the main plate portion, Is provided with an elongated portion so as to be in contact with the other long side, and with the elongated portion of the heat transfer plate serving as a reference, the heat transfer plate that faces the elongated portion and is adjacent to the side on which the wall portion protrudes.
  • the distance to the convex portion of the heat plate is configured to be smaller than the distance from the elongated portion to the convex portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the heat conducting plate. ..
  • the heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately formed on the main plate.
  • a plate heat exchanger that is alternately formed in the stacking direction, by stacking the plurality of heat transfer plates, four sides formed by the plurality of wall portions at positions corresponding to the four sides of the main plate portion. At least one of the four side portions is configured such that the contact area of the second fluid is larger than the contact area of the first fluid.
  • the heat transfer plates having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately provided on the main plate portion.
  • a plurality of layers are formed by reversing by 180 degrees with respect to an axis extending perpendicularly from the center of the plate-shaped surface, and a first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates.
  • the main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface from which the wall portion protrudes, and the convex portion is,
  • the main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the main plate portion.
  • the heat transfer provided with an elongated portion so as to be in contact with the other long side and facing the elongated portion of the heat transfer plate next to the side where the wall portion projects from the elongated portion.
  • the distance to the convex portion of the plate is configured to be smaller than the distance from the long portion to the convex portion of the heat transfer plate that is adjacent and adjacent to the side on which the convex portion protrudes, and in the wall portion.
  • a temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided in a portion facing the second fluid, and a compressor for compressing the second fluid, air, and the The second fluid, which includes an air heat exchanger that exchanges heat with the second fluid, an expansion valve that lowers the pressure of the second fluid, and a pressure container that holds the excess second fluid, circulates.
  • a second fluid circuit and temperature detecting means installed in the temperature detecting means installation section are provided.
  • the plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side surface of the plate heat exchanger. Further, the plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side portion of the plate heat exchanger.
  • the temperature detection means is installed in the temperature detection means installation portion, whereby the detection accuracy of the temperature of the second fluid can be improved.
  • FIG. 1 is a schematic view of the inside of a housing of an outdoor unit showing Embodiment 1 of the present invention.
  • FIG. 3 is an exploded perspective view of the plate heat exchanger used in the first embodiment of the present invention. It is a perspective view of the plate-type heat exchanger used for Embodiment 1 of this invention.
  • FIG. 3 is a front view of the heat transfer plate used in the first embodiment of the present invention. It is an enlarged view of the heat transfer plate used in Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view of a heat transfer plate used in Embodiment 1 of the present invention. It is sectional drawing of the plate heat exchanger used for Embodiment 1 of this invention. It is sectional drawing of the plate heat exchanger used for Embodiment 1 of this invention. It is a front view of the heat transfer plate used for Embodiment 2 of this invention. It is an enlarged view of the heat transfer plate used for Embodiment 2 of this invention. It is sectional drawing of the heat transfer plate used for Embodiment 2 of this invention. It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention.
  • FIG. 1 is a refrigerant circuit diagram
  • FIG. 2 is an external view of a casing 20 of the outdoor unit 1
  • FIG. 3 is a schematic view of the inside of the casing 20 of the outdoor unit 1 seen from above.
  • the lateral direction of the rectangular main plate portion 70a which will be described later, is defined as the "lateral direction”
  • the longitudinal direction of the main plate portion 70a is defined as the "longitudinal direction”.
  • the outdoor unit 1 as a heat pump device includes a refrigerant circuit 2a as a second fluid circuit.
  • the refrigerant circuit 2a includes a plate heat exchanger 3, a compressor 4 having a muffler 4a, a four-way valve 5, an air heat exchanger 6, a pressure vessel 7, an electronic expansion valve 8a, an electronic expansion valve 8b, and a refrigerant pipe connecting them. It is composed of 10.
  • the plate heat exchanger 3 is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forms a flow path between adjacent heat transfer plates, and connects the first fluid to the flow path. By alternately flowing the second fluid in the stacking direction, heat exchange is performed between the first fluid and the second fluid.
  • the water W that carries thermal energy to the outside of the outdoor unit 1 will be described as the first fluid
  • the refrigerant R that circulates in the refrigerant circuit 2a will be described as the second fluid.
  • water is used as the first fluid in the present embodiment
  • a liquid heat medium may be used.
  • the liquid heat medium include calcium oxide aqueous solution, ethylene glycol aqueous solution, and alcohol.
  • R32 is used as the refrigerant R as the second fluid, a refrigerant such as R410A, CO2, or HC may be used.
  • the air heat exchanger 6 exchanges heat between the air and the refrigerant R, and the pressure vessel 7 stores the refrigerant R.
  • the electronic expansion valve 8a and the electronic expansion valve 8b are used as a pressure reducing device for reducing the pressure of the refrigerant R.
  • the four-way valve 5 is configured to be able to switch the flow path of the refrigerant between the heating mode and the cooling mode.
  • the refrigerant circuit 2a When the refrigerant circuit 2a is set to the heating mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is transferred to the plate heat exchanger 3 (from the refrigerant pipe connection port 3c to the refrigerant pipe connection port 3d) to the electronic device.
  • a closed circuit is configured so that the expansion valve 8b, the pressure vessel 7, the electronic expansion valve 8a, the air heat exchanger 6, the muffler 4a, and the compressor 4 circulate in this order.
  • the refrigerant circuit 2a when the refrigerant circuit 2a is set in the cooling mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is supplied to the air heat exchanger 6, the electronic expansion valve 8a, the pressure vessel 7, and the electronic expansion valve 8b.
  • a closed circuit is configured so that the plate heat exchanger 3 (from the refrigerant pipe connection port 3d to the refrigerant pipe connection port 3c), the muffler 4a, and the compressor 4 circulate in this order.
  • Temperature sensors 11, 12, 13, and 14 are attached to the side surfaces of the refrigerant pipe 10 and the plate heat exchanger 3, respectively, to detect the temperature of the refrigerant R flowing through the refrigerant circuit 2a.
  • the outdoor unit 1 includes a control device 15, a storage device 16, and a computing device 17 for controlling the operation of each part.
  • the temperature sensor 11 is for detecting the temperature of the refrigerant pipe 10 on the outlet side of the compressor 4, and is fixed to the refrigerant pipe 10 on the outlet side of the compressor 4.
  • the temperature sensor 12 is for detecting the temperature of the air heat exchanger 6, and is fixed to the refrigerant pipe 10 near the air heat exchanger 6.
  • the temperature sensor 13 is for detecting the temperature of the refrigerant pipe 10 that connects the plate heat exchanger 3 and the electronic expansion valve 8b, and is fixed to the refrigerant pipe 10.
  • the temperature sensor 14 is for detecting the temperature of the refrigerant R flowing in the plate heat exchanger 3, and is fixed to the side surface of the plate heat exchanger 3.
  • the housing 20 of the outdoor unit 1 includes a grill 20a from which air is blown.
  • the outdoor unit 1 has a blower room 21 and a machine room 22, and the blower room 21 and the machine room 22 are separated by a separator 23.
  • the outdoor unit 1 includes an electrical component box that houses electrical components on the machine room 22.
  • the air heat exchanger 6, the fan 24, and the like are arranged in the blower chamber 21, and the outside air is blown to the air heat exchanger 6 by the operation of the fan 24.
  • a compressor 4 In the machine room 22, a compressor 4, a pressure vessel 7, a four-way valve 5 (not shown in FIG. 3), a plate heat exchanger 3, electronic expansion valves 8a and 8b (not shown in FIG. 3), etc. are arranged. Has been done.
  • FIG. 4 is an exploded perspective view of the plate heat exchanger 3
  • FIG. 5 is a perspective view of the plate heat exchanger 3
  • FIG. 6 is a front view of the heat transfer plates 40 and 41.
  • FIG. 7 is an enlarged view of the heat transfer plates 40 and 41.
  • 8A is a cross-sectional view of the heat transfer plates 40 and 41 seen from the position AA of FIG. 6, and
  • FIG. 8B is a cross-sectional view of the heat transfer plates 40 and 41 of BB of FIG.
  • FIG. 7 is a cross-sectional view seen from the position
  • (c) is a cross-sectional view of the heat transfer plates 40, 41 seen from the position CC in FIG.
  • FIG. 6 is a cross-sectional view seen from the position DD of FIG. 9 is a sectional view of the plate heat exchanger 3 as seen from the position BB in FIG. 6, and FIG. 10 is a sectional view of the plate heat exchanger 3 as seen from the position CC in FIG. It is a figure.
  • the reinforcing plate 44 is formed in a substantially rectangular plate shape, and the water pipe connection port 1a, the water pipe connection port 1b, the refrigerant pipe connection port 1c, and the refrigerant pipe connection port 1d are provided at the four corners of the substantially rectangular shape.
  • the outer plate 42 is for sealing the leakage of the refrigerant R and the water W, is formed in a substantially rectangular plate shape like the reinforcing plate 44, and has the first opening 46 and the second opening 47 at the four corners. , A third opening 48, and a fourth opening 49 are formed.
  • the outer plate 43 is formed in a substantially rectangular plate shape like the outer plate 42 and the like. The outer plate 43 is not provided with the first opening 46, the second opening 47, the third opening 48, and the fourth opening 49, unlike the outer plate 42.
  • Each heat transfer plate 40 is formed in a substantially rectangular plate shape, and a first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at four corners.
  • Each heat transfer plate 41 is formed in a substantially rectangular plate shape, and a first opening 54, a second opening 55, a third opening 56, and a fourth opening 57 are formed at four corners.
  • a plurality of convex portions 61 and 62 are formed on the heat transfer plates 40 and 41, respectively.
  • the convex portions 61 and 62 are formed in a substantially V shape when viewed from the front side.
  • the water pipe connection port 1a, the first opening 46, the first opening 50, and the first opening 54 overlap in the stacking direction
  • the second opening 51 and the second opening 55 overlap in the stacking direction
  • the refrigerant pipe connection port 1c, the third opening 48, the third opening 52, and the third opening 56 overlap in the stacking direction
  • the refrigerant pipe The connection port 1d, the fourth opening 49, the fourth opening 53, and the fourth opening 57 overlap in the stacking direction.
  • the heat transfer plates 40, 41, the outer plates 42, 43, and the reinforcing plates 44, 45 are stacked so that the outer peripheral wall portions of the heat transfer plates 40, 41, and the reinforcing plates 44, 45 overlap each other, and are joined by brazing.
  • the first flow path 63 in which the water W that has flowed in from the water pipe connection port 1a flows out from the water pipe connection port 1b is formed between the back surface of the heat transfer plate 40 and the front surface of the heat transfer plate 41.
  • the second flow path 64 in which the refrigerant R flowing in from the refrigerant pipe connection port 1c flows out from the refrigerant pipe connection port 1d is formed between the back surface of the heat transfer plate 41 and the front surface of the heat transfer plate 40.
  • the water W that has flowed into the first flow path 63 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the second openings 51 and 55.
  • the water W flowing out from the openings 51, 55 is configured to flow through a passage hole formed by overlapping the openings 51, 55 and flow out from the water pipe connection port 1b to the outside.
  • the refrigerant R flowing into the second flow path 64 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the fourth openings 53 and 57.
  • the refrigerant R flowing out from the fourth openings 53 and 57 is configured to flow through a passage hole formed by overlapping the fourth openings 53 and 57 and flow out to the outside from the refrigerant pipe connection port 1d.
  • the heat transfer plate 40 includes a main plate portion 70a having a substantially rectangular plate shape, wall portions 71a, 72a, 73a, 74a provided around the main plate portion 70a, and plural main plate portions 70a.
  • the projection 61 is provided.
  • the main plate portion 70a is provided with a first opening portion 50, a second opening portion 51, a third opening portion 52, a fourth opening portion 53, and a plurality of convex portions 61.
  • the wall portions 71a, 72a, 73a, 74a are formed so as to project from one side edge of the main plate portion 70a to one side of the plate-shaped surface.
  • the wall portions 71a, 72a, 73a, 74a are formed so as to project from the peripheral edge of the main plate portion 70a to one side of the plate-shaped surface.
  • the wall portion in the present invention is formed so as to project to the back side in the stacking direction.
  • the wall portions 71a and 72a are formed continuously on the long side of the main plate portion 70a, and the wall portion 71a and the wall portion 72a are formed such that the distance between them increases as the distance from the main plate portion 70a increases. That is, the wall portion 71a and the wall portion 72a are formed in a tapered shape.
  • the wall portions 73a and 74a are formed continuously on the short sides of the main plate portion 70a, and the wall portion 73a and the wall portion 74a are formed such that the distance between them increases as the distance from the main plate portion 70a increases. That is, the wall portion 73a and the wall portion 74a are formed in a tapered shape.
  • a first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at the four corners of the main plate portion 70a.
  • the first opening 50 is formed at a corner of the main plate 70a formed by the wall 71a and the wall 74a
  • the second opening 51 is formed at a corner of the main plate 70a formed by the wall 71a and the wall 73a.
  • the third opening 52 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 73a
  • the fourth opening 53 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 74a. Is formed on.
  • the main plate portion 70a is formed with a high portion 75a in which a portion around the first opening 50 protrudes in a direction opposite to a direction in which the wall portions 71a, 72a, 73a, 74a protrude.
  • the high part 75a has a trapezoidal elevation when viewed from the front side.
  • the main plate portion 70a is formed with a high portion 76a in which a portion around the second opening portion 51 projects in a direction opposite to the direction in which the wall portions 71a, 72a, 73a, 74a project.
  • the high portion 76a has a trapezoidal elevation when viewed from the front side.
  • the projection length L1 of the wall portion 71a from the main plate portion 70a is formed to be longer than the projection length L2 of the wall portion 72a from the main plate portion 70a.
  • the protrusion length L1 is 6 mm and the protrusion length L2 is 4.7 mm.
  • the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are aligned so that the wall portion H1 has a double structure and the side surface of the plate heat exchanger 3 is increased in strength. be able to.
  • the side portion H1 mentioned here is configured by a plurality of wall portions 71a and a plurality of wall portions 72b.
  • the tip end E3 of the wall portion 71b and the tip end E4 of the wall portion 72a are configured to be aligned with each other, the wall portion H2 also has a double structure, and the strength of the side surface of the plate heat exchanger 3 is similarly increased. Can be increased.
  • the side portion H2 is composed of a plurality of wall portions 71b and a plurality of wall portions 72a.
  • the side portion H1 is also a part of the side surface of the plate heat exchanger 3, and similarly, the side portion H2 is also a part of the side surface of the plate heat exchanger 3.
  • the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are configured to be aligned, but the protrusion length of the wall portion 71a is increased to form a double wall structure. If possible, the same effect as described above can be obtained, and it is not necessary to configure the tips E1 and E2 to be aligned with each other.
  • the tip E1 of the wall portion 71a may be formed at least up to the position of the front surface portion of the wall portion 72b. With this configuration, the side surface of the second flow path 64 can be doubly covered with the wall portion 71a and the wall portion 72b on the back side thereof, and the strength of the side surface of the second flow path 64 can be increased.
  • the side surface of the first flow path 63 is the wall portion 71a, the rear wall portion 72b thereof, and the rear wall portion thereof. It can be triple-covered with 71a, and the strength of the side surface of the first flow path 63 can be increased. Similar changes may be made to the relationship between the tip E3 and the tip E4.
  • Main plate part 70a, wall parts 71a, 72a, 73a, 74a, first opening part 50, second opening part 51, third opening part 52, fourth opening part 53, a plurality of convex parts 61, and high parts 75a, 76a. Are formed by pressing a plate material.
  • the convex portion 61 is formed such that the middle valley portion of the V-shape faces one end in the longitudinal direction of the main plate portion 70a and both ends of the V-shape face the other end in the longitudinal direction of the main plate portion 70a. ..
  • the protruding height of the convex portion 61 from the main plate portion 70a is formed to be the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a.
  • the protruding height of the convex portion 61 from the main plate portion 70a may be smaller than the protruding height of the high portions 75a and 76a from the main plate portion 70a.
  • one end of the V-shaped ends of the protrusion 61 is close to the wall 72a, and the other end is formed at a position spaced from the long side of the wall 71a by a predetermined distance.
  • the distance from the one end to the wall portion 72a is smaller than the distance from the other end to the wall portion 71a.
  • Each convex portion 61 is formed from a long side of the main plate portion 70a on the side of the wall portion 72a to a position at a predetermined distance from the long side of the wall portion 71a.
  • the long side on the wall 72a side corresponds to one long side according to the claims of the present application
  • the long side on the wall 71a side corresponds to the other long side according to the claims of the present application.
  • the main plate portion 70a is formed on the wall portion 71a side of the plurality of convex portions 61.
  • a long portion Fa having no protruding shape is formed. That is, by forming a plurality of convex portions 61 formed at a predetermined interval from the long side of the main plate portion 70a on the side of the wall portion 71a in an array along the longitudinal direction of the main plate portion 70a, the wall of the main plate portion 70a is formed.
  • a long portion Fa which is a region that is a part of the main plate portion 70a and in which the convex portion 61 is not formed, is formed on the long side of the portion 71a side.
  • the convex portion 61 is not included in the constituent requirements of the main plate portion 70a.
  • the convex portion 61 is intermittently formed along the long side of the main plate portion 70a on the side of the wall portion 72a as surrounded by the two-dot chain line on the right side of FIG. 7, and the long portion Fa is As shown by being surrounded by a two-dot chain line on the left side of FIG. 7, it is formed so as to be in contact with the long side of the main plate portion 70a on the wall portion 71a side.
  • the short-side length of the long portion Fa is 1.75 mm
  • the short-side length of the main plate portion 70a is 93 mm.
  • the ratio of the length in the widthwise direction of the long portion Fa to the length in the widthwise direction of the main plate portion 70a is preferably “1.2:100 to 4:100”, and is “2:100” in the present embodiment. ..
  • the ratio of the length in the short direction of the long portion Fa to the length in the short direction of the main plate portion 70a to be “1.2:100 to 4:100”
  • the long portion Fa and the convex portion 62 on the back side thereof are formed. It is possible to preferably maintain the contact state with and the area for forming the long portion Fa on the main plate portion 70a as small as possible.
  • the long portion Fa and the convex portion 62 on the back surface thereof are brought into contact with each other.
  • the state can be maintained more preferably, and the area for forming the long portion Fa on the main plate portion 70a can be reduced as much as possible.
  • the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the rear side thereof are separated by a distance K1. Since the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the front side thereof are separated by a distance K2 (K1 ⁇ K2), The temperatures of the refrigerant R and the water W are transmitted at substantially the same ratio.
  • the side portion H1 formed of the walls 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W.
  • the temperature sensor 14 is attached to the wall 71a. Therefore, the temperature sensor 14 joined to the wall portion 71a can detect the temperature of the refrigerant R while suppressing the influence of the water W.
  • the controller 15 reads the temperature data detected by the temperature sensor 14, and the arithmetic unit 17 calculates the temperature of the refrigerant R flowing in the plate heat exchanger 3 based on the temperature data.
  • the temperature transfer between the water W and the refrigerant R is not the same ratio, and the refrigerant R is more than the water W. Since the rate of temperature transfer increases, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R. In addition, since the temperature sensor 14 increases the detection accuracy of the temperature of the refrigerant R, the outdoor unit 1 increases the calculation accuracy of the pressure saturation temperature data by the control device 15 and improves the control accuracy of the electronic expansion valves 8a and 8b. Can be increased.
  • the protrusion length L1 of the wall portion 71a from the main plate portion 70a is formed to be longer than the protrusion length L2 of the wall portion 72a from the main plate portion 70a.
  • the jointable width S1 of the temperature sensor 14 is configured to be approximately twice the width S2 of the second flow path 64 of the refrigerant R in the stacking direction. Therefore, it is not necessary to use a small temperature sensor corresponding to the width S2, and the temperature sensor 14 having a size corresponding to the width S1 can be used, so that temperature detection can be performed at low cost.
  • the protruding height of the convex portion 61 from the main plate portion 70a is the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a. Therefore, both the convex portion 61 and the high portions 75a and 76a of the heat transfer plate 40 come into contact with the main plate portion 70b of the heat transfer plate 41 located on the front surface side of the heat transfer plate 40, so that the plate type heat The strength of the exchanger 3 can be increased. Further, in the heat transfer plate 41, the protruding height of the convex portion 62 from the main plate portion 70b is formed to be the same as the protruding height of the high portions 75b and 76b from the main plate portion 70b.
  • both the convex portion 62 and the high portions 75b and 76b of the heat transfer plate 41 come into contact with the main plate portion 70a of the heat transfer plate 40 located on the front surface side of the heat transfer plate 41, so that the plate type heat The strength of the exchanger 3 can be increased.
  • the total number of the heat transfer plates 40 and the heat transfer plates 41 is an odd number.
  • the flow path closest to the outer plate 42 constitutes the first flow path 63 through which the water W flows, and the water W is formed between the outer plate 43 and the heat transfer plate 40 adjacent to the outer plate 43. Is configured to flow. Therefore, in the plate heat exchanger 3, the water (W) is present between the refrigerant R and the reinforcing plates 44 and 45, so that the heat (cold air) of the refrigerant R is exchanged through the reinforcing plates 44 and 45 into the plate heat exchanger. The energy loss can be suppressed by suppressing the discharge to the outside of the container 3.
  • Embodiment 2 An outdoor unit equipped with the plate heat exchanger 80 according to Embodiment 2 of the present invention will be described with reference to FIGS. 11 to 17. 11 to 17, the same reference numerals as those in FIGS. 1 to 10 denote the same or corresponding parts.
  • the outdoor unit provided with the plate heat exchanger 80 of the second embodiment is obtained by changing the convex portions 61 and 62 of the heat transfer plates 40 and 41 of the first embodiment.
  • FIG. 11 is a front view of the heat transfer plates 81 and 82.
  • FIG. 12 is an enlarged view of the heat transfer plates 81 and 82.
  • 13A is a cross-sectional view of the heat transfer plates 81 and 82 seen from the position EE of FIG. 11, and
  • FIG. 13B is a cross-sectional view of the heat transfer plates 81 and 82 of II of FIG.
  • FIG. 12 is a cross-sectional view seen from the position
  • (c) is a cross-sectional view of the heat transfer plates 81, 82 seen from the position JJ in FIG. 11, and
  • (d) is a view showing the heat transfer plates 81, 82.
  • 11 is a cross-sectional view as seen from the position HH of 11.
  • FIG. 14 is a cross-sectional view of the plate heat exchanger 80 as seen from the position FF in FIG. 11, and FIG. 15 is a cross section of the plate heat exchanger 80 as seen from the position GG in FIG. It is a figure.
  • 16 is a cross-sectional view of the plate heat exchanger 80 as seen from the position I-I of FIG. 11, and FIG. 17 is a cross-section of the plate heat exchanger 80 as seen from the position JJ of FIG. It is a figure.
  • the plate heat exchanger 80 (see FIGS. 14 and 15) of the present embodiment includes heat transfer plates 81 and 82 as shown in FIGS. 11 and 13.
  • the heat transfer plate 81 includes a plurality of protrusions 83 and a plurality of protrusions 84.
  • the convex portion 83 and the convex strip portion 84 are formed in a substantially V shape when viewed from the front side.
  • the plurality of convex portions 83 are formed at the central positions in the longitudinal direction of the main plate portion 70a.
  • Each convex portion 83 is formed from a long side of the main plate portion 70a on the side of the wall portion 72a to a position spaced from the long side of the wall portion 71a by a predetermined distance.
  • the main plate portion 70a is provided on the wall portion 71a side of the plurality of convex portions 83.
  • a long portion Fc having no protruding shape is formed. That is, by forming a plurality of convex portions 83 formed at a predetermined interval from the long side of the main plate portion 70a on the side of the wall portion 71a so as to be arranged along the longitudinal direction of the main plate portion 70a, the wall of the main plate portion 70a is formed.
  • a long portion Fc which is a region that is a part of the main plate portion 70a and in which the convex portion 83 is not formed, is formed on the long side of the portion 71a side.
  • the convex portion 83 is intermittently formed along the long side on the wall portion 72a side of the main plate portion 70a as shown by being surrounded by the two-dot chain line on the right side of FIG. 12, and the long portion Fc is As shown by being surrounded by a two-dot chain line on the left side of FIG. 12, the main plate portion 70a is formed so as to be in contact with the long side of the wall portion 71a of the main plate portion 70a.
  • the main plate portion 70a is formed with a plurality of ridges 84 at positions on both sides in the longitudinal direction of the elongated portion Fc.
  • Each protruding portion 84 is formed from the long side of the main plate portion 70a on the side of the wall portion 72a to the long side of the wall portion 71a.
  • the constituent features of the main plate portion 70a do not include the convex portion 83 and the convex streak portion 84.
  • the temperature sensor 14 is provided at a position corresponding to the elongated portion Fc in the longitudinal direction, and is joined to the wall portion 71 a of the heat transfer plate 81 by brazing. Has been done. Furthermore, the temperature sensor 14 is attached to a portion of the wall portion 71a facing the refrigerant R.
  • the heat transfer plate 82 has the same shape as the heat transfer plate 81, and the reference numerals in parentheses correspond to the configuration of each part of the heat transfer plate 82. That is, the first opening portion 54, the second opening portion 55, the third opening portion 56, the fourth opening portion 57, the protruding portion 85, the protruding portion 86, the main plate portion 70b, the wall portions 71b and 72b of the heat transfer plate 82, The first opening 50, the second opening 51, the third opening 52, the fourth opening 53, and the convex portion 83 of the heat transfer plate 81 are respectively included in the heat transfer plate 81.
  • the contact state between the heat transfer plate 81 and the heat transfer plate 82 will be described.
  • the elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is separated from the main plate portion 70b of the heat transfer plate 82 located on the back side. This distance is shown as a distance K5 in FIG.
  • the elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is separated from the main plate portion 70b of the heat transfer plate 82 located on the front surface side. This separated distance is shown as a distance K6 in FIG.
  • the plate heat exchanger 80 is configured such that the distance K5 and the distance K6 are substantially the same.
  • the elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is separated from the main plate portion 70a of the heat transfer plate 81 located on the rear surface side. This distance is shown as a distance K7 in FIG.
  • the elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is formed separately from the main plate portion 70a of the heat transfer plate 81 located on the front surface side. This separated distance is shown as a distance K8 in FIG.
  • the plate heat exchanger 80 is configured such that the distance K7 and the distance K8 are substantially the same.
  • the high portions 75a and 76a are configured to abut against the main plate portion 70a of the heat transfer plate 82 located on the front side thereof, and the high portions 75b and 76b are located on the front side thereof.
  • the heat transfer plate 81 is configured to come into contact with the main plate portion 70a.
  • FIG. 18 is a front view of the heat transfer plates 91 and 92.
  • 19A is a cross-sectional view of the heat transfer plates 91 and 92 seen from the position KK of FIG. 18, and
  • FIG. 19B is a cross-sectional view of the heat transfer plates 91 and 92 of LL of FIG. 19 is a cross-sectional view seen from the position
  • FIG. 19C is a cross-sectional view of the heat transfer plates 91 and 92 seen from the position MM in FIG. 18,
  • FIG. 19D is a cross-sectional view of the heat transfer plates 91 and 92.
  • FIG. 18 is a cross-sectional view seen from the position NN of 18.
  • 20 is a sectional view of the plate heat exchanger 90 seen from the position LL in FIG. 18, and
  • FIG. 21 is a sectional view of the plate heat exchanger 90 seen from the position MM in FIG. It is a figure.
  • the contact state with the long-side portion Fb on the front surface side which will be described later, is further improved. It is possible to maintain it suitably, and it is possible to reduce the area where the convex portion 93 is formed on the main plate portion 70a as much as possible.
  • the convex portion 93 of the heat transfer plate 91 is configured to come into contact with the wall portion 71 b and the elongated portion Fb of the heat transfer plate 92. Therefore, at the cross-sectional positions of FIGS. 20 and 21, only the water W comes into contact with the side portion H2 including the wall portions 71b and 72a without coming into contact with the refrigerant R. That is, the convex portion 93 of the heat transfer plate 91 is in contact with the wall portion 71 b of the heat transfer plate 92 that is adjacent and adjacent to the side where the convex portion 93 projects.
  • the elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 is in contact with the convex portion 93 of the heat transfer plate 91 located next to the side where the walls 71b, 72b, 73b, 74b project.
  • the elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 is formed separately from the convex portion 93 of the heat transfer plate 91 located on the front surface side. That is, with reference to the long portion Fb of the heat transfer plate 92, the distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 that is adjacent and adjacent to the side on which the walls 71b, 72b, 73b, and 74b project is determined. The distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 that is adjacent and adjacent to the side where the convex portion 94 projects is smaller than the distance.
  • the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 is in contact with the convex portion 94 of the heat transfer plate 92 located next to the side where the walls 71a, 72a, 73a, 74a project.
  • the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 is formed separately from the convex portion 94 of the heat transfer plate 92 located on the front surface side. That is, with reference to the long portion Fa of the heat transfer plate 91, the distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the wall portions 71a, 72a, 73a, and 74a protrude. The distance is smaller than the distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the convex portion 93 projects.
  • the convex portion 61 is not in contact with the main plate portion 70b of the heat transfer plate 92 located on the front surface side, but is configured to be in contact with the main plate portion 70b depending on the sectional position. ..
  • the convex portion 62 is not in contact with the main plate portion 70a of the heat transfer plate 91 located on the front side thereof, but is configured to be in contact with the main plate portion 70a depending on the cross-sectional position. Has been done.
  • the high portions 75a and 76a are configured to abut against the main plate portion 70b of the heat transfer plate 92 located on the front side thereof, and the high portions 75b and 76b are located on the front side thereof.
  • the heat transfer plate 91 is configured to come into contact with the main plate portion 70a.
  • the convex portion 93 of the heat transfer plate 91 abuts against the elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 located on the front side thereof, and heat transfer is performed.
  • the convex portion 94 of the plate 92 is in contact with the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 located on the front side thereof. Since the heat transfer plate 91 is laminated by rotating the heat transfer plate 92 by 180 degrees with respect to the axis Z extending perpendicularly from the center of the plate-shaped surfaces of the main plate portions 70a and 70b, the heat transfer plate 92 abuts in this manner.
  • the side portion H1 including the wall portions 71a and 72b has the wall portion 71a and the elongated portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the back side thereof. Since the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front surface thereof are in contact with each other and separated from each other, the temperature from only the refrigerant R is transmitted.
  • the side portion H1 composed of the wall portions 71a and 72b has the convex portion of the wall portion 71a and the elongated portion Fa of the heat transfer plate 91 and the heat transfer plate 92 on the rear side thereof even at the cross-sectional position shown in FIG. Since the portion 94 abuts and the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front side thereof are separated from each other, the temperature from only the refrigerant R is transmitted. It
  • the distance K9 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and adjacent to the side where the walls 71a, 72a, 73a, and 74a project is: It is configured to be smaller than the distance K10 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and opposite to the side where the convex portion 61 projects. Therefore, at the cross-sectional position in FIG. 22, the side surface H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than with the water W.
  • the temperature transfer between the water W and the refrigerant R is not at the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
  • Embodiment 5 An outdoor unit including the plate heat exchanger 110 according to the fifth embodiment of the present invention will be described with reference to FIGS. 23 and 24. 23 and 24, the same reference numerals as those in FIGS. 18 to 21 indicate the same or corresponding portions.
  • the outdoor unit equipped with the plate heat exchanger 110 of the fifth embodiment has the height of the convex portions 61, 62, 93, 94 of the heat transfer plates 91, 92 of the third embodiment lower than that of the third embodiment. It was done.
  • the convex portion 93 of the heat transfer plate 91 is configured to contact the wall portion 71b of the heat transfer plate 92, and is spaced from the long portion Fb of the heat transfer plate 92. It is configured.
  • the convex portion 94 of the heat transfer plate 92 is configured to come into contact with the wall portion 71a of the heat transfer plate 91, and is spaced apart from the long portion Fa of the heat transfer plate 91.
  • FIG. 23 is a cross-sectional view of the plate heat exchanger 110 corresponding to the position LL in FIG. 18, but with the elongated portion Fa of the heat transfer plate 91 as a reference, the elongated portion Fa to the wall portion 71a,
  • the distance K11 to the convex portion 94 of the heat transfer plate 92, which is adjacent to and opposes the side on which the protrusions 72a, 73a, and 74a are projected, is the same as the distance K11 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the convex portion 93 projects from the long portion Fa. It is configured to be smaller than the distance K12 to the convex portion 94.
  • the distance K13 to the convex portion 94 of the heat transfer plate 92 that is adjacent and is opposed to the side on which the protruding portions 71a, 72a, 73a, and 74a are adjacent is the heat transfer plate that is adjacent and that is adjacent to the side on which the convex portion 93 is protruded from the long portion Fa. It is configured to be smaller than the distance K14 to the convex portion 94 of 92.
  • the side portion H1 including the wall portions 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W. Therefore, regarding the temperature transfer to the side surface of the plate heat exchanger 110 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
  • FIG. 25 An outdoor unit including a plate heat exchanger 120 according to Embodiment 6 of the present invention will be described with reference to FIG. Note that, in FIG. 25, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding portions. While the convex portions 61 and 62 of the first embodiment are formed by pressing the heat transfer plates 40 and 41, the outdoor unit including the plate heat exchanger 120 of the sixth embodiment has a convex shape. The parts 121 and 122 are formed separately from the heat transfer plates 40 and 41. As shown in FIG. 25, a plurality of convex portions 121 are attached to a portion of the main plate portion 70a of the heat transfer plate 40 excluding the long portion Fa.
  • the side portion H1 including the wall portions 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W. Therefore, regarding the temperature transfer to the side surface of the plate heat exchanger 120 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
  • the convex portions 121 and 122 are formed separately from the heat transfer plates 40 and 41 in the sixth embodiment, the convex portion 121 is integrated with the heat transfer plate 40, and the convex portion 122 is further connected to the heat transfer plate. It may be integrated with 41. Even with this structure, the same effect can be obtained.
  • the projections 93 and 94 of the third embodiment may be provided in the second embodiment.
  • the ridges 84 and 86 are formed over the entire area in the lateral direction.
  • the height can be increased as compared with the portions 83 and 85.
  • the temperature detected by the temperature sensor 14 joined to the wall portion 71a depends on the temperature based on the refrigerant R, and the refrigerant R flowing in the plate heat exchanger 3 with higher accuracy than the temperature sensor 14 of the first embodiment. The temperature of can be detected.
  • the convex portions 83, 85 of the second embodiment may be configured to have a low height, like the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature R of the refrigerant R by the temperature sensor 14 is larger. The temperature detection accuracy can be improved.
  • the convex portions 121 and 122 of the sixth embodiment may be configured to have a low height, like the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature R of the refrigerant R by the temperature sensor 14 is larger. The temperature detection accuracy can be improved.
  • the four-way valve 5 is provided to switch the flow of the refrigerant R so that the heating mode and the cooling mode can be switched, but the structure is not limited to this.
  • the four-way valve 5 may be omitted from the refrigerant circuit 2a, and the refrigerant circuit 2a may be configured to perform only one of the heating mode and the cooling mode.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

This plate-type heat exchanger 3 is formed by rotating, by 180 degrees, heat transfer plates 40 and 41 180-degrees and stacking the heat transfer plates 40 and 41 and constitutesto configure a first flow passagesth 63 through which water W flows and a second flow passagesth 64 through which a refrigerant R flows. Elongated sections Fa, and Fb are formed at one long side of main plate sections 70a, and 70b, and protruding sections 61, and 62 are formed at the other long side. The protruding section 62 of each heat transfer plateblade 41 is configured so as to be in contact with a wall section 71a and the elongated section Fa of each heat transfer blade plate 40. Therefore, whereby only the refrigerant R and not the water W comes into contact with side sections H1 that comprise wall sections 71a, and 72b. As a result, a temperature sensor 14 joined to the wall section 71a canis able to exhibit improved temperature detection accuracy of the refrigerant R.

Description

プレート式熱交換器およびヒートポンプ装置Plate heat exchanger and heat pump device
　この発明は、第１流体と第２流体との間で熱交換を行うプレート式熱交換器および、そのプレート式熱交換器を備えたヒートポンプ装置に関する。 The present invention relates to a plate heat exchanger that performs heat exchange between a first fluid and a second fluid, and a heat pump device including the plate heat exchanger.
プレート式熱交換器とは、複数の略矩形の伝熱プレートを積層して構成された熱交換器であり、隣接する伝熱プレート間に流路を形成し、該流路に第１流体と第２流体とを積層方向に交互に流すことにより、第１流体と第２流体との間で熱交換を行うものである。このプレート式熱交換器において、従来技術では、冷凍サイクルを循環する第２流体の温度を、伝熱プレートの側面に設けた温度センサで測定するものがあった（例えば、特許文献１参照）。 The plate heat exchanger is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forming a flow path between adjacent heat transfer plates, and forming a first fluid in the flow path. By alternately flowing the second fluid in the stacking direction, heat exchange is performed between the first fluid and the second fluid. In this plate heat exchanger, in the related art, there is one that measures the temperature of the second fluid circulating in the refrigeration cycle by a temperature sensor provided on the side surface of the heat transfer plate (see, for example, Patent Document 1).
特開２０１３－１２４８３６号公報JP, 2013-124836, A
　しかしながら、上記のプレート式熱交換器は、プレート式熱交換器の側面は、第１流体の接触面積と第２流体の接触面積とがほぼ同割合となる構成となっている。そのため、温度センサを第２流体に対向する側面の位置に設けても、第１流体の温度影響を受けやすく、第２流体の検出精度が悪化するという問題があった。 However, in the plate-type heat exchanger described above, the contact area of the first fluid and the contact area of the second fluid on the side surface of the plate-type heat exchanger have substantially the same ratio. Therefore, even if the temperature sensor is provided at the position of the side surface facing the second fluid, there is a problem that the temperature of the first fluid is easily affected and the detection accuracy of the second fluid deteriorates.
　この発明は上記した問題点を解決するためになされたものであり、プレート式熱交換器内の第２流体の温度の検出精度を高めることができるプレート式熱交換器およびヒートポンプ装置を得ることを目的とする。 The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to obtain a plate heat exchanger and a heat pump device capable of increasing the detection accuracy of the temperature of the second fluid in the plate heat exchanger. To aim.
　この発明に係るプレート式熱交換器は、矩形で板状の主板部と前記主板部の縁から板状の面の一方側へ突出させた壁部とを有した伝熱プレートを交互に前記主板部の板状面の中心から垂直に延びる軸を基準に１８０度反転して複数積層し、前記伝熱プレート間に第１流体が流れる第１流路と第２流体が流れる第２流路とを積層方向に交互に形成するプレート式熱交換器において、前記主板部には、前記壁部が突出した面とは反対側の板状の面から突出する凸部が設けられ、前記凸部は、前記主板部の一方の長辺に沿って断続的にまたは連続的に形成され、且つ該凸部が突出する側の隣で対向する前記伝熱プレートの前記壁部に当接し、前記主板部は、他方の長辺に接して沿うように長尺部を備え、前記伝熱プレートの前記長尺部を基準として、前記長尺部から前記壁部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離は、前記長尺部から前記凸部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離よりも小さくなるよう構成されたものである。 In the plate heat exchanger according to the present invention, the heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately formed on the main plate. A first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates by stacking a plurality of layers by reversing 180 degrees with respect to an axis that extends vertically from the center of the plate-shaped surface of the portion. In the plate-type heat exchanger that alternately forms in the stacking direction, the main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface from which the wall portion protrudes, and the convex portion is , The main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the main plate portion, Is provided with an elongated portion so as to be in contact with the other long side, and with the elongated portion of the heat transfer plate serving as a reference, the heat transfer plate that faces the elongated portion and is adjacent to the side on which the wall portion protrudes. The distance to the convex portion of the heat plate is configured to be smaller than the distance from the elongated portion to the convex portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the heat conducting plate. ..
　この発明に係るプレート式熱交換器は、矩形で板状の主板部と前記主板部の縁から板状の面の一方側へ突出させた壁部とを有した伝熱プレートを交互に前記主板部の板状面の中心から垂直に延びる軸を基準に１８０度反転して複数積層し、前記伝熱プレート間に第１流体が流れる第１流路と第２流体が流れる第２流路とを積層方向に交互に形成するプレート式熱交換器において、前記複数の伝熱プレートを積層することで前記主板部の四つの辺に対応する位置に前記複数の壁部によって構成される四つの側部を備え、前記四つの側部のうちの少なくとも一つの側部は、前記第１流体の接触面積よりも前記第２流体の接触面積が大きくなるように構成されたものである。 In the plate heat exchanger according to the present invention, the heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately formed on the main plate. A first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates by stacking a plurality of layers by reversing 180 degrees with respect to an axis that extends vertically from the center of the plate-shaped surface of the portion. In a plate heat exchanger that is alternately formed in the stacking direction, by stacking the plurality of heat transfer plates, four sides formed by the plurality of wall portions at positions corresponding to the four sides of the main plate portion. At least one of the four side portions is configured such that the contact area of the second fluid is larger than the contact area of the first fluid.
　また、この発明に係るヒートポンプ装置は、矩形で板状の主板部と前記主板部の縁から板状の面の一方側へ突出させた壁部とを有した伝熱プレートを交互に前記主板部の板状面の中心から垂直に延びる軸を基準に１８０度反転して複数積層し、前記伝熱プレート間に第１流体が流れる第１流路と第２流体が流れる第２流路とを積層方向に交互に形成するプレート式熱交換器において、前記主板部には、前記壁部が突出した面とは反対側の板状の面から突出する凸部が設けられ、前記凸部は、前記主板部の一方の長辺に沿って断続的にまたは連続的に形成され、且つ該凸部が突出する側の隣で対向する前記伝熱プレートの前記壁部に当接し、前記主板部は、他方の長辺に接して沿うように長尺部を備え、前記伝熱プレートの前記長尺部を基準として、前記長尺部から前記壁部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離は、前記長尺部から前記凸部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離よりも小さくなるよう構成され、前記壁部における前記第２流体と対向する部分に前記第２流体の温度を検出する温度検出手段を設置するための温度検出手段設置部が設けられ、前記第２流体の圧縮を行う圧縮機と、空気と前記第２流体との熱交換を行う空気熱交換器と、前記第２流体の圧力を低下させる膨張弁と、余剰の前記第２流体を保留する圧力容器とを備えた前記第２流体が循環する第２流体回路と、前記温度検出手段設置部に設置された温度検出手段と、を備えたものである。 Further, in the heat pump device according to the present invention, the heat transfer plates having a rectangular plate-shaped main plate portion and a wall portion projecting from an edge of the main plate portion to one side of the plate-shaped surface are alternately provided on the main plate portion. A plurality of layers are formed by reversing by 180 degrees with respect to an axis extending perpendicularly from the center of the plate-shaped surface, and a first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates. In the plate heat exchanger formed alternately in the stacking direction, the main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface from which the wall portion protrudes, and the convex portion is, The main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate that is adjacent and adjacent to the protruding side of the main plate portion. , The heat transfer provided with an elongated portion so as to be in contact with the other long side and facing the elongated portion of the heat transfer plate next to the side where the wall portion projects from the elongated portion. The distance to the convex portion of the plate is configured to be smaller than the distance from the long portion to the convex portion of the heat transfer plate that is adjacent and adjacent to the side on which the convex portion protrudes, and in the wall portion. A temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided in a portion facing the second fluid, and a compressor for compressing the second fluid, air, and the The second fluid, which includes an air heat exchanger that exchanges heat with the second fluid, an expansion valve that lowers the pressure of the second fluid, and a pressure container that holds the excess second fluid, circulates. A second fluid circuit and temperature detecting means installed in the temperature detecting means installation section are provided.
　この発明のプレート式熱交換器は、プレート式熱交換器の側面から第２流体の温度を検出する際の検出精度を高めることができる。
　また、この発明のプレート式熱交換器は、プレート式熱交換器の側部から第２流体の温度を検出する際の検出精度を高めることができる。
　この発明のヒートポンプ装置は、温度検出手段設置部に温度検出手段を設置することにより、第２流体の温度の検出精度を高めることができる。 The plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side surface of the plate heat exchanger.
Further, the plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side portion of the plate heat exchanger.
In the heat pump device of the present invention, the temperature detection means is installed in the temperature detection means installation portion, whereby the detection accuracy of the temperature of the second fluid can be improved.
この発明の実施の形態１を示す冷媒回路図である。It is a refrigerant circuit diagram showing Embodiment 1 of this invention. この発明の実施の形態１を示す室外機の筐体の外形図である。It is an outline view of the case of the outdoor unit showing Embodiment 1 of this invention. この発明の実施の形態１を示す室外機の筐体内部の概略図である。1 is a schematic view of the inside of a housing of an outdoor unit showing Embodiment 1 of the present invention. この発明の実施の形態１に用いられるプレート式熱交換器の分解斜視図である。FIG. 3 is an exploded perspective view of the plate heat exchanger used in the first embodiment of the present invention. この発明の実施の形態１に用いられるプレート式熱交換器の斜視図である。It is a perspective view of the plate-type heat exchanger used for Embodiment 1 of this invention. この発明の実施の形態１に用いられる伝熱プレートの正面図である。FIG. 3 is a front view of the heat transfer plate used in the first embodiment of the present invention. この発明の実施の形態１に用いられる伝熱プレートの拡大図である。It is an enlarged view of the heat transfer plate used in Embodiment 1 of the present invention. この発明の実施の形態１に用いられる伝熱プレートの断面図である。FIG. 3 is a cross-sectional view of a heat transfer plate used in Embodiment 1 of the present invention. この発明の実施の形態１に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate heat exchanger used for Embodiment 1 of this invention. この発明の実施の形態１に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate heat exchanger used for Embodiment 1 of this invention. この発明の実施の形態２に用いられる伝熱プレートの正面図である。It is a front view of the heat transfer plate used for Embodiment 2 of this invention. この発明の実施の形態２に用いられる伝熱プレートの拡大図である。It is an enlarged view of the heat transfer plate used for Embodiment 2 of this invention. この発明の実施の形態２に用いられる伝熱プレートの断面図である。It is sectional drawing of the heat transfer plate used for Embodiment 2 of this invention. この発明の実施の形態２に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. この発明の実施の形態２に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. この発明の実施の形態２に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. この発明の実施の形態２に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate-type heat exchanger used for Embodiment 2 of this invention. この発明の実施の形態３に用いられる伝熱プレートの正面図である。It is a front view of the heat transfer plate used for Embodiment 3 of this invention. この発明の実施の形態３に用いられる伝熱プレートの断面図である。It is sectional drawing of the heat transfer plate used for Embodiment 3 of this invention. この発明の実施の形態３に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate heat exchanger used for Embodiment 3 of this invention. この発明の実施の形態３に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate heat exchanger used for Embodiment 3 of this invention. この発明の実施の形態４に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate-type heat exchanger used for Embodiment 4 of this invention. この発明の実施の形態５に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate type heat exchanger used for Embodiment 5 of this invention. この発明の実施の形態５に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate type heat exchanger used for Embodiment 5 of this invention. この発明の実施の形態６に用いられるプレート式熱交換器の断面図である。It is sectional drawing of the plate heat exchanger used for Embodiment 6 of this invention.
実施の形態１．
この発明のプレート式熱交換器を備えたヒートポンプ装置について、図１から図１０を用いて説明する。図１は冷媒回路図、図２は室外機１の筐体２０の外形図、図３は室外機１の筐体２０内部を上方から見た概略図である。
なお、本実施形態では、後述する矩形の主板部７０ａの短手方向を「短手方向」、主板部７０ａの長手方向を「長手方向」と定義している。 Embodiment 1.
A heat pump device including the plate heat exchanger of the present invention will be described with reference to FIGS. 1 to 10. FIG. 1 is a refrigerant circuit diagram, FIG. 2 is an external view of a casing 20 of the outdoor unit 1, and FIG. 3 is a schematic view of the inside of the casing 20 of the outdoor unit 1 seen from above.
In this embodiment, the lateral direction of the rectangular main plate portion 70a, which will be described later, is defined as the "lateral direction", and the longitudinal direction of the main plate portion 70a is defined as the "longitudinal direction".
ヒートポンプ装置としての室外機１は、図１に示すように、第２流体回路としての冷媒回路２ａを備えている。冷媒回路２ａは、プレート式熱交換器３、マフラー４ａを有する圧縮機４、四方弁５、空気熱交換器６、圧力容器７、電子膨張弁８ａ、電子膨張弁８ｂと、それらを繋ぐ冷媒配管１０で構成されている。
プレート式熱交換器３は、複数の略矩形の伝熱プレートを積層して構成された熱交換器であり、隣接する伝熱プレート間に流路を形成し、該流路に第１流体と第２流体とを積層方向に交互に流すことにより、第１流体と第２流体との間で熱交換を行うものである。 本実施の形態では、室外機１の外へ熱エネルギーを搬送する水Ｗを第１流体、冷媒回路２ａ内を循環する冷媒Ｒを第２流体として説明する。
なお、本実施の形態では、第１流体として水を用いているが、液状の熱媒体を用いてもよい。液状の熱媒体としては、例えば、酸化カルシウム水溶液、エチレングリコール水溶液、アルコールなどがある。また、第２流体としての冷媒ＲはＲ３２を用いているが、Ｒ４１０Ａ、ＣＯ２、ＨＣ等の冷媒を用いてもよい。 As shown in FIG. 1, the outdoor unit 1 as a heat pump device includes a refrigerant circuit 2a as a second fluid circuit. The refrigerant circuit 2a includes a plate heat exchanger 3, a compressor 4 having a muffler 4a, a four-way valve 5, an air heat exchanger 6, a pressure vessel 7, an electronic expansion valve 8a, an electronic expansion valve 8b, and a refrigerant pipe connecting them. It is composed of 10.
The plate heat exchanger 3 is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forms a flow path between adjacent heat transfer plates, and connects the first fluid to the flow path. By alternately flowing the second fluid in the stacking direction, heat exchange is performed between the first fluid and the second fluid. In the present embodiment, the water W that carries thermal energy to the outside of the outdoor unit 1 will be described as the first fluid, and the refrigerant R that circulates in the refrigerant circuit 2a will be described as the second fluid.
Although water is used as the first fluid in the present embodiment, a liquid heat medium may be used. Examples of the liquid heat medium include calcium oxide aqueous solution, ethylene glycol aqueous solution, and alcohol. Although R32 is used as the refrigerant R as the second fluid, a refrigerant such as R410A, CO2, or HC may be used.
プレート式熱交換器３は、水配管接続口３ａ、水配管接続口３ｂ、冷媒配管接続口３ｃ、冷媒配管接続口３ｄを備えている。水配管接続口３ａ、水配管接続口３ｂは水Ｗが循環する水回路２ｂ（第１流体回路）に接続されている。水回路２ｂには、給湯器、ラジエータ、床暖房、パネルヒータ、ファルコンベクタなどの放熱器に水を利用する装置（図示せず）が接続される。
圧縮機４は冷媒Ｒの圧縮を行い、四方弁５は冷媒Ｒの流れを切替える。空気熱交換器６は、空気と冷媒Ｒとの熱交換を行い、圧力容器７は冷媒Ｒを貯留する。電子膨張弁８ａ及び電子膨張弁８ｂは、冷媒Ｒの圧力を低下させる減圧装置として使用する。 The plate heat exchanger 3 includes a water pipe connection port 3a, a water pipe connection port 3b, a refrigerant pipe connection port 3c, and a refrigerant pipe connection port 3d. The water pipe connection port 3a and the water pipe connection port 3b are connected to a water circuit 2b (first fluid circuit) through which the water W circulates. To the water circuit 2b, a device (not shown) that uses water is connected to a radiator such as a water heater, a radiator, a floor heater, a panel heater, and a falcon vector.
The compressor 4 compresses the refrigerant R, and the four-way valve 5 switches the flow of the refrigerant R. The air heat exchanger 6 exchanges heat between the air and the refrigerant R, and the pressure vessel 7 stores the refrigerant R. The electronic expansion valve 8a and the electronic expansion valve 8b are used as a pressure reducing device for reducing the pressure of the refrigerant R.
四方弁５は、加熱モードと冷却モードとで冷媒の流路を切り替え可能に構成されている。
冷媒回路２ａは、加熱モードに設定されている場合には、圧縮機４で高温高圧になった冷媒Ｒを、プレート式熱交換器３（冷媒配管接続口３ｃから冷媒配管接続口３ｄ）、電子膨張弁８ｂ、圧力容器７、電子膨張弁８ａ、空気熱交換器６、マフラー４ａ、圧縮機４の順に循環するように閉回路を構成する。
一方、冷媒回路２ａは、冷却モードに設定されている場合には、圧縮機４で高温高圧になった冷媒Ｒを、空気熱交換器６、電子膨張弁８ａ、圧力容器７、電子膨張弁８ｂ、プレート式熱交換器３（冷媒配管接続口３ｄから冷媒配管接続口３ｃ）、マフラー４ａ、圧縮機４の順に循環するように閉回路を構成する。 The four-way valve 5 is configured to be able to switch the flow path of the refrigerant between the heating mode and the cooling mode.
When the refrigerant circuit 2a is set to the heating mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is transferred to the plate heat exchanger 3 (from the refrigerant pipe connection port 3c to the refrigerant pipe connection port 3d) to the electronic device. A closed circuit is configured so that the expansion valve 8b, the pressure vessel 7, the electronic expansion valve 8a, the air heat exchanger 6, the muffler 4a, and the compressor 4 circulate in this order.
On the other hand, when the refrigerant circuit 2a is set in the cooling mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is supplied to the air heat exchanger 6, the electronic expansion valve 8a, the pressure vessel 7, and the electronic expansion valve 8b. A closed circuit is configured so that the plate heat exchanger 3 (from the refrigerant pipe connection port 3d to the refrigerant pipe connection port 3c), the muffler 4a, and the compressor 4 circulate in this order.
冷媒配管１０およびプレート式熱交換器３の側面には、それぞれ温度センサ１１、１２、１３、１４が取り付けられており、それぞれ冷媒回路２ａを流れる冷媒Ｒの温度を検出している。室外機１には、冷媒回路２ａの他に、各部の動作を制御するための制御装置１５、記憶装置１６、演算装置１７を備えている。
温度センサ１１は、圧縮機４の出口側の冷媒配管１０の温度を検出するためのものであり、圧縮機４の出口側の冷媒配管１０に固定されている。温度センサ１２は、空気熱交換器６の温度を検出するためのものであり、空気熱交換器６近傍の冷媒配管１０に固定されている。温度センサ１３は、プレート式熱交換器３と電子膨張弁８ｂとをつなぐ冷媒配管１０の温度を検出するためのものであり、その冷媒配管１０に固定されている。温度センサ１４は、プレート式熱交換器３内を流れる冷媒Ｒの温度を検出するためのものであり、プレート式熱交換器３の側面に固定されている。 Temperature sensors 11, 12, 13, and 14 are attached to the side surfaces of the refrigerant pipe 10 and the plate heat exchanger 3, respectively, to detect the temperature of the refrigerant R flowing through the refrigerant circuit 2a. In addition to the refrigerant circuit 2a, the outdoor unit 1 includes a control device 15, a storage device 16, and a computing device 17 for controlling the operation of each part.
The temperature sensor 11 is for detecting the temperature of the refrigerant pipe 10 on the outlet side of the compressor 4, and is fixed to the refrigerant pipe 10 on the outlet side of the compressor 4. The temperature sensor 12 is for detecting the temperature of the air heat exchanger 6, and is fixed to the refrigerant pipe 10 near the air heat exchanger 6. The temperature sensor 13 is for detecting the temperature of the refrigerant pipe 10 that connects the plate heat exchanger 3 and the electronic expansion valve 8b, and is fixed to the refrigerant pipe 10. The temperature sensor 14 is for detecting the temperature of the refrigerant R flowing in the plate heat exchanger 3, and is fixed to the side surface of the plate heat exchanger 3.
温度センサ１１、１２、１３、１４は、検出値を制御装置１５に送信可能なように接続されている。制御装置１５は、四方弁５の切り替え動作、および電子膨張弁８ａ、８ｂの開度を調整可能なように接続されている 。
制御装置１５は、例えばマイコンで構成され、温度センサ１１、１２、１３、１４で検出した温度データを読み込んで記憶装置１６に記憶する。演算装置１７は、記憶装置１６から温度センサ１４の温度データを読み出し、その温度データに基づいて冷媒Ｒの圧力飽和温度を算出し、その算出した冷媒Ｒの圧力飽和温度を圧力飽和温度データとして記憶装置１６に記憶する。また、制御装置１５は、記憶装置１６からの温度データおよび圧力飽和温度データを読み出し、その温度および圧力に基づいて電子膨張弁８ａ、８ｂを制御する。 The temperature sensors 11, 12, 13, 14 are connected so that the detected values can be transmitted to the control device 15. The control device 15 is connected so that the switching operation of the four-way valve 5 and the opening degrees of the electronic expansion valves 8a and 8b can be adjusted.
The control device 15 is composed of, for example, a microcomputer, reads the temperature data detected by the temperature sensors 11, 12, 13, and 14 and stores the temperature data in the storage device 16. The computing device 17 reads the temperature data of the temperature sensor 14 from the storage device 16, calculates the pressure saturation temperature of the refrigerant R based on the temperature data, and stores the calculated pressure saturation temperature of the refrigerant R as pressure saturation temperature data. Stored in device 16. Further, the control device 15 reads the temperature data and the pressure saturation temperature data from the storage device 16 and controls the electronic expansion valves 8a and 8b based on the temperature and the pressure.
室外機１の筐体２０は、図２に示すように、空気が吹出されるグリル２０ａを備える。室外機１は、図３に示すように、送風機室２１、機械室２２を有しており、送風機室２１と機械室２２とはセパレータ２３で仕切られている。図示はしないが、室外機１は、機械室２２の上に電気部品を収納する電気品箱を備えている。
送風機室２１には、空気熱交換器６やファン２４等が配置されており、ファン２４が動作することにより空気熱交換器６に外気が送風される。 As shown in FIG. 2, the housing 20 of the outdoor unit 1 includes a grill 20a from which air is blown. As shown in FIG. 3, the outdoor unit 1 has a blower room 21 and a machine room 22, and the blower room 21 and the machine room 22 are separated by a separator 23. Although not shown, the outdoor unit 1 includes an electrical component box that houses electrical components on the machine room 22.
The air heat exchanger 6, the fan 24, and the like are arranged in the blower chamber 21, and the outside air is blown to the air heat exchanger 6 by the operation of the fan 24.
また、機械室２２には、圧縮機４、圧力容器７、四方弁５（図３では図示しない）、プレート式熱交換器３、電子膨張弁８ａ、８ｂ（図３では図示しない）等が配置されている。 In the machine room 22, a compressor 4, a pressure vessel 7, a four-way valve 5 (not shown in FIG. 3), a plate heat exchanger 3, electronic expansion valves 8a and 8b (not shown in FIG. 3), etc. are arranged. Has been done.
次に、プレート式熱交換器３の構成について図４～図１０を用いて説明する。
　図４は、プレート式熱交換器３の分解斜視図であり、図５は、プレート式熱交換器３の斜視図であり、図６は、伝熱プレート４０、４１の正面図である。図７は、伝熱プレート４０、４１の拡大図である。図８の（ａ）は、伝熱プレート４０、４１を図６のＡ－Ａの位置から見た断面図であり、（ｂ）は、伝熱プレート４０、４１を図６のＢ－Ｂの位置から見た断面図であり、（ｃ）は、伝熱プレート４０、４１を図６のＣ－Ｃの位置から見た断面図であり、（ｄ）は、伝熱プレート４０、４１を図６のＤ－Ｄの位置から見た断面図である。図９は、プレート式熱交換器３を図６のＢ－Ｂの位置から見た断面図であり、図１０は、プレート式熱交換器３を図６のＣ－Ｃの位置から見た断面図である。 Next, the configuration of the plate heat exchanger 3 will be described with reference to FIGS. 4 to 10.
FIG. 4 is an exploded perspective view of the plate heat exchanger 3, FIG. 5 is a perspective view of the plate heat exchanger 3, and FIG. 6 is a front view of the heat transfer plates 40 and 41. FIG. 7 is an enlarged view of the heat transfer plates 40 and 41. 8A is a cross-sectional view of the heat transfer plates 40 and 41 seen from the position AA of FIG. 6, and FIG. 8B is a cross-sectional view of the heat transfer plates 40 and 41 of BB of FIG. FIG. 7 is a cross-sectional view seen from the position, (c) is a cross-sectional view of the heat transfer plates 40, 41 seen from the position CC in FIG. 6, and (d) is a view showing the heat transfer plates 40, 41. 6 is a cross-sectional view seen from the position DD of FIG. 9 is a sectional view of the plate heat exchanger 3 as seen from the position BB in FIG. 6, and FIG. 10 is a sectional view of the plate heat exchanger 3 as seen from the position CC in FIG. It is a figure.
プレート式熱交換器３は、図４に示すように、伝熱プレート４０、４１、外側プレート４２、４３、補強プレート４４、４５を備えている。プレート式熱交換器３は、前面側から背面側へ向けて、補強プレート４４、外側プレート４２、伝熱プレート４０、４１、４０、４１、４０、４１、４０、４１、４０、外側プレート４３、補強プレート４５の順で積層されている。
　なお、本実施形態では、図４及び図５で示すように、プレート式熱交換器３における補強プレート４４が設けられている側を前面側、補強プレート４５が設けられている側を背面側と定義している。 As shown in FIG. 4, the plate heat exchanger 3 includes heat transfer plates 40 and 41, outer plates 42 and 43, and reinforcing plates 44 and 45. The plate heat exchanger 3 includes a reinforcing plate 44, an outer plate 42, heat transfer plates 40, 41, 40, 41, 40, 41, 40, 41, 40, and an outer plate 43 from the front surface side to the back surface side. The reinforcing plates 45 are laminated in this order.
In this embodiment, as shown in FIGS. 4 and 5, the side of the plate heat exchanger 3 where the reinforcing plate 44 is provided is the front side, and the side where the reinforcing plate 45 is provided is the back side. It is defined.
図４に示すように、補強プレート４４は略矩形の板状に形成され、略矩形の四隅に、水配管接続口１ａ 、水配管接続口１ｂ、冷媒配管接続口１ｃ、冷媒配管接続口１ｄが形成されている。
外側プレート４２は、冷媒Ｒや水Ｗの漏れを封止するためのものであり、補強プレート４４と同様に略矩形の板状に形成され、四隅に第１開口部４６、第２開口部４７、第３開口部４８、第４開口部４９が形成されている。外側プレート４３は、外側プレート４２等と同様に、略矩形の板状に形成される。外側プレート４３には、外側プレート４２のような第１開口部４６、第２開口部４７、第３開口部４８、第４開口部４９が設けられていない。 As shown in FIG. 4, the reinforcing plate 44 is formed in a substantially rectangular plate shape, and the water pipe connection port 1a, the water pipe connection port 1b, the refrigerant pipe connection port 1c, and the refrigerant pipe connection port 1d are provided at the four corners of the substantially rectangular shape. Has been formed.
The outer plate 42 is for sealing the leakage of the refrigerant R and the water W, is formed in a substantially rectangular plate shape like the reinforcing plate 44, and has the first opening 46 and the second opening 47 at the four corners. , A third opening 48, and a fourth opening 49 are formed. The outer plate 43 is formed in a substantially rectangular plate shape like the outer plate 42 and the like. The outer plate 43 is not provided with the first opening 46, the second opening 47, the third opening 48, and the fourth opening 49, unlike the outer plate 42.
プレート式熱交換器３は、略矩形の伝熱プレート４０、４１を交互に積層させ、それらの伝熱プレート４０、４１間に冷媒Ｒと水Ｗを交互に流通させて熱交換を行うものである。図４～図１０では、説明の便宜上伝熱プレート４０を５枚、伝熱プレート４１を４枚として説明している。また、伝熱プレート４０と、伝熱プレート４１は同じ形状のものを主板部７０ａ、７０ｂ板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転させたものである。 The plate heat exchanger 3 is configured to alternately stack substantially rectangular heat transfer plates 40 and 41, and to alternately exchange the refrigerant R and the water W between the heat transfer plates 40 and 41 to perform heat exchange. is there. 4 to 10, it is assumed that the heat transfer plates 40 are 5 and the heat transfer plates 41 are 4 for convenience of description. Further, the heat transfer plate 40 and the heat transfer plate 41 are the same in shape and rotated by 180 degrees with respect to the axis Z extending vertically from the center of the plate-shaped surfaces of the main plate portions 70a and 70b.
各伝熱プレート４０は、略矩形の板状に形成され、四隅に第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３が形成されている。各伝熱プレート４１は、略矩形の板状に形成され、四隅に第１開口部５４、第２開口部５５、第３開口部５６、第４開口部５７が形成されている。また、各伝熱プレート４０、４１には、複数の凸部６１、６２がそれぞれ形成されている。凸部６１、６２は、前面側から見た場合に、略Ｖ字状に形成されている。ここで、プレート式熱交換器３は伝熱プレート４０と伝熱プレート４１を主板部７０ａ、７０ｂの板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転させて積層された構成であるので、積層された状態においては、伝熱プレート４０に形成された凸部６１と伝熱プレート４１に形成された凸部６２とでは略Ｖ字状の向きが逆向きになるよう構成されている。
このように、向きの異なる略Ｖ字状の凸部６１、６２が重なり合う構成にすることにより、伝熱プレート４０と伝熱プレート４１との間に複雑な流れを引き起こす流路が形成される。 Each heat transfer plate 40 is formed in a substantially rectangular plate shape, and a first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at four corners. Each heat transfer plate 41 is formed in a substantially rectangular plate shape, and a first opening 54, a second opening 55, a third opening 56, and a fourth opening 57 are formed at four corners. A plurality of convex portions 61 and 62 are formed on the heat transfer plates 40 and 41, respectively. The convex portions 61 and 62 are formed in a substantially V shape when viewed from the front side. Here, the plate heat exchanger 3 has a configuration in which the heat transfer plate 40 and the heat transfer plate 41 are laminated by rotating them by 180 degrees with respect to an axis Z extending perpendicularly from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the stacked state, the convex portion 61 formed on the heat transfer plate 40 and the convex portion 62 formed on the heat transfer plate 41 are configured such that the substantially V-shaped directions are opposite to each other. There is.
In this way, the configuration in which the substantially V-shaped convex portions 61 and 62 having different directions are overlapped with each other forms a flow path that causes a complicated flow between the heat transfer plate 40 and the heat transfer plate 41.
プレート式熱交換器３は、水配管接続口１ａ、第１開口部４６、第１開口部５０、及び第１開口部５４が積層方向で重なり、水配管接続口１ｂ、第２開口部４７、第２開口部５１、及び第２開口部５５が積層方向で重なり、冷媒配管接続口１ｃ、第３開口部４８、第３開口部５２、及び第３開口部５６が積層方向で重なり、冷媒配管接続口１ｄ、第４開口部４９、第４開口部５３、及び第４開口部５７が積層方向で重なっている。
そして、伝熱プレート４０、４１、外側プレート４２、４３、及び補強プレート４４、４５の外周の壁部が重なるように積層され、ロウにより接合されている。 In the plate heat exchanger 3, the water pipe connection port 1a, the first opening 46, the first opening 50, and the first opening 54 overlap in the stacking direction, and the water pipe connection port 1b, the second opening 47, The second opening 51 and the second opening 55 overlap in the stacking direction, and the refrigerant pipe connection port 1c, the third opening 48, the third opening 52, and the third opening 56 overlap in the stacking direction, and the refrigerant pipe The connection port 1d, the fourth opening 49, the fourth opening 53, and the fourth opening 57 overlap in the stacking direction.
Then, the heat transfer plates 40, 41, the outer plates 42, 43, and the reinforcing plates 44, 45 are stacked so that the outer peripheral wall portions of the heat transfer plates 40, 41, and the reinforcing plates 44, 45 overlap each other, and are joined by brazing.
これにより、水配管接続口１ａから流入した水Ｗが水配管接続口１ｂから流出する第１流路６３が、伝熱プレート４０の背面と伝熱プレート４１の前面との間に形成される。同様に、冷媒配管接続口１ｃから流入した冷媒Ｒが冷媒配管接続口１ｄから流出する第２流路６４が、伝熱プレート４１の背面と伝熱プレート４０の前面との間に形成される。 Thereby, the first flow path 63 in which the water W that has flowed in from the water pipe connection port 1a flows out from the water pipe connection port 1b is formed between the back surface of the heat transfer plate 40 and the front surface of the heat transfer plate 41. Similarly, the second flow path 64 in which the refrigerant R flowing in from the refrigerant pipe connection port 1c flows out from the refrigerant pipe connection port 1d is formed between the back surface of the heat transfer plate 41 and the front surface of the heat transfer plate 40.
外部から水配管接続口１ａに流入した水Ｗは、伝熱プレート４０、４１の第１開口部５０、５４が重なり合うことで形成された通路孔を流れ、各第１流路６３へ流入するように構成されている。第１流路６３へ流入した水Ｗは、短手方向へ徐々に広がりながら、長手方向へ流れて、第２開口部５１、５５から流出するように構成されている。開口部５１、５５から流出した水Ｗは、開口部５１、５５が重なり合うことで形成された通路孔を流れ、水配管接続口１ｂから外部へ流出するように構成されている。
同様に、外部から冷媒配管接続口１ｃへ流入した冷媒Ｒは、各伝熱プレート４０、４１の第３開口部５２、５６が重なり合うことで形成された通路孔を流れ、各第２流路６４へ流入するように構成されている。第２流路６４へ流入した冷媒Ｒは、短手方向へ徐々に広がりながら、長手方向へ流れて、第４開口部５３、５７から流出するように構成されている。第４開口部５３、５７から流出した冷媒Ｒは、第４開口部５３、５７が重なり合うことで形成された通路孔を流れ、冷媒配管接続口１ｄから外部へ流出するように構成されている。 The water W that has flowed into the water pipe connection port 1 a from the outside flows through the passage holes formed by overlapping the first openings 50 and 54 of the heat transfer plates 40 and 41 and flows into the respective first flow paths 63. Is configured. The water W that has flowed into the first flow path 63 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the second openings 51 and 55. The water W flowing out from the openings 51, 55 is configured to flow through a passage hole formed by overlapping the openings 51, 55 and flow out from the water pipe connection port 1b to the outside.
Similarly, the refrigerant R that has flowed into the refrigerant pipe connection port 1c from the outside flows through the passage holes formed by overlapping the third openings 52 and 56 of the heat transfer plates 40 and 41, and the second flow paths 64. Is configured to flow into. The refrigerant R flowing into the second flow path 64 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the fourth openings 53 and 57. The refrigerant R flowing out from the fourth openings 53 and 57 is configured to flow through a passage hole formed by overlapping the fourth openings 53 and 57 and flow out to the outside from the refrigerant pipe connection port 1d.
次に、伝熱プレート４０の詳細な構成について説明する。
伝熱プレート４０は、図６及び図８に示すように、略矩形の板状をなしている主板部７０ａ、主板部７０ａの周囲に設けられた壁部７１ａ、７２ａ、７３ａ、７４ａ、複数の凸部６１を備えている。主板部７０ａには、第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３、及び複数の凸部６１が形成されている。壁部７１ａ、７２ａ、７３ａ、７４ａは、主板部７０ａの各辺の縁から板状の面の一方側へ突出させるように形成されている。すなわち、壁部７１ａ、７２ａ、７３ａ、７４ａは、主板部７０ａの周縁から板状の面の一方側へ突出させるように形成されている。
なお、本発明における壁部は、積層方向における背面側に突出するように形成されている。 Next, the detailed configuration of the heat transfer plate 40 will be described.
As shown in FIGS. 6 and 8, the heat transfer plate 40 includes a main plate portion 70a having a substantially rectangular plate shape, wall portions 71a, 72a, 73a, 74a provided around the main plate portion 70a, and plural main plate portions 70a. The projection 61 is provided. The main plate portion 70a is provided with a first opening portion 50, a second opening portion 51, a third opening portion 52, a fourth opening portion 53, and a plurality of convex portions 61. The wall portions 71a, 72a, 73a, 74a are formed so as to project from one side edge of the main plate portion 70a to one side of the plate-shaped surface. That is, the wall portions 71a, 72a, 73a, 74a are formed so as to project from the peripheral edge of the main plate portion 70a to one side of the plate-shaped surface.
The wall portion in the present invention is formed so as to project to the back side in the stacking direction.
壁部７１ａ、７２ａは、主板部７０ａの長辺に連続して形成されており、壁部７１ａと壁部７２ａとは、主板部７０ａから離れるにつれ互いの間隔が広がるように形成されている。すなわち、壁部７１ａと壁部７２ａとはテーパー状に形成されている。
壁部７３ａ、７４ａは、主板部７０ａの短辺に連続して形成されており、壁部７３ａと壁部７４ａとは、主板部７０ａから離れるにつれ互いの間隔が広がるように形成されている。すなわち、壁部７３ａと壁部７４ａとはテーパー状に形成されている。 The wall portions 71a and 72a are formed continuously on the long side of the main plate portion 70a, and the wall portion 71a and the wall portion 72a are formed such that the distance between them increases as the distance from the main plate portion 70a increases. That is, the wall portion 71a and the wall portion 72a are formed in a tapered shape.
The wall portions 73a and 74a are formed continuously on the short sides of the main plate portion 70a, and the wall portion 73a and the wall portion 74a are formed such that the distance between them increases as the distance from the main plate portion 70a increases. That is, the wall portion 73a and the wall portion 74a are formed in a tapered shape.
主板部７０ａの四隅には、第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３が形成されている。
第１開口部５０は壁部７１ａと壁部７４ａとがなす主板部７０ａの隅部に形成され、第２開口部５１は壁部７１ａと壁部７３ａとがなす主板部７０ａの隅部に形成され、第３開口部５２は壁部７２ａと壁部７３ａとがなす主板部７０ａの隅部に形成され、第４開口部５３は壁部７２ａと壁部７４ａとがなす主板部７０ａの隅部に形成されている。
主板部７０ａには、第１開口部５０の周囲の部分が、壁部７１ａ、７２ａ、７３ａ、７４ａが突出する方向とは逆方向へ突出した高部７５ａが形成されている。高部７５ａは前面側から見て台形状をなす盛り上がりとなっている。
同様に、主板部７０ａには、第２開口部５１の周囲の部分が、壁部７１ａ、７２ａ、７３ａ、７４ａが突出する方向とは逆方向へ突出した高部７６ａが形成されている。高部７６ａは前面側から見て台形状をなす盛り上がりとなっている。 A first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at the four corners of the main plate portion 70a.
The first opening 50 is formed at a corner of the main plate 70a formed by the wall 71a and the wall 74a, and the second opening 51 is formed at a corner of the main plate 70a formed by the wall 71a and the wall 73a. The third opening 52 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 73a, and the fourth opening 53 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 74a. Is formed on.
The main plate portion 70a is formed with a high portion 75a in which a portion around the first opening 50 protrudes in a direction opposite to a direction in which the wall portions 71a, 72a, 73a, 74a protrude. The high part 75a has a trapezoidal elevation when viewed from the front side.
Similarly, the main plate portion 70a is formed with a high portion 76a in which a portion around the second opening portion 51 projects in a direction opposite to the direction in which the wall portions 71a, 72a, 73a, 74a project. The high portion 76a has a trapezoidal elevation when viewed from the front side.
壁部７１ａの主板部７０ａからの突出長さＬ１は、図８に示すように、壁部７２ａの主板部７０ａからの突出長さＬ２よりも長くなるように形成されている。なお、本実施の形態では、突出長さＬ１は６ｍｍ、突出長さＬ２は４．７ｍｍとしている。
　このように壁部７１ａを壁部７２ａより長い構成にすることにより、伝熱プレート４０と伝熱プレート４１との積層状態において、図９に示すように、伝熱プレート４０の壁部７１ａの先端Ｅ１と、伝熱プレート４０の背面に位置する伝熱プレート４１の壁部７２ｂ（壁部７２ｂは後述する）の先端Ｅ２とが揃うように構成されている。このように、壁部７１ａの先端Ｅ１と、壁部７２ｂの先端Ｅ２とが揃うように構成されていることにより、壁部Ｈ１が二重構造となりプレート式熱交換器３の側面の強度を高めることができる。なお、ここでいう側部Ｈ１とは、複数の壁部７１ａと複数の壁部７２ｂとで構成されるものである。また、壁部７１ｂの先端Ｅ３と、壁部７２ａの先端Ｅ４とが揃うように構成されていることにより、同様に、壁部Ｈ２が二重構造となりプレート式熱交換器３の側面の強度を高めることができる。側部Ｈ２とは、複数の壁部７１ｂと複数の壁部７２ａとで構成されるものである。側部Ｈ１はプレート式熱交換器３の側面の一部でもあり、同様に、側部Ｈ２はプレート式熱交換器３の側面の一部でもある。 As shown in FIG. 8, the projection length L1 of the wall portion 71a from the main plate portion 70a is formed to be longer than the projection length L2 of the wall portion 72a from the main plate portion 70a. In the present embodiment, the protrusion length L1 is 6 mm and the protrusion length L2 is 4.7 mm.
By thus making the wall portion 71a longer than the wall portion 72a, as shown in FIG. 9, in the stacked state of the heat transfer plate 40 and the heat transfer plate 41, the tip of the wall portion 71a of the heat transfer plate 40 is formed. E1 and the end portion E2 of the wall portion 72b (the wall portion 72b will be described later) of the heat transfer plate 41 located on the back surface of the heat transfer plate 40 are configured to be aligned with each other. In this manner, the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are aligned so that the wall portion H1 has a double structure and the side surface of the plate heat exchanger 3 is increased in strength. be able to. In addition, the side portion H1 mentioned here is configured by a plurality of wall portions 71a and a plurality of wall portions 72b. Further, since the tip end E3 of the wall portion 71b and the tip end E4 of the wall portion 72a are configured to be aligned with each other, the wall portion H2 also has a double structure, and the strength of the side surface of the plate heat exchanger 3 is similarly increased. Can be increased. The side portion H2 is composed of a plurality of wall portions 71b and a plurality of wall portions 72a. The side portion H1 is also a part of the side surface of the plate heat exchanger 3, and similarly, the side portion H2 is also a part of the side surface of the plate heat exchanger 3.
なお、本実施の形態では、壁部７１ａの先端Ｅ１と、壁部７２ｂの先端Ｅ２とが揃うように構成したが、壁部７１ａの突出長さを長くして壁部の二重構造を形成できれば上記と同様の効果を得ることができるものであり、互いの先端Ｅ１、Ｅ２を揃うように構成しなくてもよい。壁部７１ａの先端Ｅ１は少なくとも壁部７２ｂの前面部の位置まで形成されていればよい。かかる構成によれば、第二流路６４の側面を壁部７１ａとその背面側の壁部７２ｂとにより二重に覆うことができ、第二流路６４の側面の強度を高めることができる。壁部７１ａの先端Ｅ１を壁部７２ｂの先端Ｅ２の位置まで形成した場合には、第一流路６３の側面を壁部７１ａと、その背面側の壁部７２ｂと、さらにその背面側の壁部７１ａとにより三重に覆うことができ、第一流路６３の側面の強度を高めることができる。先端Ｅ３と先端Ｅ４との関係についても同様の変更としてもよい。
主板部７０ａ、壁部７１ａ、７２ａ、７３ａ、７４ａ、第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３、複数の凸部６１、及び高部７５ａ、７６ａは、板材をプレス加工することによって形成されている。  In the present embodiment, the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are configured to be aligned, but the protrusion length of the wall portion 71a is increased to form a double wall structure. If possible, the same effect as described above can be obtained, and it is not necessary to configure the tips E1 and E2 to be aligned with each other. The tip E1 of the wall portion 71a may be formed at least up to the position of the front surface portion of the wall portion 72b. With this configuration, the side surface of the second flow path 64 can be doubly covered with the wall portion 71a and the wall portion 72b on the back side thereof, and the strength of the side surface of the second flow path 64 can be increased. When the tip E1 of the wall portion 71a is formed to the position of the tip E2 of the wall portion 72b, the side surface of the first flow path 63 is the wall portion 71a, the rear wall portion 72b thereof, and the rear wall portion thereof. It can be triple-covered with 71a, and the strength of the side surface of the first flow path 63 can be increased. Similar changes may be made to the relationship between the tip E3 and the tip E4.
Main plate part 70a, wall parts 71a, 72a, 73a, 74a, first opening part 50, second opening part 51, third opening part 52, fourth opening part 53, a plurality of convex parts 61, and high parts 75a, 76a. Are formed by pressing a plate material.
主板部７０ａにおける高部７５ａ、７６ａを除いた部位には、図６に示すように、主板部７０ａの長手方向（以下、単に長手方向という）に沿って凸部６１が配列された状態で形成されている。凸部６１は、前面側から見てＶ字形状の突出となっており、Ｖ字の中間の谷となる部分が壁部７３ａを向き、Ｖ字の両端が壁部７４ａを向くように形成されている。すなわち、凸部６１は、Ｖ字の中間の谷となる部分が主板部７０ａの長手方向の一端を向き、Ｖ字の両端が主板部７０ａの長手方向の他端を向くように形成されている。
凸部６１の主板部７０ａからの突出高さは、高部７５ａ、７６ａの主板部７０ａからの突出高さと同じとなるように形成されている。なお、凸部６１の主板部７０ａからの突出高さを、高部７５ａ、７６ａの主板部７０ａからの突出高さよりも小さく形成してもよい。 As shown in FIG. 6, the main plate portion 70a is formed in a state where the convex portions 61 are arranged along the longitudinal direction of the main plate portion 70a (hereinafter, simply referred to as the longitudinal direction), except for the high portions 75a and 76a. Has been done. The convex portion 61 has a V-shaped protrusion when viewed from the front side, and is formed such that the middle valley of the V-shape faces the wall portion 73a and both ends of the V-shape face the wall portion 74a. ing. That is, the convex portion 61 is formed such that the middle valley portion of the V-shape faces one end in the longitudinal direction of the main plate portion 70a and both ends of the V-shape face the other end in the longitudinal direction of the main plate portion 70a. ..
The protruding height of the convex portion 61 from the main plate portion 70a is formed to be the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a. The protruding height of the convex portion 61 from the main plate portion 70a may be smaller than the protruding height of the high portions 75a and 76a from the main plate portion 70a.
すなわち、突部６１のＶ字の両端のうちの一端は壁部７２ａに近接しており、他端は壁部７１ａの長辺から所定間隔をおいた位置に形成されている。かかる構成により、当該一端から壁部７２ａまでの距離は、当該他端から壁部７１ａまでの距離よりも小さくなっている。
各凸部６１は、主板部７０ａの壁部７２ａ側の長辺から、壁部７１ａの長辺から所定間隔をおいた位置まで形成されている。
なお、壁部７２ａ側の長辺は、本願請求項に係る一方の長辺に相当し、壁部７１ａ側の長辺は、本願請求項に係る他方の長辺に相当する。 That is, one end of the V-shaped ends of the protrusion 61 is close to the wall 72a, and the other end is formed at a position spaced from the long side of the wall 71a by a predetermined distance. With this configuration, the distance from the one end to the wall portion 72a is smaller than the distance from the other end to the wall portion 71a.
Each convex portion 61 is formed from a long side of the main plate portion 70a on the side of the wall portion 72a to a position at a predetermined distance from the long side of the wall portion 71a.
The long side on the wall 72a side corresponds to one long side according to the claims of the present application, and the long side on the wall 71a side corresponds to the other long side according to the claims of the present application.
複数の凸部６１が、主板部７０ａの壁部７１ａ側の長辺から所定間隔をおいた位置まで形成されていることにより、複数の凸部６１の壁部７１ａ側には、主板部７０ａが突出した形状を有していない長尺部Ｆａが形成されている。すなわち、主板部７０ａの壁部７１ａ側の長辺から所定間隔をおいて形成した複数の凸部６１を、主板部７０ａの長手方向に沿って配列させて形成することにより、主板部７０ａの壁部７１ａ側の長辺側には、主板部７０ａの一部であるとともに凸部６１が形成されていない領域である長尺部Ｆａが形成されている。なお、主板部７０ａの構成要件には、凸部６１を含んでいない。 Since the plurality of convex portions 61 are formed from the long side on the wall portion 71a side of the main plate portion 70a to a position spaced by a predetermined distance, the main plate portion 70a is formed on the wall portion 71a side of the plurality of convex portions 61. A long portion Fa having no protruding shape is formed. That is, by forming a plurality of convex portions 61 formed at a predetermined interval from the long side of the main plate portion 70a on the side of the wall portion 71a in an array along the longitudinal direction of the main plate portion 70a, the wall of the main plate portion 70a is formed. A long portion Fa, which is a region that is a part of the main plate portion 70a and in which the convex portion 61 is not formed, is formed on the long side of the portion 71a side. In addition, the convex portion 61 is not included in the constituent requirements of the main plate portion 70a.
すなわち、凸部６１は、図７の右側の二点鎖線で囲んで示したように主板部７０ａの壁部７２ａ側の長辺に沿って断続的に形成され、且つ、長尺部Ｆａは、図７の左側の二点鎖線で囲んで示したように主板部７０ａの壁部７１ａ側の長辺に接して沿うように形成されている。 That is, the convex portion 61 is intermittently formed along the long side of the main plate portion 70a on the side of the wall portion 72a as surrounded by the two-dot chain line on the right side of FIG. 7, and the long portion Fa is As shown by being surrounded by a two-dot chain line on the left side of FIG. 7, it is formed so as to be in contact with the long side of the main plate portion 70a on the wall portion 71a side.
本実施形態では、長尺部Ｆａの短手方向長さを１．７５ｍｍ、主板部７０ａの短手方向長さを９３ｍｍとしている。長尺部Ｆａの短手方向長さと主板部７０ａの短手方向長さの比は、「１．２：１００～４：１００」が望ましく、本実施の形態では、「２：１００」としている。長尺部Ｆａの短手方向長さと主板部７０ａの短手方向長さの比を「１．２：１００～４：１００」とすることで、長尺部Ｆａとその背面側の凸部６２との当接状態を好適に維持でき、かつ、主板部７０ａ上に長尺部Ｆａを構成させる面積を極力少なくすることが可能となる。また、長尺部Ｆａの短手方向長さと主板部７０ａの短手方向長さの比を「２：１００」とすることで、長尺部Ｆａとその背面側の凸部６２との当接状態をよりいっそう好適に維持でき、かつ、主板部７０ａ上に長尺部Ｆａを構成させる面積を極力少なくすることが可能となる。 In the present embodiment, the short-side length of the long portion Fa is 1.75 mm, and the short-side length of the main plate portion 70a is 93 mm. The ratio of the length in the widthwise direction of the long portion Fa to the length in the widthwise direction of the main plate portion 70a is preferably “1.2:100 to 4:100”, and is “2:100” in the present embodiment. .. By setting the ratio of the length in the short direction of the long portion Fa to the length in the short direction of the main plate portion 70a to be “1.2:100 to 4:100”, the long portion Fa and the convex portion 62 on the back side thereof are formed. It is possible to preferably maintain the contact state with and the area for forming the long portion Fa on the main plate portion 70a as small as possible. Further, by setting the ratio of the short-side length of the long portion Fa to the short-side length of the main plate portion 70a to "2:100", the long portion Fa and the convex portion 62 on the back surface thereof are brought into contact with each other. The state can be maintained more preferably, and the area for forming the long portion Fa on the main plate portion 70a can be reduced as much as possible.
次に、伝熱プレート４１の詳細な構成について説明する。
　伝熱プレート４１は、図６及び図８に示すように、伝熱プレート４０と同形状をなしており、カッコで示す符号が伝熱プレート４１の各部の構成に対応している。
　すなわち、伝熱プレート４１における第１開口部５４、第２開口部５５、第３開口部５６、第４開口部５７、凸部６２、主板部７０ｂ、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂ、高部７５ｂ、７６ｂ、長尺部Ｆｂのそれぞれは、伝熱プレート４０における第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３、凸部６１、主板部７０ａ、壁部７１ａ、７２ａ、７３ａ、７４ａ、高部７５ａ、７６ａ、長尺部Ｆａにそれぞれ対応している。そのため、伝熱プレート４１の各部の説明は省略する。なお、主板部７０ｂの構成要件には、凸部６２を含んでいない。 Next, the detailed configuration of the heat transfer plate 41 will be described.
As shown in FIGS. 6 and 8, the heat transfer plate 41 has the same shape as the heat transfer plate 40, and the reference numerals in parentheses correspond to the configurations of the respective parts of the heat transfer plate 41.
That is, the first opening portion 54, the second opening portion 55, the third opening portion 56, the fourth opening portion 57, the convex portion 62, the main plate portion 70b, the wall portions 71b, 72b, 73b, 74b, and the high portions of the heat transfer plate 41 are high. Each of the portions 75b and 76b and the elongated portion Fb has a first opening portion 50, a second opening portion 51, a third opening portion 52, a fourth opening portion 53, a convex portion 61, a main plate portion 70a in the heat transfer plate 40. They correspond to the wall portions 71a, 72a, 73a, 74a, the high portions 75a, 76a, and the long portion Fa, respectively. Therefore, description of each part of the heat transfer plate 41 is omitted. In addition, the convex portion 62 is not included in the constituent requirements of the main plate portion 70b.
　次に、伝熱プレート４０と伝熱プレート４１との接触状態を説明する。
プレート式熱交換器３は伝熱プレート４０と伝熱プレート４１を主板部７０ａ、７０ｂの板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転させて積層された構成である。そのため、積層された状態においては、壁部７１ａと壁部７２ｂとが、壁部７２ａと壁部７１ｂとが、壁部７３ａと壁部７４ｂとが、壁部７４ａと壁部７３ｂとがそれぞれ重なるように構成されている。 Next, the contact state between the heat transfer plate 40 and the heat transfer plate 41 will be described.
The plate heat exchanger 3 has a structure in which the heat transfer plate 40 and the heat transfer plate 41 are laminated by rotating them by 180 degrees with respect to an axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the stacked state, the wall portion 71a and the wall portion 72b overlap, the wall portion 72a and the wall portion 71b overlap, the wall portion 73a and the wall portion 74b overlap, and the wall portion 74a and the wall portion 73b overlap. Is configured.
図９に示すように、伝熱プレート４０の主板部７０ａの長尺部Ｆａは、背面側に位置する伝熱プレート４１の主板部７０ｂと離れて構成されている。この離れた距離を図９では、距離Ｋ１として示している。また、伝熱プレート４０の主板部７０ａの長尺部Ｆａは、前面側に位置する伝熱プレート４１の主板部７０ｂと離れて構成されている。この離れた距離を図９では、距離Ｋ２として示している。プレート式熱交換器３は、距離Ｋ１と距離Ｋ２とが、ほぼ同じになるように構成されている。 As shown in FIG. 9, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 40 is separated from the main plate portion 70b of the heat transfer plate 41 located on the back side. This distance is shown as the distance K1 in FIG. Further, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 40 is formed separately from the main plate portion 70b of the heat transfer plate 41 located on the front surface side. This distance is shown as a distance K2 in FIG. The plate heat exchanger 3 is configured such that the distance K1 and the distance K2 are substantially the same.
図９に示すように、伝熱プレート４１の主板部７０ｂの長尺部Ｆｂは、背面側に位置する伝熱プレート４０の主板部７０ａと離れて構成されている。この離れた距離を図９では、距離Ｋ３として示している。また、伝熱プレート４１の主板部７０ｂの長尺部Ｆｂは、前面側に位置する伝熱プレート４０の主板部７０ａと離れて構成されている。この離れた距離を図９では、距離Ｋ４として示している。プレート式熱交換器３は、距離Ｋ３と距離Ｋ４とが、ほぼ同じになるように構成されている。 As shown in FIG. 9, the elongated portion Fb of the main plate portion 70b of the heat transfer plate 41 is separated from the main plate portion 70a of the heat transfer plate 40 located on the back surface side. This distance is shown as the distance K3 in FIG. The elongated portion Fb of the main plate portion 70b of the heat transfer plate 41 is formed separately from the main plate portion 70a of the heat transfer plate 40 located on the front surface side. This distance is shown as a distance K4 in FIG. The plate heat exchanger 3 is configured such that the distance K3 and the distance K4 are substantially the same.
　図１０に示すように、伝熱プレート４０の凸部６１は、伝熱プレート４１の壁部７１ｂ及び長尺部Ｆｂに当接するように構成されている。このため、図１０の断面位置においては、壁部７１ｂ、７２ａからなる側部Ｈ２には、冷媒Ｒが接触することなく、水Ｗのみが接触する。すなわち、伝熱プレート４０の凸部６１は、その凸部６１が突出する側の隣で対向する伝熱プレート４１の壁部７１ｂに当接されている。また、伝熱プレート４１の主板部７０ｂの長尺部Ｆｂは、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣に位置する伝熱プレート４０の凸部６１と当接されている。 As shown in FIG. 10, the convex portion 61 of the heat transfer plate 40 is configured to come into contact with the wall portion 71b and the elongated portion Fb of the heat transfer plate 41. Therefore, at the cross-sectional position of FIG. 10, the coolant H does not come into contact with the side portion H2 including the walls 71b and 72a, but only the water W comes into contact therewith. That is, the convex portion 61 of the heat transfer plate 40 is in contact with the wall portion 71b of the heat transfer plate 41 that is adjacent and adjacent to the side on which the convex portion 61 projects. Further, the elongated portion Fb of the main plate portion 70b of the heat transfer plate 41 is in contact with the convex portion 61 of the heat transfer plate 40 located next to the side where the walls 71b, 72b, 73b, 74b project.
一方、伝熱プレート４１の主板部７０ｂの長尺部Ｆｂは、前面側に位置する伝熱プレート４０の凸部６１と離れて構成されている。
すなわち、伝熱プレート４１の長尺部Ｆｂを基準として、長尺部Ｆｂから壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣で対向する伝熱プレート４０の凸部６１までの距離は、長尺部Ｆｂから凸部６２が突出する側の隣で対向する伝熱プレート４０の凸部６１までの距離よりも小さくなるように構成されている。 On the other hand, the elongated portion Fb of the main plate portion 70b of the heat transfer plate 41 is formed separately from the convex portion 61 of the heat transfer plate 40 located on the front surface side.
That is, based on the elongated portion Fb of the heat transfer plate 41, the distance from the elongated portion Fb to the convex portion 61 of the heat transfer plate 40 that is adjacent and adjacent to the side on which the walls 71b, 72b, 73b, and 74b project is determined. The distance is smaller than the distance from the long portion Fb to the convex portion 61 of the heat transfer plate 40 that is adjacent and adjacent to the side on which the convex portion 62 projects.
　図１０に示すように、伝熱プレート４１の凸部６２は、伝熱プレート４０の壁部７１ａ及び長尺部Ｆａに当接するように構成されている。このため、図１０の断面位置においては、壁部７１ａ、７２ｂからなる側部Ｈ１には、水Ｗが接触することなく、冷媒Ｒのみが接触する。すなわち、伝熱プレート４１の凸部６２は、その凸部６２が突出する側の隣で対向する伝熱プレート４０の壁部７１ａに当接されている。また、伝熱プレート４０の主板部７０ａの長尺部Ｆａは、壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣に位置する伝熱プレート４１の凸部６２と当接されている。 As shown in FIG. 10, the convex portion 62 of the heat transfer plate 41 is configured to come into contact with the wall portion 71 a and the elongated portion Fa of the heat transfer plate 40. Therefore, at the cross-sectional position of FIG. 10, only the refrigerant R comes into contact with the side portion H1 including the wall portions 71a and 72b without coming into contact with the water W. That is, the convex portion 62 of the heat transfer plate 41 is in contact with the wall portion 71 a of the heat transfer plate 40 that is adjacent and adjacent to the side where the convex portion 62 projects. Further, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 40 is in contact with the convex portion 62 of the heat transfer plate 41 located next to the side where the walls 71a, 72a, 73a, 74a project.
一方、伝熱プレート４０の主板部７０ａの長尺部Ｆａは、前面側に位置する伝熱プレート４１の凸部６２と離れて構成されている。
すなわち、伝熱プレート４０の長尺部Ｆａを基準として、長尺部Ｆａから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート４１の凸部６２までの距離は、長尺部Ｆａから凸部６１が突出する側の隣で対向する伝熱プレート４１の凸部６２までの距離よりも小さくなるように構成されている。
伝熱プレート４１は伝熱プレート４０を主板部７０ａ、７０ｂの板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転して積層されているので、伝熱プレート４０と伝熱プレート４１とは上記のように当接する。 On the other hand, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 40 is formed separately from the convex portion 62 of the heat transfer plate 41 located on the front surface side.
That is, with the long portion Fa of the heat transfer plate 40 as a reference, the distance from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and adjacent to the side where the wall portions 71a, 72a, 73a, and 74a protrude. The distance is smaller than the distance from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and adjacent to the side on which the convex portion 61 projects.
The heat transfer plate 41 is laminated by rotating the heat transfer plate 40 by 180 degrees with respect to the axis Z extending perpendicularly from the center of the plate-like surfaces of the main plate portions 70a and 70b, so that the heat transfer plate 40 and the heat transfer plate 41 are laminated. And abut as described above.
　図９の断面位置では、凸部６１は、その前面側に位置する伝熱プレート４１の主板部７０ｂに対して当接していないが、断面位置によっては当接するように構成されている。同様に、図９の断面位置では、凸部６２は、その前面側に位置する伝熱プレート４０の主板部７０ａに対して当接していないが、断面位置によっては当接するように構成されている。また、図示はしないが、高部７５ａ、７６ａは、その前面側に位置する伝熱プレート４１の主板部７０ｂに対して当接するように構成され、高部７５ｂ、７６ｂは、その前面側に位置する伝熱プレート４０の主板部７０ａに対して当接するように構成されている。 At the cross-sectional position of FIG. 9, the convex portion 61 is not in contact with the main plate portion 70b of the heat transfer plate 41 located on the front surface side thereof, but is configured to be in contact with the main plate portion 70b depending on the cross-sectional position. Similarly, at the cross-sectional position of FIG. 9, the convex portion 62 does not abut against the main plate portion 70a of the heat transfer plate 40 located on the front side thereof, but is configured to abut depending on the cross-sectional position. .. Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70b of the heat transfer plate 41 located on the front side thereof, and the high portions 75b and 76b are located on the front side thereof. The heat transfer plate 40 is configured to come into contact with the main plate portion 70a.
プレート式熱交換器３は、同じ形状の伝熱プレート４０と伝熱プレート４１とを主板部７０ａ、７０ｂの板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転した状態で積層しているため、積層した状態では、壁部７１ａと壁部７２ｂとが当接し、壁部７２ａと壁部７１ｂとが当接するように構成されている。 The plate heat exchanger 3 is formed by stacking a heat transfer plate 40 and a heat transfer plate 41 having the same shape in a state of being rotated by 180 degrees with respect to an axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the stacked state, the wall portion 71a and the wall portion 72b are in contact with each other, and the wall portion 72a and the wall portion 71b are in contact with each other.
温度センサ１４は、図６に示すように、長手方向において長尺部Ｆａに対応する位置に設けられており、伝熱プレート４０の壁部７１ａに対してロウにより接合されている。さらに述べると、温度センサ１４は壁部７１ａにおける水Ｗと対向する面積よりも冷媒Ｒと対向する面積が多くなる部分に貼り付けられている。積層方向における壁部７１ａへの温度センサ１４の接合可能な幅Ｓ１は、図９に示すように、冷媒Ｒの第２流路６４の積層方向の幅Ｓ２の約二倍となるように構成されている。このため、一辺の幅が幅Ｓ１の長さとなる温度センサを壁部７１ａに貼り付けることができるため、この温度センサよりも小型の温度センサ（例えば、一辺の幅が幅Ｓ２の長さとなる温度センサ）を用いる場合よりも安価に温度検出を行うことができる。 As shown in FIG. 6, the temperature sensor 14 is provided at a position corresponding to the long portion Fa in the longitudinal direction, and is joined to the wall portion 71a of the heat transfer plate 40 by brazing. Furthermore, the temperature sensor 14 is attached to a portion of the wall portion 71a where the area facing the coolant R is larger than the area facing the water W. As shown in FIG. 9, the width S1 of the temperature sensor 14 that can be joined to the wall portion 71a in the stacking direction is configured to be approximately twice the width S2 of the second flow path 64 of the refrigerant R in the stacking direction. ing. Therefore, a temperature sensor having a width of one side having a length of the width S1 can be attached to the wall portion 71a. Therefore, a temperature sensor smaller than the temperature sensor (for example, a temperature having a width of one side having a length of the width S2) can be attached. The temperature can be detected at a lower cost than when a sensor is used.
本実施の形態では幅Ｓ１は、４ｍｍとしているが、これは、例えば３ｍｍ～７ｍｍの範囲で設定してもよい。このように壁部７１ａの突出長さを壁部７２ｂより長くする構成とすることで、一辺の幅が４ｍｍの温度センサを壁部７１ａに貼り付けることができるため、この温度センサよりも小型の温度センサを用いる場合よりも安価に温度検出を行うことができる。
なお、本実施の形態では、温度センサ１４は、幅Ｓ２に対応したものを接合しているが、複数の壁部７１ａを跨るように接合してもよい。
温度センサ１４は、本願請求項の温度検出手段に相当し、壁部７１ａは、本願請求項の温度検出手段設置部に相当する。 In the present embodiment, the width S1 is set to 4 mm, but this may be set in the range of 3 mm to 7 mm, for example. In this way, by making the projection length of the wall portion 71a longer than the wall portion 72b, a temperature sensor having a side width of 4 mm can be attached to the wall portion 71a, which is smaller than the temperature sensor. The temperature can be detected at a lower cost than when using the temperature sensor.
In addition, in the present embodiment, the temperature sensor 14 is joined to correspond to the width S2, but may be joined to span the plurality of wall portions 71a.
The temperature sensor 14 corresponds to the temperature detecting means in the claims of the present application, and the wall portion 71a corresponds to the temperature detecting means installation portion in the claims of the present application.
　次に、このように構成された室外機１の動作について説明する。
プレート式熱交換器３で水Ｗを加熱する場合には、図１に示すように、圧縮機４で冷媒Ｒを圧縮して高圧・高温のガス冷媒とし、四方弁５を介してプレート式熱交換器３の一方の冷媒配管接続口３ｃに供給する。プレート式熱交換器３では、冷媒Ｒと水Ｗとが対向流となり、冷媒Ｒと水Ｗとの間で熱交換が行われて、水Ｗが加熱される。プレート式熱交換器３の他方の冷媒配管接続口３ｄを出た液冷媒は、電子膨張弁８ｂで過冷却（サブクールをつける）されて圧力容器７に入る。さらに、電子膨張弁８ａで減圧されて二相冷媒となり、空気熱交換器６で蒸発し低圧のガス冷媒となり、四方弁５を介して吸入マフラー４ａから圧縮機４に戻る。プレート式熱交換器３で加熱された高温の水は、図示しない給湯タンク、ファンコイルユニット等に供給される。 Next, the operation of the outdoor unit 1 thus configured will be described.
When the water W is heated by the plate heat exchanger 3, as shown in FIG. 1, the refrigerant R is compressed by the compressor 4 into a high-pressure/high-temperature gas refrigerant, and the plate heat is passed through the four-way valve 5. Supply to one refrigerant pipe connection port 3c of the exchanger 3. In the plate heat exchanger 3, the refrigerant R and the water W are in counterflow, heat exchange is performed between the refrigerant R and the water W, and the water W is heated. The liquid refrigerant exiting the other refrigerant pipe connection port 3d of the plate heat exchanger 3 is supercooled (subcooled) by the electronic expansion valve 8b and enters the pressure vessel 7. Further, the pressure is reduced by the electronic expansion valve 8a to become a two-phase refrigerant, which is evaporated in the air heat exchanger 6 to become a low-pressure gas refrigerant, and returns from the suction muffler 4a to the compressor 4 via the four-way valve 5. The high-temperature water heated by the plate heat exchanger 3 is supplied to a hot water tank, a fan coil unit, etc., which are not shown.
  また、プレート式熱交換器３で水Ｗを冷却する場合は、図１に対して冷媒Ｒの流れは上記と逆方向になるように四方弁５が切り換えられる。圧縮機４で冷媒Ｒを圧縮して高圧・高温のガス冷媒とし、四方弁５を介して空気熱交換器６に供給する。空気熱交換器６を出た液冷媒は、電子膨張弁８ａで過冷却されて圧力容器７に入る。さらに、電子膨張弁８ｂで減圧されて二相冷媒となり冷媒配管接続口３ｄに供給され、プレート式熱交換器３で蒸発し低圧のガス冷媒となる。プレート式熱交換器３では、冷媒Ｒと水Ｗとが対向流となり、冷媒Ｒと水Ｗとの間で熱交換が行われて、水Ｗが冷却される。プレート式熱交換器３の冷媒配管接続口３ｃから出た低圧のガス冷媒は、四方弁５を介して吸入マフラー４ａから圧縮機４に戻る。プレート式熱交換器３で冷却された水Ｗは、例えばファンコイルユニットに供給され冷房等に利用される。 Further, when the water W is cooled by the plate heat exchanger 3, the four-way valve 5 is switched so that the flow of the refrigerant R is in the opposite direction to the above with respect to FIG. The refrigerant R is compressed by the compressor 4 into a high-pressure/high-temperature gas refrigerant, and is supplied to the air heat exchanger 6 via the four-way valve 5. The liquid refrigerant discharged from the air heat exchanger 6 is supercooled by the electronic expansion valve 8a and enters the pressure vessel 7. Further, the pressure is reduced by the electronic expansion valve 8b to become a two-phase refrigerant, which is supplied to the refrigerant pipe connection port 3d and evaporated by the plate heat exchanger 3 to become a low-pressure gas refrigerant. In the plate heat exchanger 3, the refrigerant R and the water W are in counterflow, heat exchange is performed between the refrigerant R and the water W, and the water W is cooled. The low-pressure gas refrigerant discharged from the refrigerant pipe connection port 3c of the plate heat exchanger 3 returns to the compressor 4 from the suction muffler 4a via the four-way valve 5. The water W cooled by the plate heat exchanger 3 is supplied to, for example, a fan coil unit and used for cooling or the like.
次に、プレート式熱交換器３の作用について説明する。
壁部７１ａ、７２ｂから構成される側部Ｈ１は、図１０で示す断面位置では、伝熱プレート４０の壁部７１ａ及び長尺部Ｆａとその背面側の伝熱プレート４１の凸部６２とが当接し、且つ伝熱プレート４０の長尺部Ｆａとその前面側の伝熱プレート４１の凸部６２とが離れる構成となっていることから、冷媒Ｒのみからの温度が伝達される。
一方、壁部７１ａ、７２ｂから構成される側部Ｈ１は、図９で示す断面位置では、伝熱プレート４０の長尺部Ｆａとその背面側の伝熱プレート４１の主板部７０ｂとが距離Ｋ１だけ離れた構成とされ、且つ伝熱プレート４０の長尺部Ｆａとその前面側の伝熱プレート４１の主板部７０ｂとが距離Ｋ２（Ｋ１≒Ｋ２）だけ離れた構成とされていることから、冷媒Ｒと水Ｗとの温度がほぼ同割合で伝達される。
図９及び図１０の状態を総合的に考えると、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなる。 Next, the operation of the plate heat exchanger 3 will be described.
In the side portion H1 composed of the wall portions 71a and 72b, at the cross-sectional position shown in FIG. 10, the wall portion 71a and the elongated portion Fa of the heat transfer plate 40 and the convex portion 62 of the heat transfer plate 41 on the back side thereof are formed. Since the long portion Fa of the heat transfer plate 40 is in contact with the convex portion 62 of the heat transfer plate 41 on the front side of the heat transfer plate 40, the temperature is transmitted only from the refrigerant R.
On the other hand, in the side portion H1 including the wall portions 71a and 72b, at the cross-sectional position shown in FIG. 9, the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the rear side thereof are separated by a distance K1. Since the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the front side thereof are separated by a distance K2 (K1≈K2), The temperatures of the refrigerant R and the water W are transmitted at substantially the same ratio.
Considering the states of FIG. 9 and FIG. 10 comprehensively, the side portion H1 formed of the walls 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W.
本実施の形態においては、図６、図９及び図１０に示されるように、温度センサ１４は、壁部７１ａに取り付けられている。このため、壁部７１ａに接合された温度センサ１４は、水Ｗによる影響を抑制しつつ冷媒Ｒの温度を検出することができる。
制御装置１５は、温度センサ１４で検出した温度データを読み、演算装置１７はその温度データに基づいて、プレート式熱交換器３内を流れる冷媒Ｒの温度を算出する。 In the present embodiment, as shown in FIGS. 6, 9 and 10, the temperature sensor 14 is attached to the wall 71a. Therefore, the temperature sensor 14 joined to the wall portion 71a can detect the temperature of the refrigerant R while suppressing the influence of the water W.
The controller 15 reads the temperature data detected by the temperature sensor 14, and the arithmetic unit 17 calculates the temperature of the refrigerant R flowing in the plate heat exchanger 3 based on the temperature data.
　このように、プレート式熱交換器３における温度センサ１４を接合した側の側面への温度伝達は、水Ｗと冷媒Ｒとの温度伝達が同割合ではなく、冷媒Ｒの方が水Ｗよりも温度伝達の割合が多くなるため、温度センサ１４は、冷媒Ｒの温度の検出精度を高めることができる。
加えて、温度センサ１４による冷媒Ｒの温度の検出精度が高くなることによって、室外機１は、制御装置１５による圧力飽和温度データの算出精度が高くなり、電子膨張弁８ａ、８ｂの制御精度を高めることができる。 As described above, regarding the temperature transfer to the side surface of the plate heat exchanger 3 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not the same ratio, and the refrigerant R is more than the water W. Since the rate of temperature transfer increases, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
In addition, since the temperature sensor 14 increases the detection accuracy of the temperature of the refrigerant R, the outdoor unit 1 increases the calculation accuracy of the pressure saturation temperature data by the control device 15 and improves the control accuracy of the electronic expansion valves 8a and 8b. Can be increased.
　また、図８に示すように、壁部７１ａの主板部７０ａからの突出長さＬ１を、壁部７２ａの主板部７０ａからの突出長さＬ２よりも長くなるように形成し、この結果、図９に示すように、温度センサ１４の接合可能な幅Ｓ１を、冷媒Ｒの第２流路６４の積層方向の幅Ｓ２の約二倍となるように構成した。したがって、幅Ｓ２に対応した小型の温度センサを用いる必要がなく、幅Ｓ１に対応した大きさの温度センサ１４を用いることができるため、低コストで温度検出を行うことができる。 In addition, as shown in FIG. 8, the protrusion length L1 of the wall portion 71a from the main plate portion 70a is formed to be longer than the protrusion length L2 of the wall portion 72a from the main plate portion 70a. As shown in FIG. 9, the jointable width S1 of the temperature sensor 14 is configured to be approximately twice the width S2 of the second flow path 64 of the refrigerant R in the stacking direction. Therefore, it is not necessary to use a small temperature sensor corresponding to the width S2, and the temperature sensor 14 having a size corresponding to the width S1 can be used, so that temperature detection can be performed at low cost.
伝熱プレート４０においては、凸部６１の主板部７０ａからの突出高さが、高部７５ａ、７６ａの主板部７０ａからの突出高さと同じとなるように形成されている。このため、伝熱プレート４０の凸部６１と高部７５ａ、７６ａとの両方が、伝熱プレート４０の前面側に位置する伝熱プレート４１の主板部７０ｂに対して当接するため、プレート式熱交換器３の強度を高めることができる。
また、伝熱プレート４１においては、凸部６２の主板部７０ｂからの突出高さが、高部７５ｂ、７６ｂの主板部７０ｂからの突出高さと同じとなるように形成されている。このため、伝熱プレート４１の凸部６２と高部７５ｂ、７６ｂとの両方が、伝熱プレート４１の前面側に位置する伝熱プレート４０の主板部７０ａに対して当接するため、プレート式熱交換器３の強度を高めることができる。 In the heat transfer plate 40, the protruding height of the convex portion 61 from the main plate portion 70a is the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a. Therefore, both the convex portion 61 and the high portions 75a and 76a of the heat transfer plate 40 come into contact with the main plate portion 70b of the heat transfer plate 41 located on the front surface side of the heat transfer plate 40, so that the plate type heat The strength of the exchanger 3 can be increased.
Further, in the heat transfer plate 41, the protruding height of the convex portion 62 from the main plate portion 70b is formed to be the same as the protruding height of the high portions 75b and 76b from the main plate portion 70b. Therefore, both the convex portion 62 and the high portions 75b and 76b of the heat transfer plate 41 come into contact with the main plate portion 70a of the heat transfer plate 40 located on the front surface side of the heat transfer plate 41, so that the plate type heat The strength of the exchanger 3 can be increased.
　また、プレート式熱交換器３は、図９に示すように、伝熱プレート４０と伝熱プレート４１との合計枚数が奇数となっている。そして、外側プレート４２に最も近い流路は、水Ｗが流れる第１流路６３が構成されており、かつ外側プレート４３と、その外側プレート４３に隣接した伝熱プレート４０との間を水Ｗが流れるように構成されている。そのため、プレート式熱交換器３では、冷媒Ｒと補強プレート４４、４５との間に水Ｗが介在することによって、冷媒Ｒの熱（冷気）が補強プレート４４、４５を介してプレート式熱交換器３の外に放出されることを抑制し、エネルギーロスを抑制できる。 Further, in the plate heat exchanger 3, as shown in FIG. 9, the total number of the heat transfer plates 40 and the heat transfer plates 41 is an odd number. The flow path closest to the outer plate 42 constitutes the first flow path 63 through which the water W flows, and the water W is formed between the outer plate 43 and the heat transfer plate 40 adjacent to the outer plate 43. Is configured to flow. Therefore, in the plate heat exchanger 3, the water (W) is present between the refrigerant R and the reinforcing plates 44 and 45, so that the heat (cold air) of the refrigerant R is exchanged through the reinforcing plates 44 and 45 into the plate heat exchanger. The energy loss can be suppressed by suppressing the discharge to the outside of the container 3.
実施の形態２．
　この発明の実施の形態２のプレート式熱交換器８０を備えた室外機について図１１～図１７を用いて説明する。なお、図１１～図１７中、図１～図１０と同一符号は同一又は相当部分を示す。この実施の形態２のプレート式熱交換器８０を備えた室外機は実施の形態１の伝熱プレート４０、４１の凸部６１、６２を変更したものである。 Embodiment 2.
An outdoor unit equipped with the plate heat exchanger 80 according to Embodiment 2 of the present invention will be described with reference to FIGS. 11 to 17. 11 to 17, the same reference numerals as those in FIGS. 1 to 10 denote the same or corresponding parts. The outdoor unit provided with the plate heat exchanger 80 of the second embodiment is obtained by changing the convex portions 61 and 62 of the heat transfer plates 40 and 41 of the first embodiment.
　図１１は、伝熱プレート８１、８２の正面図である。図１２は、伝熱プレート８１、８２の拡大図である。図１３の（ａ）は、伝熱プレート８１、８２を図１１のＥ－Ｅの位置から見た断面図であり、（ｂ）は、伝熱プレート８１、８２を図１１のＩ－Ｉの位置から見た断面図であり、（ｃ）は、伝熱プレート８１、８２を図１１のＪ－Ｊの位置から見た断面図であり、（ｄ）は、伝熱プレート８１、８２を図１１のＨ－Ｈの位置から見た断面図である。図１４は、プレート式熱交換器８０を図１１のＦ－Ｆの位置から見た断面図であり、図１５は、プレート式熱交換器８０を図１１のＧ－Ｇの位置から見た断面図である。図１６は、プレート式熱交換器８０を図１１のＩ－Ｉの位置から見た断面図であり、図１７は、プレート式熱交換器８０を図１１のＪ－Ｊの位置から見た断面図である。
本実施の形態のプレート式熱交換器８０（図１４、図１５参照）は、図１１及び図１３に示すように、伝熱プレート８１、８２を備えている。 FIG. 11 is a front view of the heat transfer plates 81 and 82. FIG. 12 is an enlarged view of the heat transfer plates 81 and 82. 13A is a cross-sectional view of the heat transfer plates 81 and 82 seen from the position EE of FIG. 11, and FIG. 13B is a cross-sectional view of the heat transfer plates 81 and 82 of II of FIG. FIG. 12 is a cross-sectional view seen from the position, (c) is a cross-sectional view of the heat transfer plates 81, 82 seen from the position JJ in FIG. 11, and (d) is a view showing the heat transfer plates 81, 82. 11 is a cross-sectional view as seen from the position HH of 11. 14 is a cross-sectional view of the plate heat exchanger 80 as seen from the position FF in FIG. 11, and FIG. 15 is a cross section of the plate heat exchanger 80 as seen from the position GG in FIG. It is a figure. 16 is a cross-sectional view of the plate heat exchanger 80 as seen from the position I-I of FIG. 11, and FIG. 17 is a cross-section of the plate heat exchanger 80 as seen from the position JJ of FIG. It is a figure.
The plate heat exchanger 80 (see FIGS. 14 and 15) of the present embodiment includes heat transfer plates 81 and 82 as shown in FIGS. 11 and 13.
まず、伝熱プレート８１の詳細な構成について説明する。
　伝熱プレート８１は、複数の凸部８３及び複数の凸条部８４を備えている。凸部８３及び凸条部８４は、前面側から見た場合に、略Ｖ字状に形成されている。
　複数の凸部８３は、主板部７０ａの長手方向の中央位置に形成されている。各凸部８３は、主板部７０ａの壁部７２ａ側の長辺から、壁部７１ａの長辺から所定間隔をおいた位置まで形成されている。 First, the detailed configuration of the heat transfer plate 81 will be described.
The heat transfer plate 81 includes a plurality of protrusions 83 and a plurality of protrusions 84. The convex portion 83 and the convex strip portion 84 are formed in a substantially V shape when viewed from the front side.
The plurality of convex portions 83 are formed at the central positions in the longitudinal direction of the main plate portion 70a. Each convex portion 83 is formed from a long side of the main plate portion 70a on the side of the wall portion 72a to a position spaced from the long side of the wall portion 71a by a predetermined distance.
複数の凸部８３が、主板部７０ａの壁部７１ａ側の長辺から所定間隔をおいた位置まで形成されていることにより、複数の凸部８３の壁部７１ａ側には、主板部７０ａが突出した形状を有していない長尺部Ｆｃが形成されている。すなわち、主板部７０ａの壁部７１ａ側の長辺から所定間隔をおいて形成した複数の凸部８３を、主板部７０ａの長手方向に沿って配列させて形成することにより、主板部７０ａの壁部７１ａ側の長辺側には、主板部７０ａの一部であるとともに凸部８３が形成されていない領域である長尺部Ｆｃが形成されている。 Since the plurality of convex portions 83 are formed from the long side on the wall portion 71a side of the main plate portion 70a to a position spaced by a predetermined distance, the main plate portion 70a is provided on the wall portion 71a side of the plurality of convex portions 83. A long portion Fc having no protruding shape is formed. That is, by forming a plurality of convex portions 83 formed at a predetermined interval from the long side of the main plate portion 70a on the side of the wall portion 71a so as to be arranged along the longitudinal direction of the main plate portion 70a, the wall of the main plate portion 70a is formed. A long portion Fc, which is a region that is a part of the main plate portion 70a and in which the convex portion 83 is not formed, is formed on the long side of the portion 71a side.
すなわち、凸部８３は、図１２の右側の二点鎖線で囲んで示したように主板部７０ａの壁部７２ａ側の長辺に沿って断続的に形成され、且つ、長尺部Ｆｃは、図１２の左側の二点鎖線で囲んで示したように主板部７０ａの壁部７１ａ側の長辺側に接して沿うように形成されている。 That is, the convex portion 83 is intermittently formed along the long side on the wall portion 72a side of the main plate portion 70a as shown by being surrounded by the two-dot chain line on the right side of FIG. 12, and the long portion Fc is As shown by being surrounded by a two-dot chain line on the left side of FIG. 12, the main plate portion 70a is formed so as to be in contact with the long side of the wall portion 71a of the main plate portion 70a.
　主板部７０ａには、長尺部Ｆｃにおける長手方向両側の位置に複数の凸条部８４がそれぞれ形成されている。各凸条部８４は、主板部７０ａの壁部７２ａ側の長辺から壁部７１ａの長辺まで形成されている。なお、主板部７０ａの構成要件には、凸部８３および凸条部８４を含んでいない。 The main plate portion 70a is formed with a plurality of ridges 84 at positions on both sides in the longitudinal direction of the elongated portion Fc. Each protruding portion 84 is formed from the long side of the main plate portion 70a on the side of the wall portion 72a to the long side of the wall portion 71a. The constituent features of the main plate portion 70a do not include the convex portion 83 and the convex streak portion 84.
温度センサ１４は、図１１、図１４、及び図１５に示すように、長手方向において長尺部Ｆｃに対応する位置に設けられており、伝熱プレート８１の壁部７１ａに対してロウにより接合されている。さらに述べると、温度センサ１４は壁部７１ａにおける冷媒Ｒと対向する部分に貼り付けられている。 As shown in FIGS. 11, 14, and 15, the temperature sensor 14 is provided at a position corresponding to the elongated portion Fc in the longitudinal direction, and is joined to the wall portion 71 a of the heat transfer plate 81 by brazing. Has been done. Furthermore, the temperature sensor 14 is attached to a portion of the wall portion 71a facing the refrigerant R.
次に、伝熱プレート８２の詳細な構成について説明する。
　伝熱プレート８２は、図１１及び図１３に示すように、伝熱プレート８１と同形状をなしており、カッコで示す符号が伝熱プレート８２の各部の構成に対応している。
　すなわち、伝熱プレート８２における第１開口部５４、第２開口部５５、第３開口部５６、第４開口部５７、凸部８５、凸条部８６、主板部７０ｂ、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂ、高部７５ｂ、７６ｂ、長尺部Ｆｄのそれぞれは、伝熱プレート８１における第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３、凸部８３、凸条部８４、主板部７０ａ、壁部７１ａ、７２ａ、７３ａ、７４ａ、高部７５ａ、７６ａ、長尺部Ｆｃにそれぞれ対応している。そのため、伝熱プレート８２の各部の説明は省略する。なお、主板部７０ｂの構成要件には、凸部８５および凸条部８６を含んでいない。 Next, the detailed configuration of the heat transfer plate 82 will be described.
As shown in FIGS. 11 and 13, the heat transfer plate 82 has the same shape as the heat transfer plate 81, and the reference numerals in parentheses correspond to the configuration of each part of the heat transfer plate 82.
That is, the first opening portion 54, the second opening portion 55, the third opening portion 56, the fourth opening portion 57, the protruding portion 85, the protruding portion 86, the main plate portion 70b, the wall portions 71b and 72b of the heat transfer plate 82, The first opening 50, the second opening 51, the third opening 52, the fourth opening 53, and the convex portion 83 of the heat transfer plate 81 are respectively included in the heat transfer plate 81. The ridge portion 84, the main plate portion 70a, the wall portions 71a, 72a, 73a, 74a, the high portions 75a, 76a, and the elongated portion Fc, respectively. Therefore, description of each part of the heat transfer plate 82 is omitted. The constituent requirements of the main plate portion 70b do not include the convex portion 85 and the convex streak portion 86.
　次に、伝熱プレート８１と伝熱プレート８２との接触状態を説明する。
図１４に示すように、伝熱プレート８１の主板部７０ａの長尺部Ｆｃは、背面側に位置する伝熱プレート８２の主板部７０ｂと離れて構成されている。この離れた距離を図１４では、距離Ｋ５として示している。また、伝熱プレート８１の主板部７０ａの長尺部Ｆｃは、前面側に位置する伝熱プレート８２の主板部７０ｂと離れて構成されている。この離れた距離を図１４では、距離Ｋ６として示している。プレート式熱交換器８０は、距離Ｋ５と距離Ｋ６とが、ほぼ同じになるように構成されている。 Next, the contact state between the heat transfer plate 81 and the heat transfer plate 82 will be described.
As shown in FIG. 14, the elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is separated from the main plate portion 70b of the heat transfer plate 82 located on the back side. This distance is shown as a distance K5 in FIG. The elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is separated from the main plate portion 70b of the heat transfer plate 82 located on the front surface side. This separated distance is shown as a distance K6 in FIG. The plate heat exchanger 80 is configured such that the distance K5 and the distance K6 are substantially the same.
図１４に示すように、伝熱プレート８２の主板部７０ｂの長尺部Ｆｄは、背面側に位置する伝熱プレート８１の主板部７０ａと離れて構成されている。この離れた距離を図１４では、距離Ｋ７として示している。また、伝熱プレート８２の主板部７０ｂの長尺部Ｆｄは、前面側に位置する伝熱プレート８１の主板部７０ａと離れて構成されている。この離れた距離を図１４では、距離Ｋ８として示している。プレート式熱交換器８０は、距離Ｋ７と距離Ｋ８とが、ほぼ同じになるように構成されている。 As shown in FIG. 14, the elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is separated from the main plate portion 70a of the heat transfer plate 81 located on the rear surface side. This distance is shown as a distance K7 in FIG. The elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is formed separately from the main plate portion 70a of the heat transfer plate 81 located on the front surface side. This separated distance is shown as a distance K8 in FIG. The plate heat exchanger 80 is configured such that the distance K7 and the distance K8 are substantially the same.
　図１５に示すように、伝熱プレート８１の凸部８３は、伝熱プレート８２の壁部７１ｂ及び長尺部Ｆｄに当接するように構成されている。このため、図１５の断面位置においては、壁部７１ｂ、７２ａからなる側部Ｈ２には、冷媒Ｒが接触することなく、水Ｗのみが接触する。すなわち、伝熱プレート８１の凸部８３は、その凸部８３が突出する側の隣で対向する伝熱プレート８２の壁部７１ｂに当接されている。また、伝熱プレート８２の主板部７０ｂの長尺部Ｆｄは、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣に位置する伝熱プレート８１の凸部８３と当接されている。 As shown in FIG. 15, the convex portion 83 of the heat transfer plate 81 is configured to come into contact with the wall portion 71b and the elongated portion Fd of the heat transfer plate 82. Therefore, at the cross-sectional position of FIG. 15, only the water W comes into contact with the side portion H2 formed of the wall portions 71b and 72a without coming into contact with the refrigerant R. That is, the convex portion 83 of the heat transfer plate 81 is in contact with the wall portion 71b of the heat transfer plate 82 that is adjacent to and on the side where the convex portion 83 protrudes. The elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is in contact with the convex portion 83 of the heat transfer plate 81 located next to the side where the walls 71b, 72b, 73b, 74b project.
一方、伝熱プレート８２の主板部７０ｂの長尺部Ｆｄは、前面側に位置する伝熱プレート８１の凸部８３と離れて構成されている。
すなわち、伝熱プレート８２の長尺部Ｆｄを基準として、長尺部Ｆｄから壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣で対向する伝熱プレート８１の凸部８３までの距離は、長尺部Ｆｄから凸部８５が突出する側の隣で対向する伝熱プレート８１の凸部８３までの距離よりも小さくなるように構成されている。 On the other hand, the elongated portion Fd of the main plate portion 70b of the heat transfer plate 82 is formed apart from the convex portion 83 of the heat transfer plate 81 located on the front surface side.
That is, with reference to the elongated portion Fd of the heat transfer plate 82, the distance from the elongated portion Fd to the convex portion 83 of the heat transfer plate 81 that is adjacent and adjacent to the side where the walls 71b, 72b, 73b, 74b project is determined. The distance is smaller than the distance from the long portion Fd to the convex portion 83 of the heat transfer plate 81 that is adjacent and opposite to the side where the convex portion 85 projects.
図１５に示すように、伝熱プレート８２の凸部８５は、伝熱プレート８１の壁部７１ａ及び長尺部Ｆｃに当接するように構成されている。このため、図１５の断面位置においては、壁部７１ａ、７２ｂからなる側部Ｈ１には、水Ｗが接触することなく、冷媒Ｒのみが接触する。すなわち、伝熱プレート８２の凸部８５は、その凸部８５が突出する側の隣で対向する伝熱プレート８１の壁部７１ａに当接されている。また、伝熱プレート８１の主板部７０ａの長尺部Ｆｃは、壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣に位置する伝熱プレート８２の凸部８５と当接されている。 As shown in FIG. 15, the convex portion 85 of the heat transfer plate 82 is configured to come into contact with the wall portion 71 a and the elongated portion Fc of the heat transfer plate 81. Therefore, at the cross-sectional position of FIG. 15, only the refrigerant R comes into contact with the side portion H1 including the walls 71a and 72b without coming into contact with the water W. That is, the convex portion 85 of the heat transfer plate 82 is in contact with the wall portion 71a of the heat transfer plate 81 that is adjacent to and on the side where the convex portion 85 protrudes. The elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is in contact with the convex portion 85 of the heat transfer plate 82 located next to the side where the walls 71a, 72a, 73a, 74a project.
一方、伝熱プレート８１の主板部７０ａの長尺部Ｆｃは、前面側に位置する伝熱プレート８２の凸部８５と離れて構成されている。
すなわち、伝熱プレート８１の長尺部Ｆｃを基準として、長尺部Ｆｃから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート８２の凸部８５までの距離は、長尺部Ｆｃから凸部８３が突出する側の隣で対向する伝熱プレート８２の凸部８５までの距離よりも小さくなるように構成されている。 On the other hand, the elongated portion Fc of the main plate portion 70a of the heat transfer plate 81 is formed separately from the convex portion 85 of the heat transfer plate 82 located on the front surface side.
That is, based on the elongated portion Fc of the heat transfer plate 81, the distance from the elongated portion Fc to the convex portion 85 of the heat transfer plate 82 that is adjacent and adjacent to the side on which the walls 71a, 72a, 73a, and 74a protrude. The distance is smaller than the distance from the elongated portion Fc to the convex portion 85 of the heat transfer plate 82 that is adjacent and adjacent to the protruding side of the convex portion 83.
　図１４及び図１６の断面位置では、凸部８３及び凸条部８４は、その前面側に位置する伝熱プレート８２の主板部７０ｂに対して当接していないが、断面位置によっては当接するように構成されている。同様に、図１４及び図１６の断面位置では、凸部８５及び凸条部８６は、その前面側に位置する伝熱プレート８１の主板部７０ａに対して当接していないが、断面位置によっては当接するように構成されている。
また、図示はしないが、高部７５ａ、７６ａは、その前面側に位置する伝熱プレート８２の主板部７０ａに対して当接するように構成され、高部７５ｂ、７６ｂは、その前面側に位置する伝熱プレート８１の主板部７０ａに対して当接するように構成されている。 At the cross-sectional position of FIGS. 14 and 16, the convex portion 83 and the convex strip portion 84 do not abut on the main plate portion 70b of the heat transfer plate 82 located on the front surface side thereof, but they may abut on the cross-sectional position. Is configured. Similarly, at the cross-sectional positions of FIGS. 14 and 16, the convex portion 85 and the convex streak portion 86 are not in contact with the main plate portion 70a of the heat transfer plate 81 located on the front side thereof, but depending on the cross-sectional position. It is configured to abut.
Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70a of the heat transfer plate 82 located on the front side thereof, and the high portions 75b and 76b are located on the front side thereof. The heat transfer plate 81 is configured to come into contact with the main plate portion 70a.
　このように構成されたプレート式熱交換器８０を備えた室外機においても、実施の形態１の室外機１と同様の動作を奏する。
　また、第２の実施の形態では、第１の実施の形態と同様の効果を奏するとともに、以下の効果を奏する。
　長手方向における温度センサ１４が設けられていない位置では、図１６、図１７で示すように、凸条部８４、８６は、短手方向の全域にわたって形成されているため、この部分での熱交換効率を、凸部８３、８５部分に比して高めることができる。 The outdoor unit including the plate heat exchanger 80 configured in this manner also performs the same operation as the outdoor unit 1 of the first embodiment.
In addition, the second embodiment has the same effects as those of the first embodiment, and also has the following effects.
At the position where the temperature sensor 14 is not provided in the longitudinal direction, as shown in FIGS. 16 and 17, since the ridges 84 and 86 are formed over the entire area in the lateral direction, heat exchange in this portion is performed. The efficiency can be increased as compared with the convex portions 83 and 85.
実施の形態３．
　この発明の実施の形態３のプレート式熱交換器９０を備えた室外機について図１８～図２１を用いて説明する。なお、図１８～図２１中、図１～図１０と同一符号は同一又は相当部分を示す。この実施の形態３のプレート式熱交換器９０を備えた室外機は実施の形態１の伝熱プレート４０、４１の凸部６１、６２の形状を一部変更し、かつ凸部９３、９４を追加したものである。 Embodiment 3.
An outdoor unit equipped with the plate heat exchanger 90 according to Embodiment 3 of the present invention will be described with reference to FIGS. 18 to 21. 18 to 21, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding portions. The outdoor unit including the plate heat exchanger 90 according to the third embodiment partially changes the shapes of the convex portions 61 and 62 of the heat transfer plates 40 and 41 according to the first embodiment, and has the convex portions 93 and 94. It was added.
図１８は、伝熱プレート９１、９２の正面図である。図１９の（ａ）は、伝熱プレート９１、９２を図１８のＫ－Ｋの位置から見た断面図であり、（ｂ）は、伝熱プレート９１、９２を図１８のＬ－Ｌの位置から見た断面図であり、（ｃ）は、伝熱プレート９１、９２を図１８のＭ－Ｍの位置から見た断面図であり、（ｄ）は、伝熱プレート９１、９２を図１８のＮ－Ｎの位置から見た断面図である。図２０は、プレート式熱交換器９０を図１８のＬ－Ｌの位置から見た断面図であり、図２１は、プレート式熱交換器９０を図１８のＭ－Ｍの位置から見た断面図である。 FIG. 18 is a front view of the heat transfer plates 91 and 92. 19A is a cross-sectional view of the heat transfer plates 91 and 92 seen from the position KK of FIG. 18, and FIG. 19B is a cross-sectional view of the heat transfer plates 91 and 92 of LL of FIG. 19 is a cross-sectional view seen from the position, FIG. 19C is a cross-sectional view of the heat transfer plates 91 and 92 seen from the position MM in FIG. 18, and FIG. 19D is a cross-sectional view of the heat transfer plates 91 and 92. FIG. 18 is a cross-sectional view seen from the position NN of 18. 20 is a sectional view of the plate heat exchanger 90 seen from the position LL in FIG. 18, and FIG. 21 is a sectional view of the plate heat exchanger 90 seen from the position MM in FIG. It is a figure.
本実施の形態のプレート式熱交換器９０（図２０、図２１参照）は、図１８、図１９に示すように、伝熱プレート９１、９２を備えている。
まず、伝熱プレート９１の詳細な構成について説明する。
伝熱プレート９１には、主板部７０ａの壁部７２ａ側に近接して凸部９３が形成されている。凸部９３は、長手方向に沿って延びるように形成されている。凸部９３は、先端面９３ａが平面となるように形成されており、その平面は、凸部６１の頂点と同じ高さになるように形成されている。凸部９３は、主板部７０ａから突出するように形成されており、板材をプレス加工することによって形成されている。
主板部７０ａの壁部７２ａ側の長辺から長尺部Ｆａまで形成されている複数の凸部６１は、主板部７０ａの壁部７２ａ側の長辺に沿って連続的に形成された凸部９３に連続して形成されている。なお、主板部７０ａの構成要件には、凸部６１、９３を含んでいない。 The plate heat exchanger 90 (see FIGS. 20 and 21) of the present embodiment includes heat transfer plates 91 and 92, as shown in FIGS. 18 and 19.
First, the detailed configuration of the heat transfer plate 91 will be described.
A convex portion 93 is formed on the heat transfer plate 91 close to the wall portion 72a side of the main plate portion 70a. The convex portion 93 is formed so as to extend along the longitudinal direction. The convex portion 93 is formed such that the tip end surface 93 a is a flat surface, and the flat surface is formed to have the same height as the apex of the convex portion 61. The convex portion 93 is formed so as to protrude from the main plate portion 70a, and is formed by pressing a plate material.
The plurality of convex portions 61 formed from the long side on the wall portion 72a side of the main plate portion 70a to the long portion Fa is a convex portion formed continuously along the long side on the wall portion 72a side of the main plate portion 70a. It is formed continuously at 93. The constituent requirements of the main plate portion 70a do not include the convex portions 61 and 93.
本実施形態では、凸部９３の短手方向長さを１．７５ｍｍとしている。凸部９３の短手方向長さと主板部７０ａの短手方向長さの比は、「１．２：１００～４：１００」が望ましく、本実施の形態では、「２：１００」としている。凸部９３の短手方向長さと主板部７０ａの短手方向長さの比を「１．２：１００～４：１００」とすることで、後述する前面側の長尺部Ｆｂとの当接状態を好適に維持でき、かつ、主板部７０ａ上に凸部９３を構成させる面積を極力少なくすることが可能となる。また、凸部９３の短手方向長さと主板部７０ａの短手方向長さの比を「２：１００」とすることで、後述する前面側の長尺部Ｆｂとの当接状態をよりいっそう好適に維持でき、かつ、主板部７０ａ上に凸部９３を構成させる面積を極力少なくすることが可能となる。 In this embodiment, the lateral length of the convex portion 93 is 1.75 mm. The ratio of the short-side length of the convex portion 93 to the short-side length of the main plate portion 70a is preferably “1.2:100 to 4:100”, and is “2:100” in the present embodiment. By setting the ratio of the short-side length of the convex portion 93 and the short-side length of the main plate portion 70a to "1.2:100 to 4:100", the contact with the long-side portion Fb on the front surface side described later. The state can be preferably maintained, and the area for forming the convex portion 93 on the main plate portion 70a can be reduced as much as possible. Further, by setting the ratio of the short-side length of the convex portion 93 and the short-side length of the main plate portion 70a to “2:100”, the contact state with the long-side portion Fb on the front surface side, which will be described later, is further improved. It is possible to maintain it suitably, and it is possible to reduce the area where the convex portion 93 is formed on the main plate portion 70a as much as possible.
次に、伝熱プレート９２の詳細な構成について説明する。
　伝熱プレート９２は、図１８、図１９に示すように、伝熱プレート９１と同形状をなしており、カッコで示す符号が伝熱プレート９２の各部の構成に対応している。
　すなわち、伝熱プレート９２における第１開口部５４、第２開口部５５、第３開口部５６、第４開口部５７、凸部６２、主板部７０ｂ、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂ、高部７５ｂ、７６ｂ、凸部９４、先端面９４ａ、長尺部Ｆｂのそれぞれは、伝熱プレート９１における第１開口部５０、第２開口部５１、第３開口部５２、第４開口部５３、凸部６１、主板部７０ａ、壁部７１ａ、７２ａ、７３ａ、７４ａ、高部７５ａ、７６ａ、凸部９３、先端面９３ａ、長尺部Ｆａにそれぞれ対応している。そのため、伝熱プレート９２の各部の説明は省略する。なお、主板部７０ｂの構成要件には、凸部６２、９４を含んでいない。 Next, the detailed configuration of the heat transfer plate 92 will be described.
As shown in FIGS. 18 and 19, the heat transfer plate 92 has the same shape as the heat transfer plate 91, and the reference numerals in parentheses correspond to the configurations of the respective parts of the heat transfer plate 92.
That is, the first opening portion 54, the second opening portion 55, the third opening portion 56, the fourth opening portion 57, the convex portion 62, the main plate portion 70b, the wall portions 71b, 72b, 73b and 74b, and the height of the heat transfer plate 92 are high. Each of the portions 75b and 76b, the convex portion 94, the tip surface 94a, and the elongated portion Fb has a first opening portion 50, a second opening portion 51, a third opening portion 52, a fourth opening portion 53 in the heat transfer plate 91. It corresponds to the convex portion 61, the main plate portion 70a, the wall portions 71a, 72a, 73a, 74a, the high portions 75a, 76a, the convex portion 93, the tip surface 93a, and the long portion Fa, respectively. Therefore, description of each part of the heat transfer plate 92 is omitted. The constituent requirements of the main plate portion 70b do not include the convex portions 62 and 94.
　次に、伝熱プレート９１と伝熱プレート９２との接触状態を説明する。
図２０及び図２１に示すように、伝熱プレート９１の凸部９３は、伝熱プレート９２の壁部７１ｂ及び長尺部Ｆｂに当接するように構成されている。このため、図２０及び図２１の断面位置においては、壁部７１ｂ、７２ａからなる側部Ｈ２には、冷媒Ｒが接触することなく、水Ｗのみが接触する。すなわち、伝熱プレート９１の凸部９３は、その凸部９３が突出する側の隣で対向する伝熱プレート９２の壁部７１ｂに当接されている。また、伝熱プレート９２の主板部７０ｂの長尺部Ｆｂは、壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣に位置する伝熱プレート９１の凸部９３と当接されている。 Next, a contact state between the heat transfer plate 91 and the heat transfer plate 92 will be described.
As shown in FIGS. 20 and 21, the convex portion 93 of the heat transfer plate 91 is configured to come into contact with the wall portion 71 b and the elongated portion Fb of the heat transfer plate 92. Therefore, at the cross-sectional positions of FIGS. 20 and 21, only the water W comes into contact with the side portion H2 including the wall portions 71b and 72a without coming into contact with the refrigerant R. That is, the convex portion 93 of the heat transfer plate 91 is in contact with the wall portion 71 b of the heat transfer plate 92 that is adjacent and adjacent to the side where the convex portion 93 projects. The elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 is in contact with the convex portion 93 of the heat transfer plate 91 located next to the side where the walls 71b, 72b, 73b, 74b project.
一方、伝熱プレート９２の主板部７０ｂの長尺部Ｆｂは、前面側に位置する伝熱プレート９１の凸部９３と離れて構成されている。
すなわち、伝熱プレート９２の長尺部Ｆｂを基準として、長尺部Ｆｂから壁部７１ｂ、７２ｂ、７３ｂ、７４ｂが突出する側の隣で対向する伝熱プレート９１の凸部９３までの距離は、長尺部Ｆｂから凸部９４が突出する側の隣で対向する伝熱プレート９１の凸部９３までの距離よりも小さくなるように構成されている。 On the other hand, the elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 is formed separately from the convex portion 93 of the heat transfer plate 91 located on the front surface side.
That is, with reference to the long portion Fb of the heat transfer plate 92, the distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 that is adjacent and adjacent to the side on which the walls 71b, 72b, 73b, and 74b project is determined. The distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 that is adjacent and adjacent to the side where the convex portion 94 projects is smaller than the distance.
図２０及び図２１に示すように、伝熱プレート９２の凸部９４は、伝熱プレート９１の壁部７１ａ及び長尺部Ｆａに当接するように構成されている。このため、図２０及び図２１の断面位置においては、壁部７１ａ、７２ｂからなる側部Ｈ１には、水Ｗが接触することなく、冷媒Ｒのみが接触する。すなわち、伝熱プレート９２の凸部９４は、その凸部９３が突出する側の隣で対向する伝熱プレート９１の壁部７１ａに当接されている。また、伝熱プレート９１の主板部７０ａの長尺部Ｆａは、壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣に位置する伝熱プレート９２の凸部９４と当接されている。 As shown in FIGS. 20 and 21, the convex portion 94 of the heat transfer plate 92 is configured to come into contact with the wall portion 71 a and the elongated portion Fa of the heat transfer plate 91. Therefore, at the cross-sectional positions of FIGS. 20 and 21, only the refrigerant R comes into contact with the side portion H1 including the wall portions 71a and 72b without coming into contact with the water W. That is, the convex portion 94 of the heat transfer plate 92 is in contact with the wall portion 71a of the heat transfer plate 91 that is adjacent to and opposes the side on which the convex portion 93 projects. Further, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 is in contact with the convex portion 94 of the heat transfer plate 92 located next to the side where the walls 71a, 72a, 73a, 74a project.
一方、伝熱プレート９１の主板部７０ａの長尺部Ｆａは、前面側に位置する伝熱プレート９２の凸部９４と離れて構成されている。
すなわち、伝熱プレート９１の長尺部Ｆａを基準として、長尺部Ｆａから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離は、長尺部Ｆａから凸部９３が突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離よりも小さくなるように構成されている。 On the other hand, the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 is formed separately from the convex portion 94 of the heat transfer plate 92 located on the front surface side.
That is, with reference to the long portion Fa of the heat transfer plate 91, the distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the wall portions 71a, 72a, 73a, and 74a protrude. The distance is smaller than the distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the convex portion 93 projects.
　図２０及び図２１の断面位置では、凸部６１は、その前面側に位置する伝熱プレート９２の主板部７０ｂに対して当接していないが、断面位置によっては当接するように構成されている。同様に、図２０及び図２１の断面位置では、凸部６２は、その前面側に位置する伝熱プレート９１の主板部７０ａに対して当接していないが、断面位置によっては当接するように構成されている。 20 and 21, the convex portion 61 is not in contact with the main plate portion 70b of the heat transfer plate 92 located on the front surface side, but is configured to be in contact with the main plate portion 70b depending on the sectional position. .. Similarly, at the cross-sectional positions of FIGS. 20 and 21, the convex portion 62 is not in contact with the main plate portion 70a of the heat transfer plate 91 located on the front side thereof, but is configured to be in contact with the main plate portion 70a depending on the cross-sectional position. Has been done.
また、図示はしないが、高部７５ａ、７６ａは、その前面側に位置する伝熱プレート９２の主板部７０ｂに対して当接するように構成され、高部７５ｂ、７６ｂは、その前面側に位置する伝熱プレート９１の主板部７０ａに対して当接するように構成されている。
　加えて、図２０及び図２１の断面位置では、伝熱プレート９１の凸部９３は、その前面側に位置する伝熱プレート９２の主板部７０ｂにおける長尺部Ｆｂに対して当接し、伝熱プレート９２の凸部９４は、その前面側に位置する伝熱プレート９１の主板部７０ａにおける長尺部Ｆａに対して当接している。伝熱プレート９１は伝熱プレート９２を主板部７０ａ、７０ｂの板状面の中心から垂直に延びる軸Ｚを基準に１８０度回転して積層されているので、このように当接する。 Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70b of the heat transfer plate 92 located on the front side thereof, and the high portions 75b and 76b are located on the front side thereof. The heat transfer plate 91 is configured to come into contact with the main plate portion 70a.
In addition, at the cross-sectional positions of FIGS. 20 and 21, the convex portion 93 of the heat transfer plate 91 abuts against the elongated portion Fb of the main plate portion 70b of the heat transfer plate 92 located on the front side thereof, and heat transfer is performed. The convex portion 94 of the plate 92 is in contact with the elongated portion Fa of the main plate portion 70a of the heat transfer plate 91 located on the front side thereof. Since the heat transfer plate 91 is laminated by rotating the heat transfer plate 92 by 180 degrees with respect to the axis Z extending perpendicularly from the center of the plate-shaped surfaces of the main plate portions 70a and 70b, the heat transfer plate 92 abuts in this manner.
　このように構成されたプレート式熱交換器９０を備えた室外機においても、実施の形態１の室外機１と同様の動作を奏する。
　また、第３の実施の形態では、第１の実施の形態と同様の効果を奏するとともに、以下の効果を奏する。 The outdoor unit including the plate heat exchanger 90 configured in this manner also performs the same operation as the outdoor unit 1 of the first embodiment.
In addition, the third embodiment has the same effects as those of the first embodiment, and also has the following effects.
壁部７１ａ、７２ｂから構成される側部Ｈ１は、図２０で示す断面位置では、伝熱プレート９１の壁部７１ａ及び長尺部Ｆａとその背面側の伝熱プレート９２の凸部９４とが当接し、且つ伝熱プレート９１の長尺部Ｆａとその前面側の伝熱プレート９２の凸部９４とが離れる構成となっていることから、冷媒Ｒのみからの温度が伝達される。
同様に、壁部７１ａ、７２ｂから構成される側部Ｈ１は、図２１で示す断面位置においても、伝熱プレート９１の壁部７１ａ及び長尺部Ｆａとその背面側の伝熱プレート９２の凸部９４とが当接し、且つ伝熱プレート９１の長尺部Ｆａとその前面側の伝熱プレート９２の凸部９４とが離れる構成となっていることから、冷媒Ｒのみからの温度が伝達される。 At the cross-sectional position shown in FIG. 20, the side portion H1 including the wall portions 71a and 72b has the wall portion 71a and the elongated portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the back side thereof. Since the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front surface thereof are in contact with each other and separated from each other, the temperature from only the refrigerant R is transmitted.
Similarly, the side portion H1 composed of the wall portions 71a and 72b has the convex portion of the wall portion 71a and the elongated portion Fa of the heat transfer plate 91 and the heat transfer plate 92 on the rear side thereof even at the cross-sectional position shown in FIG. Since the portion 94 abuts and the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front side thereof are separated from each other, the temperature from only the refrigerant R is transmitted. It
　図２０及び図２１の状態を総合的に考えると、壁部７１ａに接合された温度センサ１４が検出する温度は、冷媒Ｒに基づく温度によるものとなり、実施の形態１温度センサ１４よりも精度よくプレート式熱交換器３内を流れる冷媒Ｒの温度を検出ことができる。
　このため、第３の実施の形態の制御装置１５は、第１の実施の形態の制御装置１５に比して、プレート式熱交換器３内を流れる冷媒Ｒの温度を精度よく算出することができる。 Considering the states of FIG. 20 and FIG. 21 comprehensively, the temperature detected by the temperature sensor 14 joined to the wall portion 71a depends on the temperature based on the refrigerant R, and is more accurate than the temperature sensor 14 of the first embodiment. The temperature of the refrigerant R flowing through the plate heat exchanger 3 can be detected.
Therefore, the control device 15 of the third embodiment can calculate the temperature of the refrigerant R flowing in the plate heat exchanger 3 more accurately than the control device 15 of the first embodiment. it can.
実施の形態４．
　この発明の実施の形態４のプレート式熱交換器１００を備えた室外機について図２２を用いて説明する。なお、図２２中、図１～図１０と同一符号は同一又は相当部分を示す。この実施の形態４のプレート式熱交換器１００を備えた室外機は実施の形態１の伝熱プレート４０、４１の凸部６１、６２の高さを実施の形態１よりも低くしたものである。
　図２２に示すように、伝熱プレート４０の凸部６１は、伝熱プレート４１の壁部７１ｂに当接するように構成され、伝熱プレート４１の長尺部Ｆｂとは間隔をおいて構成されている。また、伝熱プレート４１の凸部６２は、伝熱プレート４０の壁部７１ａに当接するように構成され、伝熱プレート４０の長尺部Ｆａとは間隔をおいて構成されている。 Fourth Embodiment
An outdoor unit equipped with the plate heat exchanger 100 according to Embodiment 4 of the present invention will be described with reference to FIG. 22, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding parts. The outdoor unit provided with the plate heat exchanger 100 of the fourth embodiment is one in which the heights of the convex portions 61, 62 of the heat transfer plates 40, 41 of the first embodiment are lower than those of the first embodiment. ..
As shown in FIG. 22, the convex portion 61 of the heat transfer plate 40 is configured to abut against the wall portion 71b of the heat transfer plate 41, and is spaced apart from the long portion Fb of the heat transfer plate 41. ing. Further, the convex portion 62 of the heat transfer plate 41 is configured to come into contact with the wall portion 71 a of the heat transfer plate 40, and is spaced apart from the long portion Fa of the heat transfer plate 40.
伝熱プレート４０の長尺部Ｆａを基準として、長尺部Ｆａから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート４１の凸部６２までの距離Ｋ９は、長尺部Ｆａから凸部６１が突出する側の隣で対向する伝熱プレート４１の凸部６２までの距離Ｋ１０よりも小さくなるように構成されている。
このため、図２２の断面位置においては、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなる。
　従って、プレート式熱交換器１００における温度センサ１４を接合した側の側面への温度伝達は、水Ｗと冷媒Ｒとの温度伝達が同割合ではなく、冷媒Ｒの方が水Ｗよりも温度伝達の割合が多くなるため、温度センサ１４は、冷媒Ｒの温度の検出精度を高めることができる。 With reference to the long portion Fa of the heat transfer plate 40, the distance K9 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and adjacent to the side where the walls 71a, 72a, 73a, and 74a project is: It is configured to be smaller than the distance K10 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 that is adjacent and opposite to the side where the convex portion 61 projects.
Therefore, at the cross-sectional position in FIG. 22, the side surface H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than with the water W.
Therefore, regarding the temperature transfer to the side surface of the plate heat exchanger 100 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not at the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
実施の形態５．
　この発明の実施の形態５のプレート式熱交換器１１０を備えた室外機について図２３及び図２４を用いて説明する。なお、図２３及び図２４中、図１８～図２１と同一符号は同一又は相当部分を示す。この実施の形態５のプレート式熱交換器１１０を備えた室外機は実施の形態３の伝熱プレート９１、９２の凸部６１、６２、９３、９４の高さを実施の形態３よりも低くしたものである。
　図２３及び図２４に示すように、伝熱プレート９１の凸部９３は、伝熱プレート９２の壁部７１ｂに当接するように構成され、伝熱プレート９２の長尺部Ｆｂとは間隔をおいて構成されている。伝熱プレート９２の凸部９４は、伝熱プレート９１の壁部７１ａに当接するように構成され、伝熱プレート９１の長尺部Ｆａとは間隔をおいて構成されている。 Embodiment 5.
An outdoor unit including the plate heat exchanger 110 according to the fifth embodiment of the present invention will be described with reference to FIGS. 23 and 24. 23 and 24, the same reference numerals as those in FIGS. 18 to 21 indicate the same or corresponding portions. The outdoor unit equipped with the plate heat exchanger 110 of the fifth embodiment has the height of the convex portions 61, 62, 93, 94 of the heat transfer plates 91, 92 of the third embodiment lower than that of the third embodiment. It was done.
As shown in FIGS. 23 and 24, the convex portion 93 of the heat transfer plate 91 is configured to contact the wall portion 71b of the heat transfer plate 92, and is spaced from the long portion Fb of the heat transfer plate 92. It is configured. The convex portion 94 of the heat transfer plate 92 is configured to come into contact with the wall portion 71a of the heat transfer plate 91, and is spaced apart from the long portion Fa of the heat transfer plate 91.
　図２３は、図１８のＬ－Ｌの位置に対応したプレート式熱交換器１１０の断面図であるが、伝熱プレート９１の長尺部Ｆａを基準として、長尺部Ｆａから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離Ｋ１１は、長尺部Ｆａから凸部９３が突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離Ｋ１２よりも小さくなるように構成されている。
また、図２４は、図１８のＭ－Ｍの位置に対応したプレート式熱交換器１１０の断面図であるが、伝熱プレート９１の長尺部Ｆａを基準として、長尺部Ｆａから壁部７１ａ、７２ａ、７３ａ、７４ａが突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離Ｋ１３は、長尺部Ｆａから凸部９３が突出する側の隣で対向する伝熱プレート９２の凸部９４までの距離Ｋ１４よりも小さくなるように構成されている。 FIG. 23 is a cross-sectional view of the plate heat exchanger 110 corresponding to the position LL in FIG. 18, but with the elongated portion Fa of the heat transfer plate 91 as a reference, the elongated portion Fa to the wall portion 71a, The distance K11 to the convex portion 94 of the heat transfer plate 92, which is adjacent to and opposes the side on which the protrusions 72a, 73a, and 74a are projected, is the same as the distance K11 of the heat transfer plate 92 that is adjacent and adjacent to the side on which the convex portion 93 projects from the long portion Fa. It is configured to be smaller than the distance K12 to the convex portion 94.
FIG. 24 is a cross-sectional view of the plate heat exchanger 110 corresponding to the position MM in FIG. 18, but with the long portion Fa of the heat transfer plate 91 as a reference, the long portion Fa to the wall portion is used. The distance K13 to the convex portion 94 of the heat transfer plate 92 that is adjacent and is opposed to the side on which the protruding portions 71a, 72a, 73a, and 74a are adjacent is the heat transfer plate that is adjacent and that is adjacent to the side on which the convex portion 93 is protruded from the long portion Fa. It is configured to be smaller than the distance K14 to the convex portion 94 of 92.
このため、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなる。
　従って、プレート式熱交換器１１０における温度センサ１４を接合した側の側面への温度伝達は、水Ｗと冷媒Ｒとの温度伝達が同割合ではなく、冷媒Ｒの方が水Ｗよりも温度伝達の割合が多くなるため、温度センサ１４は、冷媒Ｒの温度の検出精度を高めることができる。 Therefore, the side portion H1 including the wall portions 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W.
Therefore, regarding the temperature transfer to the side surface of the plate heat exchanger 110 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
実施の形態６．
　この発明の実施の形態６のプレート式熱交換器１２０を備えた室外機について図２５を用いて説明する。なお、図２５中、図１～図１０と同一符号は同一又は相当部分を示す。実施の形態１の凸部６１、６２が伝熱プレート４０、４１をプレス加工して成形されていたのに対し、この実施の形態６のプレート式熱交換器１２０を備えた室外機は、凸部１２１、１２２を伝熱プレート４０、４１とは別体で形成したものである。
　図２５に示すように、伝熱プレート４０の主板部７０ａの長尺部Ｆａを除いた部位には、複数の凸部１２１が取り付けられている。また、伝熱プレート４１の主板部７０ｂの長尺部Ｆｂを除いた部位には、複数の凸部１２２が取り付けられている。伝熱プレート４０の凸部１２１のいくつかは、伝熱プレート４１の壁部７１ｂ及び長尺部Ｆｂに当接するように構成されている。また、伝熱プレート４１の凸部１２２のいくつかは、伝熱プレート４０の壁部７１ａ及び長尺部Ｆａに当接するように構成されている。 Sixth Embodiment
An outdoor unit including a plate heat exchanger 120 according to Embodiment 6 of the present invention will be described with reference to FIG. Note that, in FIG. 25, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding portions. While the convex portions 61 and 62 of the first embodiment are formed by pressing the heat transfer plates 40 and 41, the outdoor unit including the plate heat exchanger 120 of the sixth embodiment has a convex shape. The parts 121 and 122 are formed separately from the heat transfer plates 40 and 41.
As shown in FIG. 25, a plurality of convex portions 121 are attached to a portion of the main plate portion 70a of the heat transfer plate 40 excluding the long portion Fa. In addition, a plurality of convex portions 122 are attached to the main plate portion 70b of the heat transfer plate 41 excluding the elongated portion Fb. Some of the convex portions 121 of the heat transfer plate 40 are configured to come into contact with the wall portion 71b and the elongated portion Fb of the heat transfer plate 41. Further, some of the convex portions 122 of the heat transfer plate 41 are configured to abut on the wall portion 71 a and the elongated portion Fa of the heat transfer plate 40.
このため、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなる。
　従って、プレート式熱交換器１２０における温度センサ１４を接合した側の側面への温度伝達は、水Ｗと冷媒Ｒとの温度伝達が同割合ではなく、冷媒Ｒの方が水Ｗよりも温度伝達の割合が多くなるため、温度センサ１４は、冷媒Ｒの温度の検出精度を高めることができる。
　なお、実施の形態６では、凸部１２１、１２２を伝熱プレート４０、４１とは別体で形成したが、凸部１２１を伝熱プレート４０と一体に、さらには凸部１２２を伝熱プレート４１と一体に構成してもよい。このように構成しても、同様の効果を奏する。 Therefore, the side portion H1 including the wall portions 71a and 72b has a larger contact area with the refrigerant R than a contact area with the water W.
Therefore, regarding the temperature transfer to the side surface of the plate heat exchanger 120 on the side where the temperature sensor 14 is joined, the temperature transfer between the water W and the refrigerant R is not the same ratio, and the temperature transfer between the refrigerant R and the water W is higher. Therefore, the temperature sensor 14 can improve the detection accuracy of the temperature of the refrigerant R.
Although the convex portions 121 and 122 are formed separately from the heat transfer plates 40 and 41 in the sixth embodiment, the convex portion 121 is integrated with the heat transfer plate 40, and the convex portion 122 is further connected to the heat transfer plate. It may be integrated with 41. Even with this structure, the same effect can be obtained.
　なお、第２の実施の形態に対して、第３の実施の形態の凸部９３、９４を設けるように構成してもよい。このように構成すると、長手方向における温度センサ１４が設けられていない位置では、凸条部８４、８６は、短手方向の全域にわたって形成されているため、この部分での熱交換効率を、凸部８３、８５部分に比して高めることができる。加えて、壁部７１ａに接合された温度センサ１４が検出する温度は、冷媒Ｒに基づく温度によるものとなり、実施の形態１温度センサ１４よりも精度よくプレート式熱交換器３内を流れる冷媒Ｒの温度を検出ことができる。 The projections 93 and 94 of the third embodiment may be provided in the second embodiment. According to this structure, at the position where the temperature sensor 14 is not provided in the longitudinal direction, the ridges 84 and 86 are formed over the entire area in the lateral direction. The height can be increased as compared with the portions 83 and 85. In addition, the temperature detected by the temperature sensor 14 joined to the wall portion 71a depends on the temperature based on the refrigerant R, and the refrigerant R flowing in the plate heat exchanger 3 with higher accuracy than the temperature sensor 14 of the first embodiment. The temperature of can be detected.
　なお、第２の実施の形態の凸部８３、８５を、実施の形態４のプレート式熱交換器１００のように、高さを低くなるように構成してもよい。このように構成しても、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなり、温度センサ１４による冷媒Ｒの温度の検出精度を高めることができる。 Note that the convex portions 83, 85 of the second embodiment may be configured to have a low height, like the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature R of the refrigerant R by the temperature sensor 14 is larger. The temperature detection accuracy can be improved.
　なお、第６の実施の形態の凸部１２１、１２２を、実施の形態４のプレート式熱交換器１００のように、高さを低くなるように構成してもよい。このように構成しても、壁部７１ａ、７２ｂから構成される側部Ｈ１は、水Ｗとの接触面積よりも、冷媒Ｒとの接触面積の方が大きくなり、温度センサ１４による冷媒Ｒの温度の検出精度を高めることができる。 Note that the convex portions 121 and 122 of the sixth embodiment may be configured to have a low height, like the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 including the walls 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature R of the refrigerant R by the temperature sensor 14 is larger. The temperature detection accuracy can be improved.
　なお、上記各実施形態の冷媒回路２ａでは、四方弁５を設けて冷媒Ｒの流れを切り替えて、加熱モードと冷却モードに切り替え可能に構成していたが、これに限らない構成でもよい。例えば、冷媒回路２ａから四方弁５を省略し、加熱モードおよび冷却モードのうち一方もモードのみを行うように冷媒回路２ａを構成してもよい。 In addition, in the refrigerant circuit 2a of each of the above-described embodiments, the four-way valve 5 is provided to switch the flow of the refrigerant R so that the heating mode and the cooling mode can be switched, but the structure is not limited to this. For example, the four-way valve 5 may be omitted from the refrigerant circuit 2a, and the refrigerant circuit 2a may be configured to perform only one of the heating mode and the cooling mode.
１　室外機
２ａ　冷媒回路
２ｂ　水回路
３、８０、９０、１００、１１０、１２０　プレート式熱交換器
３ａ、３ｂ　水配管接続口
３ｃ、３ｄ　冷媒配管接続口
４　圧縮機
４ａ　マフラー
５　四方弁
６　空気熱交換器
７　圧力容器
８ａ、８ｂ　電子膨張弁
１０　冷媒配管
１１、１２、１３、１４　温度センサ
１５　制御装置
１６　記憶装置
１７　演算装置
２０　筐体
２０ａ　グリル
２１　送風機室
２２　機械室
２３　セパレータ
２４　ファン
４０、４１、８１、８２、９１、９２　伝熱プレート
４２、４３　外側プレート
４４、４５　補強プレート
４６、５０、５４　第１開口部
４７、５１、５５　第２開口部
４８、５２、５６　第３開口部
４９、５３、５７　第４開口部
６１、６２、８３、８５、１２１、１２２　凸部
８４、８６　凸条部
６３　第１流路
６４　第２流路
７０ａ、７０ｂ　主板部、
７１ａ、７１ｂ、７２ａ、７２ｂ、７３ａ、７３ｂ、７４ａ、７４ｂ　壁部
７５ａ、７５ｂ、７６ａ、７６ｂ　高部
９３、９４　凸部
９３ａ、９４ａ　先端面
Ｅ１、Ｅ２、Ｅ３、Ｅ４　先端
Ｆａ、Ｆｂ、Ｆｃ、Ｆｄ　長尺部
Ｈ１、Ｈ２　側部
Ｋ１、Ｋ２、Ｋ３、Ｋ４、Ｋ５、Ｋ６、Ｋ７、Ｋ８、Ｋ９、Ｋ１０、Ｋ１１、Ｋ１２、Ｋ１３、Ｋ１４　距離
Ｌ１、Ｌ２　長さ
Ｓ１、Ｓ２　幅
Ｒ　冷媒
Ｗ　水
Ｚ　軸 1 Outdoor unit 2a Refrigerant circuit 2b Water circuit 3, 80, 90, 100, 110, 120 Plate heat exchanger 3a, 3b Water pipe connection port 3c, 3d Refrigerant pipe connection port 4 Compressor 4a Muffler 5 Four-way valve 6 Air heat Exchanger 7 Pressure vessel 8a, 8b Electronic expansion valve 10 Refrigerant piping 11, 12, 13, 14 Temperature sensor 15 Control device 16 Storage device 17 Computing device 20 Housing 20a Grill 21 Blower room 22 Machine room 23 Separator 24 Fans 40, 41 , 81, 82, 91, 92 Heat transfer plates 42, 43 Outer plates 44, 45 Reinforcing plates 46, 50, 54 First openings 47, 51, 55 Second openings 48, 52, 56 Third openings 49, 53, 57 4th opening part 61, 62, 83, 85, 121, 122 convex part 84, 86 convex line part 63 1st flow path 64 2nd flow path 70a, 70b Main plate part,
71a, 71b, 72a, 72b, 73a, 73b, 74a, 74b Wall part 75a, 75b, 76a, 76b High part 93, 94 Convex part 93a, 94a Tip surface E1, E2, E3, E4 Tip Fa, Fb, Fc, Fd Long part H1, H2 Side part K1, K2, K3, K4, K5, K6, K7, K8, K9, K10, K11, K12, K13, K14 Distance L1, L2 Length S1, S2 Width R Refrigerant W Water Z axis

Claims (11)

  1. 矩形で板状の主板部と前記主板部の縁から板状の面の一方側へ突出させた壁部とを有した伝熱プレートを交互に前記主板部の板状面の中心から垂直に延びる軸を基準に１８０度反転して複数積層し、前記伝熱プレート間に第１流体が流れる第１流路と第２流体が流れる第２流路とを積層方向に交互に形成するプレート式熱交換器において、
    前記主板部には、前記壁部が突出した面とは反対側の板状の面から突出する凸部が設けられ、
    前記凸部は、前記主板部の一方の長辺に沿って断続的にまたは連続的に形成され、且つ該凸部が突出する側の隣で対向する前記伝熱プレートの前記壁部に当接し、
    前記主板部は、他方の長辺に接して沿うように長尺部を備え、
    　前記伝熱プレートの前記長尺部を基準として、前記長尺部から前記壁部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離は、前記長尺部から前記凸部が突出する側の隣で対向する前記伝熱プレートの前記凸部までの距離よりも小さくなるよう構成された
    プレート式熱交換器。     Heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion protruding from one edge of the main plate portion to one side of the plate-shaped surface extend alternately from the center of the plate-shaped surface of the main plate portion. A plate-type heat that is inverted by 180 degrees with respect to the axis and is laminated to form a plurality of first flow passages through which the first fluid flows and second flow passages through which the second fluid flows alternately between the heat transfer plates in the stacking direction. In the exchanger,
    The main plate portion is provided with a convex portion protruding from a plate-shaped surface on the side opposite to the surface from which the wall portion protrudes,
    The convex portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate that is adjacent to the protruding side of the main plate portion and is adjacent to the protruding side. ,
    The main plate portion is provided with a long portion so as to be in contact with the other long side,
    With reference to the elongated portion of the heat transfer plate, the distance from the elongated portion to the convex portion of the heat transfer plate that is adjacent and adjacent to the side where the wall portion protrudes is the distance from the elongated portion to the convex portion. A plate-type heat exchanger configured to be smaller than a distance to the convex portion of the heat transfer plate that is adjacent and adjacent to the side where the portion projects.
  2. 　前記凸部は、該凸部が突出する側の隣で対向する前記伝熱プレートの前記長尺部に当接されている請求項１に記載のプレート式熱交換器。 The plate heat exchanger according to claim 1, wherein the convex portion is in contact with the elongated portion of the heat transfer plate that is adjacent and adjacent to a side where the convex portion projects.
  3. 　前記凸部は、前記主板部の前記一方の長辺から前記長尺部まで延びるように形成されている
    請求項１又は請求項２に記載のプレート式熱交換器。     The plate heat exchanger according to claim 1 or 2, wherein the convex portion is formed so as to extend from the one long side of the main plate portion to the long portion.
  4. 　前記主板部の一方の長辺に沿って形成されている凸部は連続的に形成されたものであり、
    　前記主板部の前記一方の長辺から前記長尺部まで形成されている凸部は複数形成されている
    請求項１から請求項３のうちいずれか一項に記載のプレート式熱交換器。     The convex portion formed along one long side of the main plate portion is formed continuously,
    The plate heat exchanger according to any one of claims 1 to 3, wherein a plurality of convex portions formed from the one long side of the main plate portion to the long portion are formed.
  5. 　前記主板部には、前記長尺部における前記主板部の長手方向の両側の位置に、前記主板部の一方の長辺から前記主板部の他方の長辺まで形成された凸条部を備えた
    請求項１から請求項４のうちいずれか一項に記載のプレート式熱交換器。     The main plate portion is provided with ridge portions formed at positions on both sides in the longitudinal direction of the main plate portion in the long portion from one long side of the main plate portion to the other long side of the main plate portion. The plate heat exchanger according to any one of claims 1 to 4.
  6. 　前記他方の長辺に対応した前記壁部と、前記一方の長辺に対応した前記壁部とは、主板部から離れるにつれ互いの間隔が広がるように形成され、
    前記他方の長辺に対応した前記壁部の前記主板部からの突出長さは、前記一方の長辺に対応した前記壁部の前記主板部からの突出長さよりも長くなるように構成されている
    請求項１から請求項５のうちいずれか一項に記載のプレート式熱交換器。     The wall portion corresponding to the other long side, and the wall portion corresponding to the one long side are formed such that the distance between them widens as the distance from the main plate portion increases,
    The protrusion length from the main plate portion of the wall portion corresponding to the other long side is configured to be longer than the protrusion length from the main plate portion of the wall portion corresponding to the one long side. The plate heat exchanger according to any one of claims 1 to 5.
  7. 　前記伝熱プレートの前記一方の長辺に対応した前記壁部の先端と、前記積層方向で隣の伝熱プレートの前記他方の長辺に対応した前記壁部の先端とが揃うように構成されている
    請求項６に記載のプレート式熱交換器。     The tip of the wall portion corresponding to the one long side of the heat transfer plate and the tip of the wall portion corresponding to the other long side of the adjacent heat transfer plate in the stacking direction are configured to be aligned. The plate type heat exchanger according to claim 6.
  8. 　前記壁部における前記第２流体と対向する部分に前記第２流体の温度を検出する温度検出手段を設置するための温度検出手段設置部が設けられている請求項１から請求項７のうちいずれか一項に記載のプレート式熱交換器。 8. A temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided at a portion of the wall portion facing the second fluid. The plate heat exchanger according to 1 above.
  9. 矩形で板状の主板部と前記主板部の縁から板状の面の一方側へ突出させた壁部とを有した伝熱プレートを交互に前記主板部の板状面の中心から垂直に延びる軸を基準に１８０度反転して複数積層し、前記伝熱プレート間に第１流体が流れる第１流路と第２流体が流れる第２流路とを積層方向に交互に形成するプレート式熱交換器において、
    　前記複数の伝熱プレートを積層することで前記主板部の四つの辺に対応する位置に前記複数の壁部によって構成される四つの側部を備え、
    　前記四つの側部のうちの少なくとも一つの側部は、前記第１流体の接触面積よりも前記第２流体の接触面積が大きくなるように構成されている
    プレート式熱交換器。     Heat transfer plates each having a rectangular plate-shaped main plate portion and a wall portion protruding from one edge of the main plate portion to one side of the plate-shaped surface extend alternately from the center of the plate-shaped surface of the main plate portion. A plate-type heat that is inverted by 180 degrees with respect to the axis and is laminated to form a plurality of first flow passages through which the first fluid flows and second flow passages through which the second fluid flows alternately between the heat transfer plates in the stacking direction. In the exchanger,
    By laminating the plurality of heat transfer plates, four side portions configured by the plurality of wall portions are provided at positions corresponding to the four sides of the main plate portion,
    A plate heat exchanger in which at least one of the four side portions is configured such that the contact area of the second fluid is larger than the contact area of the first fluid.
  10. 前記第１流体の接触面積よりも前記第２流体の接触面積が大きくなるように構成された前記側部における前記第２流体と対向する部分に前記第２流体の温度を検出する温度検出手段を設置するための温度検出手段設置部が設けられている請求項９に記載のプレート式熱交換器。 Temperature detecting means for detecting the temperature of the second fluid is provided at a portion of the side portion facing the second fluid, the temperature detecting means being configured such that the contact area of the second fluid is larger than the contact area of the first fluid. The plate heat exchanger according to claim 9, further comprising a temperature detecting means installation portion for installation.
  11. 　請求項８又は請求項１０に記載のプレート式熱交換器と、前記第２流体の圧縮を行う圧縮機と、空気と前記第２流体との熱交換を行う空気熱交換器と、前記第２流体の圧力を低下させる膨張弁と、余剰の前記第２流体を保留する圧力容器とを備えた前記第２流体が循環する第２流体回路と、
    　前記温度検出手段設置部に設置された温度検出手段と、
    を備えたヒートポンプ装置。     The plate heat exchanger according to claim 8 or 10, a compressor that compresses the second fluid, an air heat exchanger that performs heat exchange between air and the second fluid, and the second heat exchanger. A second fluid circuit, in which the second fluid circulates, including an expansion valve that lowers the pressure of the fluid, and a pressure container that retains the excess second fluid,
    Temperature detecting means installed in the temperature detecting means installation section,
    Heat pump device.
PCT/JP2018/048446 2018-12-28 2018-12-28 Plate-type heat exchanger and heat pump device WO2020136863A1 (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06265289A (en) * 1993-03-11 1994-09-20 Hitachi Ltd Plate type heat exchanger
JP2002107090A (en) * 2000-09-29 2002-04-10 Hisaka Works Ltd Plate-type heat exchanger and producing method
JP2011089690A (en) * 2009-10-22 2011-05-06 Hitachi Appliances Inc Air conditioner
WO2011062118A1 (en) * 2009-11-19 2011-05-26 三菱電機株式会社 Plate-type heat exchanger and heat pump device
JP2013124836A (en) * 2011-12-16 2013-06-24 Mitsubishi Electric Corp Refrigeration cycle device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06265289A (en) * 1993-03-11 1994-09-20 Hitachi Ltd Plate type heat exchanger
JP2002107090A (en) * 2000-09-29 2002-04-10 Hisaka Works Ltd Plate-type heat exchanger and producing method
JP2011089690A (en) * 2009-10-22 2011-05-06 Hitachi Appliances Inc Air conditioner
WO2011062118A1 (en) * 2009-11-19 2011-05-26 三菱電機株式会社 Plate-type heat exchanger and heat pump device
JP2013124836A (en) * 2011-12-16 2013-06-24 Mitsubishi Electric Corp Refrigeration cycle device

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