JP3966134B2 - Heat exchanger - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat exchanger composed only of a plate-like member that constitutes an internal fluid passage through which an internal fluid flows, and is suitable for use in, for example, an evaporator for vehicle air conditioning.
[0002]
[Prior art]
As a conventional technique, Japanese Patent Application Laid-Open No. 2001-41678 discloses a heat exchanger only with plates without fins. An internal fluid (for example, a refrigerant) that circulates in the tube by laminating a large number of flat-shaped tubes that are formed by joining two aluminum plates in the middle and forming an air passage between them. Heat exchange with the air flowing through the external air passage.
[0003]
Japanese Patent No. 2749586 also discloses a heat exchanger without fins formed from a resin material. By joining the necessary portions of the two resin sheets, a header portion and a fluid passage are formed inside.
[0004]
[Problems to be solved by the invention]
However, the former one of the above prior arts has a problem that it is heavy because only the aluminum plate is laminated. In order to reduce the weight, it is essential to reduce the thickness of the plate, and reducing the thickness is advantageous in terms of heat exchange. However, the tank part and the internal fluid passage part are integrated by pressing from a single aluminum plate. Therefore, when the thickness is reduced, the tank portion having a larger pressure receiving area than the passage portion is also thinned, so that the pressure strength cannot be secured.
[0005]
In response to this, it is necessary to take measures such as reinforcing the tank portion using another member. On the other hand, taking a plate thickness sufficient for the pressure resistance in the tank portion results in an excessively thick state in the core portion to be heat exchanged, and does not become an optimum plate thickness. The latter of the above prior arts also has the effect that it can be lightened, but since the tank part and the internal fluid passage part are integrally formed by joining two resin sheets, the tank part and The problem that the optimum plate thickness conflicts with the heat exchange part is the same.
[0006]
The present invention has been made in view of the above-mentioned problems of the prior art, and it is an object of the present invention to provide a heat exchanger that can be lightened and that can optimize the plate thickness between a tank part and a heat exchange part. And
[0007]
[Means for Solving the Problems]
In order to achieve the above object, the following technical means are adopted. That is, in the first aspect of the present invention, a plurality of pairs of heat transfer plates (12a, 12b, 12), in which the internal fluid passage portion and the tank portion are integrally formed, are stacked to face each other. The contact surfaces are joined, the internal fluid passages (19, 20) through which the internal fluid flows inside the heat transfer plates (12a, 12b, 12), and the tank portions (15 to 15) communicating with the respective internal fluid passages (19, 20). 18), the heat transfer plates (12a, 12b, 12) are formed of a resin material, and the fitting protrusions are fitted to each other in the portions forming the internal fluid passages (19, 20). It is characterized in that a fitting concavo-convex part (12c) fitted to each other is provided on the contact surface forming the tank part (15-18) .
Thereby, a heat exchanger can be comprised lightly. 3A and 3B show a conventional heat transfer plate, where FIG. 3A is a sectional view of a tank portion, FIG. 3B is a sectional view of a heat exchange portion before brazing, and FIG. 3C is a sectional view of a heat exchange portion after brazing. FIG. Conventionally, since an aluminum plate is pressed and formed, each part has a bend R as shown in FIG. This is brazed and the joint strength is maintained by filling the gaps of the joints with the fillet F of the brazing material (note that the reference numerals in the drawing correspond to the embodiments described later, and are described here. Is omitted).
On the other hand, in the present invention, since the joint portion is peeled off and the joint strength is weakened without fitting, the fitting convex portion (14a) is provided in the portion forming the internal fluid passage (19, 20). The bonding strength is increased by using the force applied to the bonded portion as the shear direction. This utilizes the fact that it is easy to make a necessary shape in each part by forming the heat transfer plate (12a, 12b, 12) using a resin material by injection molding or the like.
Moreover, the heat-transfer plate (12a, 12b, 12) is provided with the fitting uneven | corrugated part (12c) which mutually fits in the contact surface which forms a tank part (15-18). Similarly to the above, since the joint part is peeled off and the joint strength is weakened without fitting, by providing the fitting uneven part (12c) on the contact surface forming the tank part (15-18), The joint strength is increased by using the force related to the joint as the shear direction. This also utilizes the fact that it is easy to make a necessary shape in each part by forming the heat transfer plates (12a, 12b, 12) using a resin material by injection molding or the like.
[0008]
In the invention according to claim 2, the heat transfer plates (12a, 12b, 12) are formed so that the plate thickness of the tank portions (15-18) is thicker than the plate thickness of the internal fluid passages (19, 20). It is characterized by that. By forming the heat transfer plates (12a, 12b, 12) using a resin material by injection molding or the like, it becomes easy to obtain a plate thickness corresponding to the required strength for each part. By utilizing this, the internal fluid passages (19, 20) for heat exchange are thin, and the tank portions (15-18) requiring pressure strength are thick, and can be formed with optimum plate thicknesses.
[0009]
In the invention according to claim 3, the heat transfer plates (12 a, 12 b, 12) have substrate portions (13) that are in contact with each other and are bonded to each other, and protrude outward with respect to the substrate portion (13). In the invention according to claim 4, the heat transfer plate (12a, 12b, 12) is configured such that the outer surface of the internal fluid passage (19, 20) portion has a substantially trapezoidal shape. The inner surface of 20) has a substantially circular shape.
[0010]
Also, by forming the heat transfer plates (12a, 12b, 12) using a resin material by injection molding or the like, it becomes easy to obtain a necessary shape for each part. Using this, the outer surface of the internal fluid passages (19, 20) has a substantially trapezoidal shape with a high effect of increasing the heat transfer coefficient, and the inner surface of the internal fluid passages (19, 20) has a substantially circular shape advantageous for ensuring pressure resistance, It can be formed in an optimal shape.
[0015]
The invention according to claim 5 is characterized in that members (21, 22, 25, 30, 31) constituting the heat exchanger other than the heat transfer plates (12a, 12b, 12) are also formed of a resin material. To do. Thereby, a heat exchanger can be comprised more lightly. Moreover, in invention of Claim 6 , joining of the contact surface in assembling a heat exchanger was joined by adhesion | attachment. Thereby, since heating like the conventional brazing becomes unnecessary, it becomes possible to assemble with simple equipment and to reduce the energy applied.
[0016]
In the present invention, expressions such as “one pair”, “two sheets”, “multiple pairs”, and “multiple sheets” related to the number of heat transfer plates appear as plate-like cross-sectional shapes in the cross-sectional views of FIGS. This means that there are a pair (two) of heat transfer plates (plate-like members) in the plate fitting direction, and a plurality of pairs (plural) in the stacking direction on the left and right in FIG. The pair of heat transfer plates can be individually cut and molded as well as can be integrally formed by a connecting part by bending or the like. Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with the specific means described in the embodiments described later.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIGS. 1 and 2 show an embodiment of the present invention, and show an example in which the heat exchanger of the present invention is applied to an evaporator 10 for vehicle air conditioning. FIG. 1A is an exploded perspective view showing the overall structure of the heat exchanger 10, and FIG. 1B is a partial cross-sectional view showing an air passage A ₁ between the heat transfer plates 12. 2 shows the heat transfer plate 12, (a) is a cross-sectional view of the tank portions 15 to 18, (b) is a cross-sectional view of a heat exchange portion before fitting, and (c) is a heat exchange after fitting. It is sectional drawing of a part.
[0018]
The evaporator 10 is configured as a cross-flow heat exchanger in which the flow direction A of air-conditioning air and the refrigerant flow direction B (vertical direction shown in FIG. 1A) in the heat transfer plate 12 portion are substantially orthogonal. Yes. As shown in FIG. 2, the evaporator 10 includes a first heat transfer plate 12a and a second heat transfer plate 12b that perform heat exchange between air for air conditioning (external fluid) and refrigerant (internal fluid). Are combined to form a heat transfer plate 12, and a large number of these are stacked.
[0019]
Each of the heat transfer plates 12a and 12b is made of, for example, a nylon resin material, and the refrigerant passages 19 and 20 are injection-molded to a thickness of about 0.1 to 0.4 mm, for example. It is. The heat transfer plate 12 has a substantially rectangular planar shape as shown in FIG. 1, and the outer dimensions thereof are the same, the length in the long side direction is, for example, 245 mm, and the width in the short side direction is, for example, 45 mm. It is.
[0020]
Although the shape of the heat transfer plates 12a and 12b is different only in the direction of a fitting uneven portion 12c described later in the present embodiment, the shape may basically be the same. However, if the layers are stacked in one direction while facing each other and the refrigerant path is complicated, there may be some differences.
[0021]
As shown in FIG. 2, a plurality of projecting portions 14 whose outer shape is substantially trapezoidal and whose inner side is substantially semicircular are projected on the outer surface of the flat substrate portion 13 of each of the heat transfer plates 12a and 12b. Yes. In addition, on the back surface of the substrate portion 13, two fitting projections 14a that are fitted to the inside of the trapezoidal shape of the other plate are formed, and the gap between the two fitting projections 14a is also substantially semicircular. It is formed into a shape.
[0022]
When the substrate portions 13 of the two heat transfer plates 12a and 12b are fitted to each other (see FIG. 2 (c)), the semicircular shape inside the previous trapezoidal shape and the substantially half between the fitting convex portion 14a. The substantially circular internal fluid passages (refrigerant passages) 19 and 20 are formed so as to face the circular shape. The internal fluid passages 19 and 20 continuously extend in parallel with the longitudinal direction of the heat transfer plate 12 (in other words, the direction substantially perpendicular to the air flow direction A). In the heat transfer plates 12a and 12b of FIG. Six protrusions 14 and six internal fluid passages 19 and 20 are formed on the upstream side and the downstream side, respectively.
[0023]
That is, in the width direction of each heat transfer plate 12, a refrigerant passage 20 on the windward side is formed inside the protruding portion 14 located on the windward side from the center portion, and the center portion in the width direction of each heat transfer plate 12. A refrigerant channel 19 on the leeward side is formed on the inner side of the projecting portion 14 located further on the leeward side (FIG. 1B, FIGS. 2B and 2C show only the refrigerant channel 20 on the leeward side. ).
[0024]
On the other hand, among the heat transfer plates 12, tank portions 15 to 15 that are divided in the heat transfer plate width direction (air flow direction A) at both ends of a direction B (heat transfer plate longitudinal direction) B orthogonal to the air flow direction A, respectively. Two 18 are formed. The tank portions 15 to 18 are formed by projecting in the same direction as the projecting portion 14 (see FIG. 2A) in each heat transfer plate 12, and the molding height thereof is the same as that of the projecting portion 14. It is.
[0025]
Further, the tank portions 15 to 18 are formed thicker than the substrate portion 13 (for example, about 2 mm in the present embodiment) in order to provide pressure resistance, and the tank portions 15 to 18 are provided on both contact surfaces in the stacking direction. Are provided with a fitting uneven portion 12c for fitting to improve sealing performance and bonding strength.
[0026]
In this way, the tank portions 15 to 18 are projected in the same direction as the projecting portion 14, and the fitting irregularities 12 c are fitted and continuous at both end surfaces in the stacking direction. Both end portions of the windward side refrigerant passage 20 communicate with the windward side tank portions 17 and 18, and both end portions of the leeward side refrigerant passage 19 communicate with the leeward side tank portions 15 and 16.
[0027]
Further, the tank portions 15 and 17 at the lower end of the heat transfer plate 12 and the tank portions 16 and 18 at the upper end of the heat transfer plate 12 are divided into two in the width direction of the heat transfer plate. As shown in FIG. 15-18 are substantially oval shape in the heat-transfer plate width direction. Communication holes 15a to 18a are opened in the center of each tank portion 15 to 18, and tank portions 15 to 18 are connected to each other between adjacent heat transfer plates in the heat transfer plate stacking direction by the communication holes 15a to 18a. The flow path is in communication.
[0028]
That is, as shown to Fig.2 (a), the end surfaces of each adjacent tank part 15-18 contact | abut with each other, and the communication holes 15a-18a mutually communicate. By the way, in the width direction (air flow direction A) of each heat transfer plate 12, as shown in FIG.1 (b), the some protrusion part 14 is shifted | deviated from the protrusion part 14 of each adjacent heat transfer plate. Thus, each protrusion 14 can be positioned on a concave surface formed by the substrate portion 13 of each adjacent heat transfer plate 12.
[0029]
As a result, a gap is surely formed between the top portion of each projecting portion 14 on the convex surface side and the concave surface portion of the substrate portion 13 of the adjacent heat transfer plate 12. Due to this gap, an air passage meandering in a wave shape as indicated by an arrow A ₁ is continuously formed over the entire length in the heat transfer plate width direction (air flow direction A). Therefore, conditioned air is blown in the direction of arrow A, can pass between the two heat transfer plates 12a · 12b while meandering the air passage in a wave as shown by the arrow A _1.
[0030]
Next, a part for entering and exiting the refrigerant with respect to the core part 11 will be described. End plates 21 and 22 and side plates 25 and 31 as side plate members having the same size as the heat transfer plate 12 are disposed at both ends in the heat transfer plate stacking direction. Each of the end plates 21 and 22 has a flat plate shape that comes into contact with the protruding portion 14 of the heat transfer plate 12 and the protruding sides of the tank portions 15 to 18 and is joined to the heat transfer plate 12.
[0031]
1 is provided with a refrigerant inlet hole 21a in the vicinity of the lower end portion thereof and a refrigerant outlet hole 21b in the vicinity of the upper end portion thereof. The refrigerant inlet hole 21a is formed at the lower end portion of the heat transfer plate 12. The refrigerant outlet hole 21b communicates with the communication hole 18a of the windward tank section 18 at the upper end of the heat transfer plate 12 and communicates with the communication hole 15a of the leeward tank section 15.
[0032]
Further, the right end plate 22 of FIG. 1 has a refrigerant outlet hole 22a in the vicinity of the upper end portion thereof and a refrigerant inlet hole 22b in the vicinity of the lower end portion thereof. The refrigerant outlet hole 22a is formed at the upper end portion of the heat transfer plate 12. The refrigerant hole 16b communicates with the communication hole 16a of the leeward tank section 16, and the refrigerant inlet hole 22b communicates with the communication hole 17a of the windward tank section 17 at the lower end of the heat transfer plate 12.
[0033]
In the present embodiment, the refrigerant inlet pipe 23 and the refrigerant outlet pipe 24 are collectively provided in a pipe joint block 30 as one pipe connecting member, thereby simplifying the connection between the evaporator 10 and the external refrigerant pipe. For this reason, as shown in FIG. 1, a side plate 31 is joined to the left end plate 21, and a refrigerant passage leading to the refrigerant inlet / outlet of the pipe joint block 30 is formed between the plates 21 and 31.
[0034]
The refrigerant passage configuration will be described in more detail. In the side plate 31, a protruding portion 31a is formed to protrude outward from a portion of the piping joint block 30 to the lower side, and upper and lower end portions of the protruding portion 31a. Are combined into one, but in the middle of the vertical direction (plate longitudinal direction), it is divided into a plurality (three in the example shown in the figure) to increase the sectional modulus of the side plate 31 to increase the strength. .
[0035]
The upper end portion of the refrigerant passage formed by the recess inside the protruding portion 31 a communicates with the refrigerant inlet pipe 23 of the piping joint block 30, and the lower end portion of the refrigerant passage communicates with the communication hole 21 a of the end plate 21. . The refrigerant outlet pipe 24 communicates with the communication hole 21 b of the end plate 21.
[0036]
The end plates 21 and 22 and the side plates 25 and 31 are made of, for example, a nylon resin material like the heat transfer plate 12, and are thicker than the heat transfer plate 12 (for example, a plate thickness t = 1). (About 0.0 mm) to improve the strength. Further, the piping joint block 30 is also formed by integrally injection-molding the refrigerant inlet pipe 23 and the refrigerant outlet pipe 24 with, for example, a nylon resin material, and is arranged on the upper side of the side plate 31 in this example. It joins by adhering both fitting parts.
[0037]
In this embodiment, the gas-liquid two-phase refrigerant decompressed by a decompression means such as an expansion valve of a refrigeration cycle (not shown) flows into the refrigerant inlet pipe 23, and the refrigerant outlet pipe 24 is connected to a compressor suction side (not shown). The gas refrigerant evaporated in the evaporator 10 is guided to the compressor suction side.
[0038]
In each heat transfer plate 12, since the refrigerant from the refrigerant inlet pipe 23 flows into the leeward refrigerant passage 19, the refrigerant passage of the entire evaporator 10 constitutes an inlet-side refrigerant passage, and the leeward refrigerant The passage 20 constitutes an outlet side refrigerant passage because the refrigerant that has passed through the refrigerant passage 19 on the leeward side (inlet side) flows in and flows out to the refrigerant outlet pipe 24.
[0039]
Next, the refrigerant path of the evaporator 10 as a whole will be described. First, among the tank parts 15 to 18 located at the upper and lower ends of the evaporator 10, the leeward tank parts 15 and 16 are the refrigerant inlet side tank parts. Further, the tank parts 17 and 18 on the windward side constitute a refrigerant outlet side tank part. Then, the low-pressure gas-liquid two-phase refrigerant depressurized by the expansion valve enters the leeward lower inlet side tank portion 15 from the refrigerant inlet pipe 23, and the refrigerant is formed by the leeward protrusion 14 of each heat transfer plate 12. The refrigerant passage 19 is raised and exits to the upper inlet side tank section 16.
[0040]
The refrigerant collected in the inlet side tank unit 16 enters the inner space of the side plate 25 from the refrigerant outlet hole 22a of the end plate 22, descends as the communication path, and passes through the refrigerant inlet hole 22b of the end plate 22. It enters the outlet side tank section 17 on the lower side of the windward side. Then, the refrigerant ascends the refrigerant passage 20 formed by the windward protruding portion 14 of each heat transfer plate 12 and exits to the upper outlet side tank portion 18, and the gas refrigerant evaporated in the evaporator 10 is the refrigerant outlet pipe. 24 is sucked into the compressor suction side.
[0041]
In the present embodiment, the refrigerant passage of the evaporator 10 is configured as described above, and the abutting surfaces of the components shown in FIG. 1 are sequentially joined while being bonded, for example, by applying an epoxy resin adhesive or the like. The evaporator 10 is assembled by stacking.
[0042]
Next, the operation of the evaporator 10 according to the present embodiment will be described. The evaporator 10 is accommodated in an air conditioning unit case (not shown) with the vertical direction in FIG. Air is blown through. When the compressor of the refrigeration cycle is activated, the low-pressure side gas-liquid two-phase refrigerant decompressed by an expansion valve (not shown) flows according to the refrigerant passage configuration described above.
[0043]
On the other hand, due to the gap formed between the protruding portion 14 protruding in a convex shape on the outer surface side of the heat transfer plate 12 of the core portion 11 and the substrate portion 13, over the entire length of the heat transfer plate width direction (air flow direction A). As shown by an arrow A _{1 in} FIG. 1B, a wavy air passage is continuously formed. As a result, the conditioned air blown in the direction of the arrow A can pass between the two heat transfer plates 12 while meandering in the air passage as indicated by the arrow A ₁ , and the refrigerant flows from this air flow. Since the evaporation latent heat is absorbed and evaporated, the conditioned air is cooled and becomes cold air.
[0044]
At this time, the inlet-side refrigerant passage 19 is disposed on the leeward side and the outlet-side refrigerant passage 20 is disposed on the leeward side with respect to the flow direction A of the conditioned air, so that the refrigerant inlet / outlet with respect to the air flow is in a counterflow relationship. Become. Further, on the air side, the air flow direction A is perpendicular to the longitudinal direction of the protrusion 14 of the heat transfer plate 12 (the refrigerant flow direction B in the refrigerant passages 19 and 20), and the protrusion Since 14 forms the convex surface (heat-transfer surface) which protrudes orthogonally with an air flow, air is prevented from going straight by the convex surface shape of the protrusion part 14 extended orthogonally.
[0045]
For this reason, the air flow forms a wobbling flow between the heat transfer plates 12 as shown by the arrow A ₁ in FIG. 1B and disturbs the flow. Therefore, the air flow becomes a turbulent state. The air side heat transfer coefficient can be dramatically improved. Here, since the core part 11 is comprised only by the heat-transfer plate 12, compared with the normal evaporator provided with the conventional fin member, the heat-transfer area by the side of air reduces significantly, Since the air side heat transfer coefficient is dramatically improved by setting the state, the reduction of the air side heat transfer area can be compensated by the improvement of the air side heat transfer coefficient, and the required cooling performance can be ensured.
[0046]
Next, features of the present embodiment will be described. First, the heat transfer plate 12 (12a, 12b) is formed of a resin material. Thereby, the heat exchanger 10 can be comprised lightly. Further, the heat transfer plates 12 (12a and 12b) are formed so that the tank portions (15 to 18) are thicker than the plate thicknesses of the internal fluid passages 19 and 20.
[0047]
By forming the heat transfer plate 12 (12a and 12b) by using a resin material by injection molding or the like, it becomes easy to obtain a plate thickness corresponding to the required strength for each part. By utilizing this, the internal fluid passages 19 and 20 for heat exchange are thin, and the tank portions 15 to 18 requiring pressure strength are thick, and can be formed with optimum plate thicknesses.
[0048]
Further, the heat transfer plate 12 (12a, 12b) has a base plate part 13 that is in contact with and joined to each other, and the outer surfaces of the internal fluid passages 19, 20 projecting outward with respect to the base plate part 13, The inner surface of the internal fluid passages 19 and 20 has a substantially circular shape.
[0049]
This is also because the heat transfer plate 12 (12a, 12b) is formed by injection molding or the like using a resin material, making it easy to obtain the required shape for each part. The outer surface 20 can be formed in a substantially trapezoidal shape with a high effect of increasing the heat transfer coefficient, and the inner surfaces of the internal fluid passages 19 and 20 can be formed in optimum shapes, each having a substantially circular shape that is advantageous for ensuring the pressure resistance.
[0050]
Further, the heat transfer plate 12 (12a, 12b) is provided with a fitting convex portion 14a that is fitted to each other at a portion that forms the internal fluid passages 19, 20. This is because the joint is peeled off and the joint strength is weakened without fitting. Therefore, by providing the fitting convex portion 14a in the portion where the internal fluid passages 19 and 20 are formed, the force applied to the joint is sheared. As a result, the bonding strength is increased.
[0051]
Further, as described above, the inner surfaces of the internal fluid passages 19 and 20 are formed in a substantially circular shape by using the fitting convex portion 14a. This also utilizes the fact that it is easy to make a necessary shape in each part by forming the heat transfer plate 12 (12a, 12b) using a resin material by injection molding or the like.
[0052]
Further, the heat transfer plate 12 (12a, 12b) is provided with a fitting uneven portion 12c that fits to the contact surfaces that form the tank portions 15-18. Similarly to the above, since the joint portion is peeled off and the joint strength is weakened without fitting, by providing the fitting uneven portion 12c on the contact surface forming the tank portions 15 to 18, the joint portion is related. The strength is increased by using force as the shear direction. This also utilizes the fact that the heat transfer plate 12 (12a, 12b) is formed by injection molding or the like using a resin material, so that it becomes easy to make a necessary shape in each part.
[0053]
In addition, members constituting the heat exchanger other than the heat transfer plates 12 (12a and 12b) (for example, the end plates 21 and 22, the side plates 25 and 30 and the pipe joint block 31 in this embodiment) are also formed of a resin material. ing. Thereby, the heat exchanger 10 can be comprised more lightly. Moreover, joining of the contact surface in assembling the heat exchanger 10 is joined by adhesion. Thereby, since heating like the conventional brazing becomes unnecessary, it becomes possible to assemble with simple equipment and to reduce the energy applied.
[0054]
(Other embodiments)
In the embodiment described above, the case where the air (external fluid) flow direction A is set to be orthogonal to the refrigerant flow direction (plate longitudinal direction) B of the heat transfer plate 12 (12a, 12b) has been described. The external fluid) flow direction A may be inclined by a predetermined angle with respect to the refrigerant flow direction (plate longitudinal direction) B of the heat transfer plate 12 (12a, 12b). In short, the air (external fluid) flow direction A And the refrigerant flow direction (plate longitudinal direction) B of the heat transfer plate 12 (12a, 12b) may be in a crossing relationship.
[0055]
In the above-described embodiment, the low-temperature refrigerant on the low-pressure side of the refrigeration cycle flows through the refrigerant passages (internal fluid passages) 19 and 20 of the heat transfer plate 12, the conditioned air flows outside the heat transfer plate 12, and the refrigerant evaporates. Although the case where the present invention is applied to the evaporator 10 that absorbs latent heat from the conditioned air and evaporates the refrigerant has been described, the present invention is not limited to this, and the present invention is heat that performs heat exchange between fluids for various uses. Of course, it can be widely applied to general exchangers. Further, the above-described embodiment is also not limited to the refrigerant forward path, the end plate configuration, the pipe connection member configuration, and the like.
[Brief description of the drawings]
FIG. 1 (a) is an exploded perspective view showing the overall configuration of a heat exchanger in an embodiment of the present invention, and FIG. 1 (b) is a partial cross-sectional view showing an air passage between heat transfer plates.
2A and 2B show a heat transfer plate according to an embodiment of the present invention, in which FIG. 2A is a cross-sectional view of a tank portion, FIG. 2B is a cross-sectional view of a heat exchange portion before fitting, and FIG. It is sectional drawing of a heat exchange part.
3A and 3B show a conventional heat transfer plate, wherein FIG. 3A is a cross-sectional view of a tank portion, FIG. 3B is a cross-sectional view of a heat exchange portion before brazing, and FIG. 3C is a cross-section of a heat exchange portion after brazing. FIG.
[Explanation of symbols]
12 heat transfer plate 12a 1st heat transfer plate 12b 2nd heat transfer plate 12c fitting uneven part 13 substrate part 14a fitting convex part 15-18 tank parts 19 and 20 refrigerant passage (internal fluid passage)
21, 22 End plate, side plate member (member constituting the heat exchanger)
25, 30 Side plate, side plate member (member constituting the heat exchanger)
31 Piping joint block, piping connecting member (members constituting the heat exchanger)

Claims (6)

A pair of heat transfer plates (12a, 12b, 12) in which the internal fluid passage part and the tank part are integrally formed are stacked in a plurality of pairs while facing each other, and all the contact surfaces are joined.
Internal fluid passages (19, 20) through which an internal fluid flows inside the heat transfer plates (12a, 12b, 12), and tank portions (15-18) communicating with the internal fluid passages (19, 20). In the heat exchanger to form,
The heat transfer plate (12a, 12b, 12) is formed of a resin material, and a fitting convex portion (14a) that is fitted to a portion that forms the internal fluid passage (19, 20), and the tank portion (15-18) The heat exchanger characterized by providing the fitting uneven | corrugated part (12c) mutually fitted in the contact surface which forms (15-18) . The heat transfer plates (12a, 12b, 12) are characterized in that the tank portions (15-18) are made thicker than the plate thickness of the internal fluid passages (19, 20). The heat exchanger according to claim 1 .   The heat transfer plates (12a, 12b, 12) have substrate portions (13) that are joined in contact with each other, and the internal fluid passages (19, 19) projecting outward with respect to the substrate portions (13). 20) The heat exchanger according to claim 1 or 2, wherein the outer surface of the portion has a substantially trapezoidal shape.   The heat exchanger according to claim 1 or 2, wherein the heat transfer plate (12a, 12b, 12) has an inner surface of the internal fluid passage (19, 20) having a substantially circular shape. The members (21, 22, 25, 30, 31) constituting the heat exchanger other than the heat transfer plates (12a, 12b, 12 ) are also formed of a resin material. The heat exchanger according to any one of 4. The heat exchanger according to any one of claims 1 to 5, wherein the abutment surfaces are joined by bonding in assembling the heat exchanger.

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