Heat exchanger

Abstract

Heat exchanger (1) comprising: a finned plate layer body (2) in which a plurality of finned plates (6, 7) each with a flow path (11) are arranged layer by layer, wherein the flow path (11) is designed to cause a first fluid to flow in the flow path (11); end plates (3a, 3b) which are provided at both ends in a layering direction in the finned plate layer body (2); and an inlet and outlet piping (4, 5) connected to the end plates (3a, 3b) through which the first fluid, which flows in the flow path (11) of each of the finned plates (6, 7) in the finned plate layer body (2), flows, wherein the heat exchanger (1) is designed to cause a second fluid to flow between layers of the finned plate layer body (2), and thereby to effect a heat exchange between the first fluid and the second fluid, wherein each of the finned plates (6,7) two plate-shaped elements (6a, 6b, 7a, 7b) with recessed surfaces forming flow paths at opposite locations in order to shape the flow path (11) through the correspondingly recessed surfaces of the two opposing and mutually attached plate-shaped elements (6a, 6b, 7a, 7b), one of the plate-shaped elements (6a, 6b, 7a, 7b) being arranged at a position opposite one of the end plates (3a, 3b) in the ribbed plate layer body (2), and one plate-shaped element (6a, 6b, 7a, 7b) being arranged opposite the end plate (3a, 3b) being provided such that one side having the recessed surface comes into contact with the end plate (3a, 3b), each of the end plates (3a, 3b) a projecting section (30) which corresponds to at least part of the recessed area of ​​the plate element opposite the end plate (3a, 3b),and the projecting section (30) of the end plate (3a, 3b) comes into contact with at least a part of the recessed surface of one of the plate-shaped elements (6a, 6b, 7a, 7b), wherein each of the two plate-shaped elements (6a, 6b, 7a, 7b) forming the ribbed plate (6, 7) contains: a flow path region (P) with a plurality of recessed sections for first fluid flow paths (33) designed to form straight first fluid flow paths (33) in which the first fluid flows in parallel; and a head section (H) with a recessed section for the head section flow path (32) designed to form a head section flow path (32) which connects the straight primary fluid flow paths (33) and the inlet and outlet piping (4, 5); and the end plate (3a, 3b) has an end plate projection section (30) which corresponds to the recessed section for the head section flow path (32),which is formed in the head section flow path (32) in the head section area (H) of one of the plate elements opposite the end plate (3a, 3b), and the end plate projection section (30) comes into contact with the recessed section for the head section flow path (32), wherein a lower end face of the ribbed plate layer body (2) has recesses for flow path formation and the largest part of the lower end face is formed from a flat surface which is connected to the lower end plate (3b).

Description

TECHNICAL AREA The present disclosure relates to a heat exchanger and in particular to a heat exchanger with layered fin plates, designed by arranging plate-shaped fin plates in layers, in which a refrigerant flows. TECHNICAL BACKGROUND Heat exchangers, in which thermal energy is exchanged between fluids with different thermal energies, are used in numerous devices. A heat exchanger with layered finned plates is particularly widespread, for example in air conditioning units in residential buildings, or for vehicles, computers, various types of electrical appliances, and the like. The heat exchanger with finned plates in layered construction has a shape in which the heat exchange takes place between a fluid (a refrigerant) flowing in flow paths formed in the plate-shaped finned plates and a fluid (air) flowing between the layered finned plates. Various designs have been proposed for the above-described heat exchanger with finned plates in layered construction, the purpose of which is to reduce weight, reduce size and achieve a high efficiency of heat exchange (reference is made here, for example, to PTL 1 and PTL 2). As described above, in the field of finned plate heat exchangers with layered construction, a technique is employed in which the finned plates are made of a thin material with high thermal conductivity to reduce weight and size while achieving high efficiency. Furthermore, to increase the heat exchanger's capacity, a technique has been considered in which the fluid (the refrigerant) flows at a higher pressure than in conventional heat exchangers through the flow paths formed in the finned plates. In the field of heat exchangers, while the use of thin, high-thermal-conductivity materials for the finned plates is advantageous in terms of weight reduction, size reduction, and high efficiency, there are concerns that this could lead to problems with operational reliability. In particular, if the design involves the high-pressure refrigerant flowing through the flow paths formed in the finned plates, there is a risk that the refrigerant flow paths in the finned plates could deform, leading to fluctuations in the refrigerant flow rate and velocity, and consequently, a decrease in the heat exchanger's performance.Furthermore, in some cases a problem has arisen in that refrigerant leaks from the refrigerant flow paths in the thin finned plates. PTL3 describes a heat exchanger in which the height of one small elevation differs from the height of another elevation, creating a height difference between the top of the elevation and the top of the smaller elevation. This disrupts the airflow through the outer airflow path more than in the conventional case where the elevations are the same. PTL4 describes a plate heat exchanger comprising a plurality of main plates with fins and valleys to guide first and second fluid flows over the main plates and effect heat exchange between the fluids while keeping the first and second fluid flows separate. The heat exchanger further comprises a first end plate with first and second inlets and first and second outlets. The first end plate has a substantially flat inner surface configured to contact the fins of a first main plate from the plurality of main plates, and at least one slot formed in the substantially flat surface to provide a fluid connection of the first fluid flow between the inlet and a cavity formed by the first end plate and the first main plate. PTL5 describes a laminated heat exchanger in which the diameter of the first opening of a first frame is larger than the diameter of the first communication opening of a plate. This creates a labyrinthine space between the first communication opening of the pair of adjacent plates and the plate, as well as the first opening of the first frame. The presence of this labyrinthine space prevents the refrigerant from flowing axially along the tube. List of cited documents Patent literature PTL 1: Japanese Patent No.: JP 3 965 901 B2 PTL 2: Japanese Unexamined Utility Model Publication No. JP 3 192 719 UPTL 3: JP 2002 - 130 977 APTL 4: US 2014 / 0 196 870 A1 PTL 5: JP 2012 - 207 809 A SUMMARY OF THE INVENTION The present disclosure therefore aims to provide a heat exchanger with which a reduction in weight, a reduction in size and a high efficiency of heat exchange can be achieved and which operates with high reliability, even if the heat exchanger has a configuration in which a refrigerant in flow is under high pressure. A heat exchanger according to one aspect of the present invention is defined in claim 1. It includes, among other things, a finned plate stack body in which a plurality of finned plates, each with a flow path, are arranged layer by layer, the flow path being designed to cause a first fluid to flow in the flow path, end plates provided at both ends in the layering direction of the finned plate stack body, and inlet and outlet piping connected to the end plates through which the first fluid, flowing in the flow path of each of the finned plates in the finned plate stack body, flows. The heat exchanger causes a second fluid to flow between layers of the finned plate stack body, thereby effecting a heat exchange between the first fluid and the second fluid. Each of the finned plates contains two plate-shaped elements.Components with recessed surfaces at opposite locations that form a flow path, in order to shape the flow path through the correspondingly recessed surfaces of the two opposing and mutually attached, plate-shaped elements. One of the plate-shaped elements is arranged in a position opposite one of the end plates in the ribbed plate layer body. The plate-shaped element positioned opposite the end plate is designed such that one side, which has the recessed surface, comes into contact with the end plate. Furthermore, the heat exchanger comprises a finned plate stack body in which a plurality of finned plates, each with a flow path, are arranged layer by layer. The flow path is designed to cause a first fluid to flow within it. End plates are provided at both ends of the finned plate stack body in the layering direction. Inlet and outlet piping is connected to the end plates, and the first fluid, flowing in the flow path of each finned plate within the finned plate stack body, flows through these piping. The heat exchanger causes a second fluid to flow between the layers of the finned plate stack body, thereby facilitating heat exchange between the first and second fluids.Each of the finned plates contains a flow path region with a multitude of straight primary fluid flow paths, ensuring parallel flow of the primary fluid, and a head section with a head section flow path that connects the corresponding straight primary fluid flow paths within the flow path region to the inlet and outlet piping. Each end plate features a projecting section for flow path support, and this projecting section abuts an outer wall of the flow path within the finned plate, opposite the end plate. According to the present disclosure, a heat exchanger can be provided which achieves a reduction in weight, a reduction in size and a high efficiency and which operates with high reliability, even if the heat exchanger has a configuration in which a flowing refrigerant is under high pressure. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view showing an external appearance of a finned plate heat exchanger in a layered construction according to the disclosure. Fig. 2 is a top view showing a finned plate in the layered finned plate heat exchanger according to the present exemplary embodiment. Fig. 3 is an exploded view showing a portion of a finned plate configuration in the layered finned plate heat exchanger of the present exemplary embodiment. Fig. 4 is a view showing various cross-sectional shapes of a refrigerant flow path in the layered finned plate heat exchanger according to the present exemplary embodiment. Fig. 5 is a top view showing a portion of the finned plate in the finned plate layer body of the layered finned plate heat exchanger according to the present exemplary embodiment.Figure 6 is a perspective view showing a cross-section obtained when the finned plate layer body shown in Figure 5 is cut along line VI-VI. Figure 7 is a cross-sectional view showing part of a head section or refrigerant flow path resulting from the processing of plate elements of different thicknesses in the present exemplary embodiment. Figure 8 is a view showing that different finned plates are arranged layer by layer to form the finned plate layer body in the present exemplary embodiment. Figure 9 is a perspective view showing a cross-section obtained when the finned plate layer body shown in Figure 8 is cut along line IX-IX.Figure 10 is a perspective view showing a state in which positioning pins are fitted into the ribbed plate body in the present exemplary embodiment. Figure 11 is a view showing an enlarged cross-section of the ribbed plate body with fitted positioning pins in the present exemplary embodiment. Figure 12 is a top view of a ribbed plate having a modification of the exemplary embodiment disclosed. Figure 13 is a top view of a ribbed plate having a modification of the exemplary embodiment disclosed. Figure 14 is a top view of a ribbed plate having a modification of the exemplary embodiment disclosed. Figure 15 is a perspective view showing an upper end plate provided at an upper end of the ribbed plate body in the present exemplary embodiment.Figure 16 is a perspective view showing a lower end plate provided at a lower end of the ribbed plate layer body in the present exemplary embodiment. Figure 17 is an enlarged perspective view showing the head region and the upper end plate of the ribbed plate layer body in the present exemplary embodiment. Figure 18 is an enlarged perspective view showing a connection between the ribbed plate layer body and the lower end plate in the present exemplary embodiment. Figure 19 is an enlarged perspective view showing a connection between the ribbed plate layer body and a lower end plate, and in which a modification of the present exemplary embodiment according to the present disclosure is shown. Figure 20 is a top view showing a top surface of the ribbed plate layer body shown in Figure 16.Figure 19 shows the lower end plate. Figure 21 is an enlarged perspective view showing a connection between the ribbed plate layer body and a lower end plate, and showing a modification of the present exemplary embodiment according to the present disclosure. Figure 22A is a top view showing the lower end plate shown in Figure 21. Figure 22B is a side view showing the lower end plate shown in Figure 21. Figure 23 is an enlarged perspective view showing a connection between the ribbed plate layer body and a lower end plate, and showing a modification of the present exemplary embodiment according to the present disclosure. Figure 24A is a top view showing the lower end plate shown in Figure 23. Figure 24B is a side view showing the lower end plate shown in Figure 23.Fig. 25 is an enlarged perspective view showing a connection between the ribbed plate layer body and a lower end plate, and showing a modification of the present exemplary embodiment according to the present disclosure. Fig. 26 is a perspective view of the ribbed plate layer body, showing a modification of the exemplary embodiment according to the disclosure. DESCRIPTION OF THE EXECUTION FORM A heat exchanger according to a first aspect of the invention comprises a finned plate stack body in which a plurality of finned plates, each with a flow path, are arranged layer by layer. The flow path is designed to cause a first fluid to flow in the flow path. End plates are provided at both ends in the layering direction of the finned plate stack body, and inlet and outlet piping is connected to the end plates through which the first fluid, flowing in the flow path of each of the finned plates in the finned plate stack body, flows. The heat exchanger causes a second fluid to flow between layers of the finned plate stack body, thereby effecting a heat exchange between the first fluid and the second fluid.Each of the rib plates has two plate-shaped elements with recessed surfaces at opposite locations, forming the flow path through the corresponding recessed surfaces of the two opposing and mutually attached plate-shaped elements. One of the plate-shaped elements is positioned opposite one of the end plates in the rib plate assembly. The plate-shaped element positioned opposite the end plate is designed such that one side with the recessed surface is in contact with the end plate. In the heat exchanger of the first aspect according to the invention, each of the end plates has a projecting section which corresponds to at least a part of the recessed surface of the plate element opposite the end plate, and the projecting section of the end plate comes into contact with at least a part of the recessed surface of the one plate-shaped element. In the heat exchanger according to the first aspect, each of the end plates can have a recessed surface shape which corresponds to a shape of the recessed surface of the plate element opposite the end plate, and the recessed surface shape of the end plate and the recessed surface of the one plate-shaped element define the flow path in which the first fluid flows. In the heat exchanger of the first aspect according to the invention, each of the two plate-shaped elements that form the finned plate in the first aspect comprises: a flow path area with a plurality of recessed sections for primary fluid flow paths, designed to form straight primary fluid flow paths in which the primary fluid flows in parallel, and a head section area with a recessed section for the head flow path, designed to form a head flow path that connects the straight primary fluid flow paths to the inlet and outlet piping.The end plate has an end plate projection section which corresponds to the recessed section for the head section flow path, which is formed in the head section flow path in the head section area of ​​one of the plate elements opposite the end plate, and the end plate projection section comes into contact with the recessed section for the head section flow path. In the first aspect of the heat exchanger according to the invention, each of the two plate-shaped elements that form the finned plate comprises: a flow path region with a plurality of recessed sections for primary fluid flow paths, designed to form straight primary fluid flow paths in which the primary fluid flows in parallel, and a head section region with a recessed section for the head section flow path, designed to form a head section flow path that connects the straight primary fluid flow paths to the inlet and outlet piping. The end plate has a flow path region and an end section region with a configuration similar to that of the plate-shaped element opposite the end plate. In the heat exchanger of the first aspect, the head section areas can be provided on both sides of the finned plate, and the head section flow paths can have a symmetrical shape in the head section areas on both sides. In the heat exchanger of the first aspect, the head section of the finned plate can be located on one end face, and the inlet and outlet piping can be located at a point corresponding to the head section. A heat exchanger according to a second aspect of the invention comprises a finned plate stack body in which a plurality of finned plates, each with a flow path, are arranged layer by layer. The flow path is designed to cause a first fluid to flow in the flow path. End plates are provided at both ends in the layering direction of the finned plate stack body, and inlet and outlet piping is connected to the end plates through which the first fluid, flowing in the flow path of each of the finned plates in the finned plate stack body, flows. The heat exchanger causes a second fluid to flow between the layers of the finned plate stack body, thereby effecting a heat exchange between the first fluid and the second fluid.Each of the finned plates contains a flow path region with a multitude of straight primary fluid flow paths, ensuring parallel flow of the primary fluid, and a head section with a head section flow path that connects the corresponding straight primary fluid flow paths within the flow path region to the inlet and outlet piping. Each end plate features a projecting section for flow path support, and this projecting section abuts an outer wall of the flow path within the finned plate, opposite the end plate. In the heat exchanger according to the second aspect, the projecting section for flow path support of the end plate can have a straight ridge shape along the straight primary fluid flow paths. In the heat exchanger according to the second aspect, the projection section for flow path support of the end plate can consist of a multitude of projections arranged along a flow direction of the second fluid. The heat exchanger according to the second aspect may further include side plates designed to sandwich-like surround the two end plates on both sides in a direction perpendicular to the layering direction, with the two end plates being provided at both ends in the layering direction of the finned plate layer body. In the heat exchanger according to the second aspect, the finned plate can have head sections on both sides and the head flow paths in the head sections on both sides can have a symmetrical shape. In the heat exchanger according to the second aspect, the head section of the finned plate can be provided on one end face and the inlet and outlet piping can be provided at a location corresponding to the head section. In the following, a finned plate heat exchanger in a layered construction is described as an exemplary embodiment of the heat exchanger according to the disclosure, with reference to the accompanying drawings. The heat exchanger according to the disclosure is not limited to one embodiment of the layered finned plate heat exchanger described in the following embodiment, but also includes an embodiment of a heat exchanger that corresponds to the technical concept described in the following embodiment. The exemplary embodiment described below illustrates an example of the present disclosure, and the configurations, functions, operating modes, and the like described in the exemplary embodiment are examples and do not limit the present disclosure.Furthermore, with regard to the design elements in the following exemplary embodiment, those design elements that are not described in the independent claim which specifies the broadest concept are described as optional design elements. Fig. 1 is a perspective view showing the external appearance of a finned plate heat exchanger in a layered construction (hereinafter referred to as a heat exchanger for simplicity) 1 according to the present exemplary embodiment. As shown in Fig. 1, the heat exchanger 1 according to the present exemplary embodiment comprises: an inlet pipe (inlet head) 4 through which a refrigerant, representing a first fluid, is supplied; a finned plate layer body 2, which is formed by arranging a plurality of finned plates 2a in layers, each of which has a rectangular plate shape; and an outlet pipe (outlet head) 5 through which the refrigerant is discharged after it has flowed through a flow path formed in each of the finned plates 2a.In the present exemplary embodiment, the inlet pipe 4 and the outlet pipe 5 are collectively referred to as the inlet and outlet piping. Furthermore, at both ends of the ribbed plate assembly 2, which is formed by arranging the plurality of ribbed plates 2a in layers, end plates 3a and 3b are provided (at an upper and a lower end). These end plates, viewed from above, have essentially the same shape as the rectangular ribbed plates 2a. The end plates 3a and 3b are each made of a stiff plate material and are, for example, machined by grinding a metal material such as aluminum, an aluminum alloy, stainless steel, or the like to achieve their shape. The end plates 3a and 3b are arranged such that they sandwich the layered ribbed plates 2a from above and below, reliably maintaining a predetermined gap between the layered ribbed plates 2a. In the present exemplary embodiment, the layering direction of the finned plate layer body 2 is vertical, and the inlet and outlet piping 4, 5 are provided in the upper end plate 3a, which is located at the upper end of the finned plate layer body 2. In the upper end plate 3a, the inlet pipe 4 and the outlet pipe 5 are provided near end sections on both sides in the longitudinal direction of the finned plate layer body 2. Accordingly, the refrigerant flows first from the inlet pipe 4 in a horizontal direction into a plurality of flow paths formed inside each of the finned plates 2a and is discharged via the outlet pipe 5. In the heat exchanger 1 according to the present exemplary embodiment, which is configured as described above, the refrigerant flows as the first fluid parallel in the longitudinal direction through the plurality of flow paths inside each of the finned plates 2a of the finned plate assembly 2. Air, representing a second fluid, flows through gaps formed between layers of finned plates 2a in the finned plate assembly 2. The heat exchanger 1, configured as described above, facilitates heat exchange between the first fluid and the second fluid within the finned plate assembly 2. The finned plate layer body 2 in the heat exchanger 1 according to the present exemplary embodiment is formed by layering finned plates 2a (6, 7) with two types of flow path configurations. Two types of finned plates 2a, i.e., the first finned plates 6 and the second finned plates 7, are arranged in alternating order in the finned plate layer body 2. First, the first finned plates 6 used in the heat exchanger 1 according to the present exemplary embodiment are described. Fig. 2 is a top view showing the first finned plate 6. As shown in Fig. 2, the first finned plate 6 has the end sections H, which are formed at both ends in the longitudinal direction, and the flow path section P, which is formed between the end sections H on both sides. In each of the head section areas H, which are formed on both sides of the first finned plate 6, the head section opening 8 is formed, through which the refrigerant coming from the inlet pipe 4 or the refrigerant flowing into the outlet pipe 5 flows. Furthermore, in each of the head section areas H, the head section flow path 10 is formed, through which the refrigerant coming from the head section opening 8 or the refrigerant flowing into the head section opening 8 flows, and the head section flow paths 10 formed on both sides of the first finned plate 6 have a symmetrical shape. In the present exemplary embodiment, the head section flow paths 10 provided on both sides of the first finned plate 6 have a point-symmetrical shape, wherein, as described below, the center point of the first finned plate 6 as seen from above forms the center of symmetry. In the first finned plate 6, a plurality of refrigerant flow paths (first fluid flow paths) 11 are formed in the flow path region P, which is located between the head section regions H on both sides, to cause the refrigerant to flow from the inlet pipe 4 to the outlet pipe 5. The refrigerant flow paths 11 are arranged parallel to each other in the longitudinal direction and communicate on both sides with the head section flow paths 10 in the head section regions H. As shown in Fig. 2, each of the head openings 8, which are circular through-holes, is formed essentially on both sides at the center point of each of the head regions H, and each of the head flow paths 10, in which the refrigerant flows, is formed around the head opening 8. The head flow path 10 comprises the outer circumferential flow path 10a, which is shaped such that it forms a vertical bulge into the outer circumference of the head opening 8, with a circumferential flow path 10b extending a short distance from one side of the flow path region P (a mid-side of the first fin plate 6) into the outer circumferential flow path 10a, and a multi-branch flow path 10c connecting this circumferential flow path 10b to corresponding refrigerant flow paths 11 in the flow path region P.The head-section flow paths 10, which are formed on both sides of the first rib plate 6, have a symmetrical shape. For example, the circumferential flow path 10b of the left head-section flow path 10 shown in Fig. 2 extends from one side of the outer circumferential flow path 10a facing the flow path region P in one short direction of expansion (upwards according to Fig. 2), while the circumferential flow path 10b of the right head-section flow path 10 extends from the side of the outer circumferential flow path 10a facing the flow path region P in the other short direction of expansion (downwards according to Fig. 2). The head section flow paths 10 provided on both sides of the first rib plate 6 have a point-symmetrical shape, with the center point of the first rib plate 6 as seen in top view forming the center of symmetry. In each of the head section flow paths 10, the circulation flow path 10b, which extends in the short expansion direction of the finned plate 6, is connected to the multi-branch flow path 10c, which branches into and communicates with the multitude of refrigerant flow paths 11 running parallel in the flow path area P. A point where the circumferential flow path 10b is connected to the multi-branch flow path 10c is located on a flow path extension of the refrigerant flow path 11 at an outermost end section in the short extension direction of the first finned plate 6. Accordingly, as shown in Fig. 2, each of the head-section flow paths 10 is formed in a U-shape by the circumferential flow path 10b, which extends from the outer circumferential flow path 10a and the multi-branch flow path 10c, and is designed such that it is folded over or folded back by the circumferential flow path 10b and the multi-branch flow path 10c.The circulating flow paths 10b and the multi-branch flow paths 10c on both sides of the first finned plate 6 have a point-symmetrical shape, with the center point of the first finned plate 6, as seen from above, forming the center of symmetry. In the head-section flow path 10 designed in this way, the refrigerant, after flowing through the circulating flow path 10b, is subsequently or successively directed into the refrigerant flow paths 11, which are arranged to run parallel to each other from the outermost end region of the refrigerant flow path 11 in the short extension direction of the first finned plate 6. As shown in Fig. 2, a plurality of projections 12 (first dowels or pins or projections: 12a, second dowels or pins or projections: 12b) are formed in the flow path region P at predetermined intervals adjacent to the refrigerant flow paths 11. These projections 12 (12a, 12b) have two different shapes (which differ in particular in their projection length). The first pins 12a are flow path region support sections that project in an edge section (a lower edge section in Fig. 2) of the flow path region P. The first pins 12a are designed such that they abut the edge section of the flow path region P in the finned plate 2a adjacent in the layering direction in the finned plate layer body 2.In this way, the first pins 12a, which abut the edge section of the flow path region P in the adjacent rib plate 2a, reliably set a distance between the layers of adjacent rib plates 2a to a predetermined length. The second pins 12b are flow path support sections arranged at predetermined intervals between the flow paths of the refrigerant flow paths 11, which are parallel to each other in the flow path region P. In the present exemplary embodiment, the second pins 12b are arranged such that they are positioned side by side with the first pins 12a along a flow direction of the second fluid (the air). The second pins 12b are arranged such that they are opposite the refrigerant flow paths 11 in the finned plate 2a adjacent in the layering direction in the finned plate layer body 2 and abut the pipe walls (outer walls) of the refrigerant flow paths 11 in the adjacent finned plate 2a.In this way, since the second pins 12b abut the outer walls of the refrigerant flow paths 11 of the adjacent finned plate 2a, a gap between the adjacent finned plate 2a and the refrigerant flow path 11 can be reliably set to a predetermined length. The first pins 12a and the second pins 12b can be arranged in a zigzag pattern in the flow direction of the second fluid (the air: B in Fig. 2) that flows between the layers of the finned plate body 2, and at least the second pins 12b can be arranged in a zigzag pattern in the flow direction of the second fluid. This configuration creates turbulence in the second fluid flowing between the layers of the finned plate body 2, ensuring a consistent flow and thus increasing thermal conductivity. Furthermore, two positioning holes 13 are formed in each of the head section areas H of the first fin plate 6. These through holes are used for positioning purposes. The positioning holes 13 serve as positioning points when the multiple fin plates 2a (6, 7) are arranged in layers, and positioning pins are fitted into the positioning holes 13 to maintain a layer position with high accuracy relative to the other fin plates 2a. Regarding the positioning pins, an embodiment can be used in which the positioning pins are fixed or bonded in their inserted state within the positioning holes, thereby improving the structural strength of the heat exchanger. Alternatively, an embodiment can be used in which the positioning pins are ultimately withdrawn from the heat exchanger to reduce its weight or for similar reasons. Furthermore, a vertically protruding positioning outer circumferential section 13a is formed in an outer circumferential region of each of the positioning holes 13. This positioning outer circumferential section 13a is formed in a space that is distinct from the flow paths in which the refrigerant flows. The positioning outer circumferential sections 13a serve as head section support sections that abut between adjacent fin plates 2a (6, 7) in the stratification direction to assume a head section support function, which consists of maintaining a predetermined interval between fin plates 2a adjacent in the stratification direction. The head-section flow path 10 (10a, 10b, 10c) and the positioning outer circumferential sections 13a formed around the positioning holes 13, which are formed in each of the head-section regions H, are designed such that they project to a predetermined height from an upper and / or lower surface of the first rib plate 6. The projecting surfaces (an upper end face and a lower end face) in the head-section flow path 10 (10a, 10b, 10c) and the positioning outer circumferential sections 13a are formed as flat or planar surfaces. Accordingly, in the head-section flow path 10 (10a, 10b, 10c), with respect to a vertical cross-sectional shape perpendicular to the flow direction, the projecting sections (an upper end section and a lower end section) each have a flat or planar rectangular shape. In the present exemplary embodiment, the head-section flow path 10 and the positioning outer circumferential sections 13a are designed such that their height is half the height (1 / 2 the slope) of the gap (the distance) between adjacent rib plates 2a in the layering direction within the rib plate layer body 2. Therefore, in the head-section regions H of the adjacent rib plate 2a in the layering direction, the tube wall (the outer wall) of the head-section flow path 10 and the positioning outer circumferential section 13a abut the tube wall (the outer wall) of the opposite head-section flow path 10 and the opposite positioning outer circumferential section 13a. Since the adjacent outer walls of the head-section flow paths 10 are flat or planar surfaces, these surfaces can be reliably joined together, for example by soldering or the like.Accordingly, the head section areas H of corresponding rib plates 2a are located in the rib plate layer body 2 in a layered arrangement with preset, predetermined intervals. Fig. 3 is an exploded view showing a magnified portion of the first ribbed plate 6 within the ribbed plate assembly 2. The first ribbed plate 6 is made of a metal plate of aluminum, an aluminum alloy, stainless steel, or the like. The second ribbed plates 7 within the ribbed plate assembly 2, which are layered alternately with the first ribbed plates 6, are also made of the same material as the first ribbed plates 6. As shown in Fig. 3, the first ribbed plate 6 is formed by pressing together the first plate-shaped element 6a, which is obtained by subjecting a plate element with at least one core layer of solder material to a pressing process, and the second plate-shaped element 6b, which is obtained by subjecting a plate material of the same design to a pressing process. In the first plate-shaped element 6a and the second plate-shaped element 6b, the head-section flow path 10 and the positioning outer circumferential sections 13a around the positioning holes 13 in the head-section region H are formed, and the refrigerant flow paths 11 and the projections 12 (the first pins 12a and the second pins 12b) in the flow path region P are subjected to a pressing process and thereby formed into the corresponding shapes described above. As described above, the head section flow paths 10, each consisting of the outer circumferential flow path 10a formed in the head section area H, the circumferential flow path 10b and the multi-branch flow path 10c, and the positioning outer circumferential sections 13a formed around the positioning holes 13 are designed such that they project from the top and bottom of the first rib plate 6, and their height is equal to half the distance (1 / 2 slope) between adjacent rib plates 2a in the layering direction.Furthermore, the outer circumferential flow path 10a, the circumferential flow path 10b, and the multi-branch flow path 10c in each of the head-section flow paths 10 are configured such that they have a greater width than any of the refrigerant flow paths 11 that are provided parallel to each other in the flow path region P, and they have a rectangular vertical cross-sectional shape perpendicular to the flow direction. On the other hand, each of the refrigerant flow paths 11 configured in the flow path region P desirablely has a hydraulic diameter of 1 mm or less. In the present exemplary embodiment, an example is described in which a cross-sectional shape of the refrigerant flow paths 11 (a cross-sectional shape perpendicular to the direction in which the refrigerant flows) is circular; however, the present disclosure is not limited to the circular shape. In the present disclosure, the circular shape includes a composite curve formed from a circle, an ellipse, and a closed curve. Regarding the refrigerant flow paths 11 according to the present disclosure, as shown, for example, in Fig. 4, the cross-sectional shape perpendicular to the direction in which the refrigerant flows includes, in addition to the circular shape, rectangular shapes and the like, and includes a configuration of shapes projecting in the stratification direction on only one side, or of shapes projecting in the stratification direction on both sides. In Fig.Figure 4, which shows different cross-sectional shapes of each of the refrigerant flow paths, to indicate that the refrigerant flow path 11 is formed from the two plate-shaped elements, illustrates the two plate-shaped elements in a separate state, but in fact the two plate-shaped elements abut each other to form the refrigerant flow path 11 with the predetermined cross-sectional shape. Fig. 5 is a top view showing the head region H of the first plate 6 in the ribbed plate assembly 2 in close-up. Fig. 6 is a perspective view showing a cross-section obtained when the ribbed plate assembly 2 shown in Fig. 5 is cut along a line VI-VI. As can be seen from the ribbed plate assembly 2 in Fig. 6, the assembly is formed by alternating layers of first ribbed plates 6 and second ribbed plates 7. While Fig. 6 shows a state in which four ribbed plates (6, 7) are arranged in layers, this is only a part of the ribbed plate assembly 2, and a number of ribbed plates (6, 7) are arranged alternately in layers within the assembly. In the ribbed plate layer body 2, the outer walls (the flat or planar surfaces) of the head-section flow paths 10 abut the outer walls (the flat or planar surfaces) of the head-section flow paths 10 of the adjacent ribbed plate (6, 7) in the respective head-section regions H of the first ribbed plate 6 and the second ribbed plate 7. Fig. 6 shows that the flat or planar surface of the outer wall of the outer circumferential flow path 10a abuts the flat or planar surface of the outer wall of the outer circumferential flow path 10a of the adjacent ribbed plate (6, 7) in the layering direction. In the present exemplary embodiment, a high pressure is applied to the refrigerant flowing in the head section flow paths 10, but since the pipe walls (the outer walls) of the head section flow paths 10 are adhering orSince the pipe walls (outer walls) of the head section flow paths 10 are bonded to adjacent finned plates (6, 7), bulging of the pipe walls in the head section flow paths 10 is regulated, resulting in a pressure-resistant design. Therefore, in the design according to the present exemplary embodiment, the pressure of the refrigerant flowing in the head section flow paths 10 can be set high, and heat exchange with high efficiency and high operational reliability can take place. An embodiment can be used in which only the pipe walls of the head section flow paths 10 in the head section regions H are formed from thick sections with a greater thickness than elsewhere. Fig. 7 is a cross-sectional view showing a portion of the head section region H resulting from the processing of sheet materials of varying thicknesses by pressing. As shown in Fig. 7, the heat exchanger can be reliably operated with the refrigerant at higher pressure due to the design of the pipe wall sections of the head section flow path 10 in the head section regions H with the thick sections that have a greater thickness than in other sections. Furthermore, an embodiment can be used in which only the pipe walls of the refrigerant flow paths 11 in the flow path regions P are formed from thick sections with a greater thickness than at other locations, as shown in Fig. 7. Such an embodiment allows the refrigerant flow paths 11 to be operated with the refrigerant at a higher pressure. As shown in Fig. 6, in the finned plate layer body 2 according to the present exemplary embodiment, the first finned plates 6 and the second finned plates 7 are arranged alternately in layers. While the second finned plate 7 has a design and shape that are essentially similar to those of the first finned plate 6, the corresponding positions of the refrigerant flow paths 11 and the projections 12 (of the first pins 12a, of the second pins 12b) in the flow path region P differ from those in the first finned plate 6. Fig. 8 is a view showing that the first finned plate 6 and the second finned plate 7 are stacked on top of each other to form the finned plate assembly 2. As shown in Fig. 8, in the second finned plate 7, the refrigerant flow paths 11 in the flow path region P are positioned such that they are opposite the pins 12b of the first finned plate 6. That is, the refrigerant flow paths 11 in the flow path region P of the second finned plate 7 are arranged such that they are positioned opposite each other between the refrigerant flow paths 11 in the flow path region P of the first finned plate 6. In the finned plate assembly 2, in which the first finned plates 6 and the second finned plates 7 are arranged in layers, the second pins 12b, acting as flow path support sections, reliably abut the pipe wall (the outer wall) of the opposite refrigerant flow path 11. In the finned plate layer body 2 according to the present exemplary embodiment, the refrigerant flow paths 11 in the first finned plates 6 and the second finned plates 7, arranged alternately in layers thereto, are arranged in a zigzag pattern in a cross-section perpendicular to the direction in which the first fluid A flows in the flow path region P. For the specific design of this zigzag pattern, reference is made to Fig. 18 described later. Furthermore, the first pins 12a, designed as flow path area support sections in the edge section of the flow path area P of the second finned plate 7, abut the edge section of the flow path area P of the adjacent first finned plate 6 and are attached or bonded to it. Accordingly, the projection height of each of the first pins 12a as flow path area support sections is one height of the refrigerant flow path 11 higher than the projection height of each of the second pins 12b as flow path support sections. Fig. 9 is a perspective view showing a cross-section obtained when the ribbed plate layer body 2 shown in Fig. 8 is cut along line IX-IX. The ribbed plate layer body 2 shown in Fig. 9 is depicted in a state where only four of the ribbed plates are arranged in layers, starting from the top: the first ribbed plate 6, the second ribbed plate 7, the first ribbed plate 6, and the second ribbed plate 7. As shown in Fig. 9, the first pins 12a of the flow path region P in the first ribbed plate 6 abut the edge section of the flow path region P in the opposite second ribbed plate 7. Furthermore, the first pins 12a of the flow path region P in the second ribbed plate 7 abut the edge section of the flow path region P in the opposite first ribbed plate 6. On the other hand, the second pins 12b of the flow path area P in the first finned plate 6 abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the flow path area P in the opposite second finned plate 7. Furthermore, the second pins 12b of the flow path area P in the second finned plate 7 abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the flow path area P in the opposite first finned plate 6. The present disclosure gives a description of the embodiment in which the rib plates 2a (6, 7) arranged layer by layer in the rib plate layer body 2 are bonded together by soldering, but the present disclosure is not limited to this embodiment and other fastening methods in which heat resistance can be ensured, such as a mechanical joining method or a bonding method using a chemical bonding element, can also be used. As described above, in the ribbed plate layer body 2 according to the present exemplary embodiment, the first pins 12a in the flow path region P reliably support the edge section of the flow path region P of opposing ribbed plates (6, 7), thereby ensuring the predetermined gap between the layers. In the present exemplary embodiment, the first pins 12a in the flow path region P are the flow path region support sections in the ribbed plate layer body 2. Furthermore, the second pins 12b in the flow path region P abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the opposite first finned plate (6, 7), and a predetermined interval is maintained between the layers between the finned plate (6, 7) and the refrigerant flow paths 11 in the finned plate layer body 2. In the present exemplary embodiment, the second pins 12b in the flow path region P are the flow path support sections in the finned plate layer body 2. In the exemplary embodiment described above, the embodiment in which the first pins 12a abut the edge section of the flow path region P of the opposite rib plate (6, 7) was described; however, another embodiment can also be used. For example, an embodiment can be used in which the first pins 12a, which are designed as flow path region support sections in the edge section of the flow path region P, are designed as flow path region projection sections, wherein flow path region recession sections are formed in the edge section of the flow path region P of the opposite rib plate (6, 7) and the flow path region projection sections are fitted into the flow path region recession sections. [Layered arrangement using positioning pins] In the ribbed plate layer body 2 according to the present exemplary embodiment, the positioning pins 9 are mounted such that the plurality of ribbed plates 2a (6, 7) can be arranged layer by layer at predetermined positions in a simple and reliable manner. Fig. 10 is a perspective view showing a state in which the positioning pins 9 are fitted into the ribbed plate layer body 2. Fig. 11 is a view showing an enlarged cross-section of the ribbed plate layer body 2 with the positioning pins 9 fitted therein. The view in Fig. 11, which shows the cross-section, is a view obtained when the ribbed plate layer body 2 is sectioned along a surface indicated by the reference mark XI-XI in Fig. 10. In the present exemplary embodiment, each of the positioning pins 9 is inserted into the corresponding positioning hole 13, which is a through-hole formed in the head region H of the finned plate 2a (6, 7) and soldered in place. This strengthens the mechanical structure of the finned plate layer body 2 and significantly increases its refrigerant pressure absorption capacity. In the present exemplary embodiment, an aluminum metal rod is used as the positioning pin 9. In the present exemplary embodiment as shown in Fig. 2, the first pins 12a and the second pins 12b, forming flow path support sections within the flow path region P, are arranged side by side parallel to the flow direction of the air as the second fluid B. In this way, since a plurality of projections are arranged side by side between the layers, the flow path resistance to the second fluid (the air) B, which flows between the layers in the ribbed plate body 2, can be reduced. This design reduces the noise generated while the second fluid flows between the layers in the ribbed plate body 2 according to the present embodiment. [Modification of the rib plate] As a modification of the finned plate 2a in the finned plate layer body 2 of the heat exchanger according to the disclosure, an embodiment can be cited in which the arrangement of the projections or dowels or pins 12 (12a, 12b) is modified. For example, an embodiment can be used in which the plurality of projections 12 (12a, 12b) provided between the layers in the finned plate layer body 2 are arranged in a zigzag pattern, thereby generating turbulence in the second fluid B flowing between the layers in order to increase the heat exchange efficiency. Fig. 12 is a top view of the finned plate 2b, which shows the embodiment in which the plurality of projections 12 (12a, 12b) are arranged in a zigzag pattern between the layers in the finned plate layer body 2.In this configuration, the first pins 12a, as flow path area support sections, also abut the edge section of the opposite flow path area P, and the second pins 12b, as flow path support sections, abut the pipe wall (the outer wall) of the refrigerant flow paths 11 in the opposite flow path area P. Furthermore, an embodiment can be used in which more projections 12 are formed between the layers on a side facing away from the flow than on a side facing the flow. These projections generate turbulence in the second fluid B as it flows between the layers, thereby increasing the heat exchange efficiency. At least a number of first pins 12a in the projections 12 can be larger on the side facing away from the flow than those on the side facing the flow in the direction of flow of the second fluid B (the air). In this way, more projections 12 are provided on the side facing away from the flow than on the side facing the flow, thus increasing the thermal conductivity on the side facing away from the flow, where the flow velocity slows down. Fig.Figure 13 is a top view of the ribbed plate 2c, which shows the configuration in which more projections 12 are provided on the side facing away from the flow than projections 12 are present on the side facing the flow in the direction of the air flow as the second fluid B. In this configuration, the first pins 12a, as flow path area support sections, also abut the edge section of the opposite flow path area P, and the second pins 12b, as flow path support sections, abut the pipe wall (the outer wall) of the refrigerant flow paths in the opposite flow path area P. As described above, various configurations can be offered with regard to the arrangement of the plurality of projections 12, which are provided between the layers of the finned plate body 2 in the present exemplary embodiment, and an optimal configuration can be selected in accordance with a specification, a design and a requirement of a user of the heat exchanger. Furthermore, a further modification of the finned plate layer body 2 in the heat exchanger 1 is described. In the finned plate layer body 2 in the preceding exemplary embodiment, the inlet pipe 4 and the outlet pipe 5 are connected to the surroundings of the end sections on both sides in the longitudinal direction, and head section areas H are formed on both sides of the finned plate 2a, and two head section openings 8 are provided (see Fig. 2). Fig. 14 is a view showing a modification of the ribbed plate body, specifically a top view of the ribbed plate 2d representing the ribbed plate body. As shown in Fig. 14, the head section H is formed only in one end section of the ribbed plate 2d (on the left side in Fig. 14), with the remaining area representing the flow path region P. In the ribbed plate body according to this modification, the inlet pipe and the outlet pipe are connected in the longitudinal direction at a point close to one end section. In the ribbed plate 2d shown in Fig. 14, the head opening 8a on an inlet side and the head opening 8b on an outlet side are formed in the head section H shown on the left side. In the finned plate 2d shown in Fig. 14, the opening shape of the head section opening 8a on the inlet side has a larger diameter than the opening shape of the head section opening 8b on the outlet side. This is because, when the heat exchanger is used as a condenser, the volume of the refrigerant decreases after the heat exchange. Furthermore, the refrigerant flows from the head section opening 8a on the inlet side into a plurality of refrigerant flow paths 11a, which are provided parallel to each other in the flow path region P, and flows back into the finned plate 2d near an end section (near a right end section in Fig. 14).In the flow path region P, refrigerant flow paths 11a are formed, into which the refrigerant flows from the head opening 8a on the inlet side, and refrigerant flow paths 11b are formed, from which the refrigerant flows back into the head opening 8b on the outlet side after the flow reversal that occurs near the end section. When the heat exchanger is used as an evaporator, the inlet and outlet openings are dimensioned in reverse compared to the previous description. As shown in Fig. 14, a number of parallel refrigerant flow paths 11b, through which the refrigerant flows to the head opening 8b on the outlet side, are smaller than a number of parallel refrigerant flow paths 11a, into which the refrigerant flows from the head opening 8a on the inlet side. The reason for this is the same as the reason for the different diameters of the head openings 8a and 8b, namely that the volume of the refrigerant decreases after the heat exchange has been completed. Furthermore, in the finned plate 2d, which has the configuration shown in Fig. 14, a plurality of holes 16 are formed to reduce heat conduction in the refrigerant inside the finned plate (thermal insulation), namely between an area in which the refrigerant flow paths 11a are formed, into which the refrigerant flows from the head opening 8a on the inlet side, and an area in which the refrigerant flow path 11b is formed, from which the refrigerant flows out into the head opening 8b on the outlet side. [End plate] Next, the end plates (3a, 3b) are described, which are provided at both ends (the upper and the lower end) in the finned plate layer body 2 of the heat exchanger 1 according to the present exemplary embodiment. Fig. 15 is a perspective view showing an upper end plate 3a provided at an upper end in the layering direction of the finned plate layer body 2, and Fig. 16 is a perspective view showing a lower end plate 3b provided at a lower end in the layering direction of the finned plate layer body 2. Fig. 17 is an enlarged perspective view showing a connection between the head section H and an upper end plate 3a in the finned plate layer body 2. In the present exemplary embodiment according to the preceding description, the first ribbed plate 6 and the second ribbed plate 7, which constitute the ribbed plate layer body 2, are formed by causing the two plate-shaped elements (6a and 6b, 7a and 7b) to adhere to each other. That is, the first ribbed plate 6 is formed by causing the first plate-shaped element 6a and the second plate-shaped element 6b, which have previously undergone pressing, to adhere to each other, and the second ribbed plate 7 is formed by causing the first plate-shaped element 7a and the second plate-shaped element 7b, which have previously undergone pressing, to adhere to each other. In the ribbed plate assembly 2 according to the present exemplary embodiment, the first ribbed plates 6 and the second ribbed plates 7 are arranged alternately in layers, and in an uppermost end section of the ribbed plate assembly 2, only the second plate-shaped element 6b is arranged, which is a side of the first ribbed plate 6 (see Fig. 17). Accordingly, an upper end face of the ribbed plate assembly 2 has recesses, which are thin grooves for flow path formation; however, the majority of this uppermost end face is formed by a flat or planar surface. Therefore, the flat or planar surface in the uppermost end face of the ribbed plate assembly 2 represents a connecting surface (a soldering surface) that is in contact with an underside of the upper end plate 3a, thus creating a large-area connection area. As shown in Fig. 17, end plate projection sections 30 are formed in a surface of the upper end plate 3a, which is arranged on the upper end face of the ribbed plate layer body 2, with this surface of the upper end plate 3a being opposite the ribbed plate layer body 2. Each of these end plate projection sections 30 has a shape that corresponds to the recess for flow path formation in the opposite second plate-shaped element 6b. Therefore, when the upper end plate 3a is arranged on an upper end face of the ribbed plate layer body 2, the end plate projection sections 30 of the upper end plate 3a are fitted into the recesses for flow path formation in the second plate-shaped element 6b. The end plate projection sections 30 formed in the upper end plate 3a may, under certain circumstances, only be designed for wider recessed sections for flow path formation in the head section region H. This is because the recessed sections (grooves) for flow path formation in the flow path region P are narrower, so that a sufficient contact area can be ensured. In the present exemplary embodiment, the example described is one in which, as a specific example, the second plate-shaped element 6b of the first ribbed plate 6 is arranged as the uppermost surface of the ribbed plate layer body 2; however, this is only one example, and the uppermost surface of the ribbed plate layer body 2 can also be configured by any other side in the first ribbed plate 6 or the second ribbed plate 7 according to the layering sequence. Fig. 18 is an enlarged perspective view showing the connection between a lower end face of the ribbed plate body 2 and the lower end plate 3b. As shown in Fig. 18, in the present exemplary embodiment, only the first plate-shaped element 7a, which is one side of the second ribbed plate 7, is arranged in a lower end section of the ribbed plate body 2. Accordingly, a lower end face of the ribbed plate body 2 has recesses for flow path formation, but the majority of this lower end face is formed from a flat surface. Thus, a sufficient connection area between the lower end face of the ribbed plate body 2 and the lower end plate 3b is ensured. [Modification of the ribbed plate layer body and the end plate] Figs. 19, 20, 21, 22, 23, 24 to 25 are views showing various modifications of the ribbed plate layer body and the end plates. Fig. 19 is an enlarged perspective view showing the connection between a lower end face of the finned plate assembly 2 and the lower end plate 31b. As shown in Fig. 19, the first plate-shaped element 7a, which is a side of the second finned plate 7, is located at the lower end of the finned plate assembly 2. The lower end face of the finned plate assembly 2 is formed from a surface with downwardly recessed areas of recessed sections for the first fluid flow paths 11a, each of which represents an upper half of the refrigerant flow path 11 as the first fluid flow path in the first plate-shaped element 7a. The surface with the recessed areas (grooves) of the recessed sections for the first fluid flow paths 11a faces downwards and is in contact with the upper surface of the lower end plate 31b. Fig. 20 is a top view showing the upper surface of the lower end plate 31b. As shown in Fig. 19 and Fig. 20, the flow path region P and the head section H are arranged in the upper surface of the lower end plate 31b, having the same configuration as the first plate-shaped element 7a, which is opposite the lower end plate 31b. That is, the head sections H are formed on both sides in the longitudinal direction of the lower end plate 31b, and the flow path region P is formed in a central section sandwiched between the head sections H. As shown in Fig. 20, in the head section areas H in the upper surface of the lower end plate 31b, recessed sections are formed to create the head section flow paths 32, and in the flow path area P, a plurality of straight recessed sections are formed parallel to each other to create the refrigerant flow paths (grooves) 33. The recessed sections for forming the head section flow paths 32 in the head section areas H in the lower end plate 31b are each designed as a recessed section with a base that has a circular shape, essentially corresponding to the circular shape of the head section opening 8 in the finned plate (6, 7). These recessed sections for forming the head section flow paths 32 insulate the refrigerant from the head section openings 8, which communicate with the supply and return piping. As described above, the recessed sections for forming the refrigerant flow paths (grooves) 33 of the flow path region P formed in the lower end plate 31b are located at the same positions and have the same shape as the recessed sections for forming the refrigerant flow paths 11a formed in the first plate-shaped element 7a, which is one side of the opposite second finned plate 7. Thus, in the lower end plate 31b, the head-side flow paths, which serve for refrigerant accumulation, are formed in the head-side regions H by the first plate-shaped element 7a opposite the lower end plate 31b, and the same refrigerant flow paths are formed in the flow path region P as the refrigerant flow paths 11 in the finned plate layer body 2.Consequently, in the heat exchanger designed in this way, the lower end plate 31b and the first plate-shaped element 7a at the lower or lowest end form the refrigerant flow paths, thereby realizing a design in which the heat exchange efficiency can be further increased. The upper or topmost end face of the finned plate layer body 2 and the underside of the upper end plate can also have a design similar to the design of the lower end face of the finned plate layer body 2 and the lower end plate 31b shown in Fig. 19 and Fig. 20, and the refrigerant flow paths can be formed between the upper end face of the finned plate layer body 2 and the underside of the upper end plate. Figures 21 and 22A, 22B are views showing the ribbed plate assembly 21 and the lower end plate 34b in a further embodiment. Figure 21 is an enlarged perspective view showing a connection between a lower end of the ribbed plate assembly 21 and the lower end plate 34b. Figure 22A is a top view showing the upper surface of the lower end plate 34b. Figure 22B is a side view of the lower end plate 34b. In the embodiment shown in Figure 21, the second ribbed plate 7 is arranged in the lower end section of the ribbed plate assembly 21. This means that in this modification the ribbed plate layer body 21 is designed by arranging the first ribbed plate 6 and the second ribbed plate 7, which are formed by making the two plate-shaped elements (6a and 6b, 7a and 7b) adhere or bond to each other, alternately in layers.Accordingly, in the present modification, either the first ribbed plate 6 or the second ribbed plate 7 is arranged at the lower end of the ribbed plate layer body 21 in accordance with the layering sequence. As shown in Fig. 22A and Fig. 22B, a plurality of projections (35, 36) are formed on the upper surface of the lower end plate 34b to support, for example, the second finned plate 7 located at the lower end of the finned plate layer body 21. The plurality of projections (35, 36) formed on the upper surface of the lower end plate 34b is subdivided into projection sections for flow path support 35, which support the refrigerant flow paths 11 of the second finned plate 7, and projection sections for flow path area support 36, which support the flow path area P of the second finned plate 7. As shown in Fig. 21, the projection sections for flow path support 35 and the projection sections for flow path area support 36 have two different shapes (in particular, the projection lengths differ). The projecting sections for flow path area support 36 of the lower end plate 34b are designed such that they abut the edge section of the flow path area P in the second rib plate 7. Thus, the projecting sections for flow path area support 36, which abut the edge section of the flow path area P in the second rib plate 7, reliably set a predetermined distance between the lower end plate 34b and the second rib plate 7. The projecting sections for flow path support 35 are the flow path support sections and are arranged at points on the refrigerant flow paths 11, which are parallel to each other in the flow path area P of the opposite second finned plate 7. In the present modification, the projecting sections for flow path support 35 are arranged such that they are positioned side by side together with the projecting sections for flow path area support 36 along the flow direction of the second fluid (the air). The projecting sections for flow path support 35 are arranged such that they are opposite the refrigerant flow paths 11 and abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the second finned plate 7.Since the projecting sections for flow path support 35 abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the second finned plate 7, a gap between the top of the lower end plate 34b and the second finned plate 7 at the lower end can be reliably set to a predetermined length. The multitude of projections (35, 36) formed in the upper surface of the lower end plate 34b can be arranged in a zigzag pattern with respect to the flow direction of the fluid (air: B) flowing in the ribbed plate layer body 21. Furthermore, more projections (35, 36) can be formed on the side facing away from the flow than on the side facing the flow. The upper end face of the ribbed plate layer body 21 and the underside of the upper end plate can also have a design similar to the design of the lower end face of the ribbed plate layer body 21 and the lower end plate 34b shown in Fig. 21 and Fig. 22A and Fig. 22B. Figures 23 and 24A, 24B are views showing the lower end plate 37b with a further embodiment. Figure 23 is an enlarged perspective view showing a connection between the lower end of the ribbed plate layer body 21 and the lower end plate 37b. Figure 24A is a top view showing the upper surface of the lower end plate 37b. Figure 24B is a side view of the lower end plate 37b. In one embodiment shown in Figure 23, the ribbed plate layer body 21 has the same configuration as the embodiment of the ribbed plate layer body 21 shown previously in Figure 21.This means that in this modification the ribbed plate layer body 21 is designed by arranging the first ribbed plate 6 and the second ribbed plate 7 alternately in layers and by arranging either the first ribbed plate 6 or the second ribbed plate 7 at the lower end of the ribbed plate layer body 21 in accordance with the layering sequence. As shown in Fig. 24A and Fig. 24B, a plurality of longitudinally extending projection sections (38, 39) are formed in the upper surface of the lower end plate 37b to support, for example, the second finned plate 7 located at the lower end of the finned plate layer body 21. The plurality of projection sections (38, 39), which project ridge-like from the upper surface of the lower end plate 37b, is subdivided into projection sections for flow path support 38, which support the refrigerant flow paths 11 of the second finned plate 7, and projection sections for flow path area support 39, which support the flow path area P of the second finned plate 7. As shown in Fig.As shown in Figure 23, the projection sections for flow path support 38 and the projection sections for flow path area support 39 have two different shapes (in particular, the projection lengths differ from each other). The projecting sections for flow path area support 39 of the lower end plate 37b are designed such that they abut the edge section of the flow path area P in the second rib plate 7. Thus, the projecting sections for flow path area support 39, which abut the edge section of the flow path area P in the second rib plate 7, reliably set a predetermined distance between the lower end plate 37b and the second rib plate 7. The projecting sections for flow path support 38 are the flow path support sections and are arranged at points on the refrigerant flow paths 11 that are parallel to each other in the flow path region P of the opposite second finned plate 7. The projecting sections for flow path support 38 are arranged such that they are opposite the refrigerant flow paths 11 and reliably abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the second finned plate 7. Since the projecting sections for flow path support 38 abut the pipe walls (the outer walls) of the refrigerant flow paths 11 of the second finned plate 7, a gap between the upper surface of the lower end plate 37b and the second finned plate 7 at the lower end can be reliably adjusted to a predetermined length. The upper end face of the ribbed plate layer body 21 and the underside of the upper end plate can also have a design similar to the design of the lower end face of the ribbed plate layer body 21 and the lower end plate 37b shown in Fig. 23 and Fig. 24A and Fig. 24B. Fig. 25 is a view showing the lower end plate 40b with a further embodiment. Fig. 25 is an enlarged perspective view showing a connection between the lower end of the ribbed plate layer body 21 and the lower end plate 40b. In one embodiment shown in Fig. 25, the ribbed plate layer body 21 has the same configuration as the embodiment of the ribbed plate layer body 21 shown previously in Fig. 21. In the embodiment shown in Fig. 25, projections 35 are formed on the upper surface of the lower end plate 40b as projection sections for flow path support and projections 36 as projection sections for flow path area support, which are described above under Fig. 21. In addition, pin-supporting or...Pin-like supporting projection sections 41 are formed, which are arranged at the lower end of the finned plate layer body 21 and abut and are connected to, for example, the second pins 12b, which serve as flow path support sections in the second finned plate 7. The pin-supporting or pin-like supporting projection sections 41 are longitudinally extending, ridge-shaped, or raised projection sections and extend between the refrigerant flow paths 11 in the opposite second finned plate 7. Furthermore, the pin-supporting or pin-like supporting projection sections 41 each have a sufficient height to reliably abut the second pins 12b, which are provided between the refrigerant flow paths 11 in the second finned plate 7.The first pins 12a, which are formed in the edge section of the ribbed plate (6, 7) arranged at the lower end of the ribbed plate layer body 21, each have a sufficient height to abut the top of the lower end plate 40b. The upper end face of the ribbed plate layer body 21 and the underside of the upper end plate can also have a design similar to the design of the lower end face of the ribbed plate layer body 21 and the lower end plate 40b shown in Fig. 25. Furthermore, as explained in the preceding modification from Fig. 14, the embodiments of the modifications shown in Fig. 19, Fig. 20, Fig. 21, Fig. 22, Fig. 23, Fig. 24 to Fig. 25 can of course also be applied to the embodiment example in which the head section H is formed on only one end section side (on the left side in Fig. 14) of the ribbed plate in the ribbed plate layer body. [Side panel] Fig. 26 is a perspective view showing a modification in which a pair of side plates 17, 18 are provided to sandwich-like surround the end plates 3a, 3b, located at the top and bottom of the finned plate body 2, in the heat exchanger according to the disclosure. The modification shown in Fig. 26 is designed such that, in the finned plate body 2, one side of a side on the side of one head section H, to which the inlet pipe 4 is connected, is sandwich-like surrounded from above and below by the first side plate 17. Furthermore, in the finned plate body 2, one side of a side on the side of the other head section H, to which the outlet pipe 5 is connected, is sandwich-like surrounded from above and below by the second side plate 18.The first side plate 17 has an upper opening 17a through which the inlet pipe 4 passes, and a side surface opening 17b is formed so that air, as a second fluid B, can flow into the head section of the ribbed plate layer body 2. Similarly, the second side plate 18 has an upper opening 18a through which the outlet pipe 5 passes, and a side surface opening 18b is formed so that air, as a second fluid B, can flow into the head section H of the ribbed plate layer body 2. As described above, in the modification shown in Fig. 26, since the pair of side plates 17, 18 is provided to sandwich-like surround the sections of the head section H from both sides of the finned plate layer body 2, even if the thickness of the end plates 3a, 3b is reduced and the design simplified, the pipe walls of the head section flow paths 10 in the head section areas H in the finned plates 2a, which constitute the finned plate layer body 2, can be safely pressed together with a predetermined pressure force from above and below. With the finned plate layer body 2 designed in this way, it is possible to allow the refrigerant to flow in the finned plate layer body 2 at a high set pressure, thereby enabling highly efficient heat exchange. Although Figure 26 describes an embodiment of the finned plate layer body 2 shown in Figure 1, the pair of side plates 17, 18 can also be provided in the embodiments described with reference to Figures 19, 20, 21, 22, 23, 24 to 25 in order to sandwich the finned plate layer body from above and below. In the embodiments according to the modifications described above, it is possible to safely compress the finned plate layer body with a predetermined pressure from above and below and to allow the refrigerant to flow into the finned plate layer body at a high set pressure, thereby enabling highly efficient heat exchange. As described above, the design of the heat exchanger according to the disclosure allows for a reduction in weight, a reduction in size and a high efficiency of heat exchange, and provides a heat exchanger with high operational reliability and a high heat exchange efficiency, even in a design in which the refrigerant under high pressure flows in the finned plates of the finned plate layer body. INDUSTRIAL APPLICABILITY The present disclosure provides a heat exchanger which is a weight-reduced and size-reduced device that performs an extremely reliable, highly efficient heat exchange and thereby achieves a high market value. REFERENCE MARKS IN THE DRAWINGS 1 Heat exchanger 2 Finned plate layer body 2a Finned plate 3 End plate 4 Inlet pipe (inlet head) 5 Outlet pipe (outlet head) 6 First finned plate 7 Second finned plate 8 Head opening 9 Positioning pin 10 Head flow path 10a Outer circumferential flow path 10b Circulation flow path 10c Multi-branch flow path 11 Refrigerant flow path (first fluid flow path) 12 Projection 12a First pin (flow path area support section) 12b Second pin (flow path support section) 13 Positioning hole 13a Positioning outer circumferential section (head area support section) 17 First side plate 18 Second side plate

Claims

Heat exchanger (1) comprising: a finned plate layer body (2) in which a plurality of finned plates (6, 7) each with a flow path (11) are arranged layer by layer, wherein the flow path (11) is designed to cause a first fluid to flow in the flow path (11); end plates (3a, 3b) which are provided at both ends in a layering direction in the finned plate layer body (2); and an inlet and outlet piping (4, 5) connected to the end plates (3a, 3b) through which the first fluid, which flows in the flow path (11) of each of the finned plates (6, 7) in the finned plate layer body (2), flows, wherein the heat exchanger (1) is designed to cause a second fluid to flow between layers of the finned plate layer body (2), and thereby to effect a heat exchange between the first fluid and the second fluid, wherein each of the finned plates (6,7) two plate-shaped elements (6a, 6b, 7a, 7b) with recessed surfaces forming flow paths at opposite locations in order to shape the flow path (11) through the correspondingly recessed surfaces of the two opposing and mutually attached plate-shaped elements (6a, 6b, 7a, 7b), one of the plate-shaped elements (6a, 6b, 7a, 7b) is arranged at a position opposite one of the end plates (3a, 3b) in the ribbed plate layer body (2), and one plate-shaped element (6a, 6b, 7a, 7b) which is arranged so that it is opposite the end plate (3a, 3b) is provided such that one side having the recessed surface comes into contact with the end plate (3a, 3b), each of the end plates (3a, 3b) has a projecting section (30) which corresponds to at least part of the recessed area of ​​the plate element opposite the end plate (3a, 3b),and the projecting section (30) of the end plate (3a, 3b) comes into contact with at least a part of the recessed surface of one of the plate-shaped elements (6a, 6b, 7a, 7b), wherein each of the two plate-shaped elements (6a, 6b, 7a, 7b) forming the ribbed plate (6, 7) contains: a flow path region (P) with a plurality of recessed sections for first fluid flow paths (33) designed to form straight first fluid flow paths (33) in which the first fluid flows in parallel; and a head section (H) with a recessed section for the head section flow path (32) designed to form a head section flow path (32) which connects the straight primary fluid flow paths (33) and the inlet and outlet piping (4, 5); and the end plate (3a, 3b) has an end plate projection section (30) which corresponds to the recessed section for the head section flow path (32),which is formed in the head section flow path (32) in the head section area (H) of one of the plate elements opposite the end plate (3a, 3b), and the end plate projection section (30) comes into contact with the recessed section for the head section flow path (32), wherein a lower end face of the ribbed plate layer body (2) has recesses for flow path formation and the largest part of the lower end face is formed from a flat surface which is connected to the lower end plate (3b). Heat exchanger (1) according to claim 1, wherein each of the end plates (3a, 3b) has a recessed surface shape which corresponds to a shape of the recessed surface of the one plate-shaped element (6a, 6b, 7a, 7b) opposite the end plate (3a, 3b), and the recessed surface shape of the end plate (3a, 3b) and the recessed surface of the one plate-shaped element (6a, 6b, 7a, 7b) form the flow path (11) in which the first fluid flows. Heat exchanger (1) according to claim 1 or claim 2, wherein the finned plate (6, 7) has head sections (H) on both sides and the head section flow paths (32) have a symmetrical shape in the head section sections (H) on both sides. Heat exchanger (1) according to claim 1 or claim 2, wherein the finned plate (6, 7) has the head section (H) on an end face and the inlet and outlet piping (4, 5) is provided at a location corresponding to the head section (H). Heat exchanger (1) comprising: a finned plate layer body (2) in which a plurality of finned plates (2a, 6, 7) each with a flow path (11) are arranged layer by layer, wherein the flow path (11) is designed to cause a first fluid to flow in the flow path (11); end plates (3a, 3b) which are provided at both ends in a layering direction in the finned plate layer body (2);and an inlet and outlet piping (4, 5) connected to the end plates (3a, 3b) through which the first fluid, which flows in the flow path (11) of each of the finned plates (2a, 6, 7) in the finned plate layer body (2), flows, wherein the heat exchanger (1) is designed to cause a second fluid to flow between layers of the finned plate layer body (2), thereby effecting a heat exchange between the first fluid and the second fluid, wherein each of the finned plates (2a, 6, 7) contains: a flow path region (P) with a plurality of straight first fluid flow paths (11), such that the first fluid flows in parallel; and a head section area (H) with a head section flow path (10) which forms the connection between the corresponding straight first fluid flow paths (11) in the flow path area (P) and the inlet and outlet piping (4, 5);and each of the end plates (3a, 3b) has a projecting section for flow path support (35) and the projecting section for flow path support (35) is arranged at points of the flow path (11) that are parallel to each other in the flow path area (P) of the opposite plate rib (2a, 6, 7) and abuts an outer wall of the flow path (11) in the rib plate (2a, 6, 7) which is opposite the end plate (3a, 3b). Heat exchanger (1) according to claim 5, wherein the projection section for flow path support (35) of the end plate (3a, 3b) has a straight ridge shape along the straight primary fluid flow paths (11). Heat exchanger (1) according to claim 5, wherein the projection section for flow path support (35) of the end plate (3a, 3b) comprises a plurality of projections arranged along a flow direction of the second fluid. Heat exchanger (1) according to one of claims 1 to 7, further comprising side plates (17, 18) which are designed to sandwich-like surround the two end plates (3a, 3b) on both sides in a direction perpendicular to the layering direction, wherein the two end plates (3a, 3b) are provided at both ends in the layering direction of the finned plate layer body (2). Heat exchanger (1) according to one of claims 5 to 8, wherein the finned plate (2a, 6, 7) has head sections (H) on both sides and the head section flow paths (10) have a symmetrical shape in the head section sections (H) on both sides. Heat exchanger (1) according to one of claims 5 to 8, wherein the finned plate (2a, 6, 7) has the head section (H) on an end face and the inlet and outlet piping (4, 5) is provided at a location corresponding to the head section (H).

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