Plate heat exchanger and heat transfer device
Patent Information
- Authority / Receiving Office
- DE · DE
- Patent Type
- Patents
- Current Assignee / Owner
- MITSUBISHI ELECTRIC CORP
- Filing Date
- 2019-06-03
- Publication Date
- 2026-07-23
AI Technical Summary
Existing plate heat exchangers using low GWP refrigerants like R32 or R290 face challenges in preventing fluid leakage due to potential cracks between heat transfer plates, leading to mixing of fluids and safety hazards, especially when exposed to varying manufacturing and environmental conditions.
The design incorporates first and second heat transfer plates with recessed and projected inner fins, forming a space between them, where the second spacer portions are wider than first spacer portions, ensuring that the plates remain non-contact areas are always weaker and prone to breakage, thus preventing fluid mixing.
This configuration enhances safety by ensuring that fluid leakage occurs only at non-contact areas, preventing inflammable refrigerants from entering the building, while maintaining effective heat exchange and reducing manufacturing costs.
Smart Images
Figure 00000000_0000_ABST
Abstract
Description
Technical field
[0001] The present disclosure relates to a plate heat exchanger and a heat transfer device. In a plate heat exchanger, a plurality of pairs of first heat transfer plates, in which a first fluid flows, and a corresponding plurality of pairs of second heat transfer plates, in which a second fluid flows, are stacked one above the other. Technical background
[0002] Patent literature 1 describes a plate heat exchanger capable of improving long-term durability by preventing fluid leakage. This heat exchanger is manufactured at low cost with a simple structure while achieving good heat exchange efficiency. In the technique described in patent literature 1, multiple pairs of first heat transfer plates, through which a first fluid flows, and a corresponding multiple pairs of second heat transfer plates, through which a second fluid flows, are stacked one above the other. Therefore, leakage is unlikely for both the first fluid flowing in a pair of first heat transfer plates and the second fluid flowing in a pair of second heat transfer plates. Citation list of patent literature
[0003] Patent literature 1: International publication no. 2013 / 183629 Overview of the invention Technical problem
[0004] In recent years, there has been a global movement towards the use of refrigerants with low global warming potential (GWP). R32 and R290, which are low-GWP refrigerants, are flammable. Therefore, measures must be taken to prevent refrigerant leakage into interior spaces. Examples of such measures include the creation of structures to prevent the escape of a first or second fluid. In such a structure, as in the technique described in patent literature 1, two heat transfer plates—a first heat transfer plate and a second heat transfer plate—are positioned between the first and second fluids.
[0005] However, the formation of a crack, for example in a part that is prone to cracking, depends on many factors, such as manufacturing and environmental conditions. There is therefore a significant possibility that an area where a first and second heat transfer plate are in contact will crack. If such an area cracks, the fluids will mix, and flammable coolant can leak into the interior. Consequently, it is difficult to ensure that all products reliably prevent leakage over extended periods.
[0006] It follows that, regardless of error factors such as manufacturing conditions and environmental conditions, it is desirable that an area that can break is always an area where a first heat transfer plate and a second heat transfer plate are not in contact with each other.
[0007] The present disclosure was made to solve the above problem, and it is an objective of the present disclosure to provide a plate heat exchanger and a heat transfer device. In the plate heat exchanger, an area that can break, regardless of failure factors such as manufacturing conditions or environmental conditions, is always an area where a first heat transfer plate and a second heat transfer plate are not in contact with each other. Solution to the problem
[0008] A plate heat exchanger according to an embodiment of the present disclosure comprises: a plurality of first heat transfer plates, each having a planar heat transfer surface, wherein a first passage is formed in each pair of the plurality of first heat transfer plates; a plurality of first inner fins, each arranged in the corresponding first passage between a pair of the plurality of first heat transfer plates, the plurality of first inner fins each being formed by repeating a region with mutually opposed depressions and projections; a plurality of second heat transfer plates, each having a planar heat transfer surface, wherein a second passage is formed in each pair of the plurality of second heat transfer plates between corresponding two pairs of the plurality of first heat transfer plates; and a plurality of second inner fins,which are each arranged in the corresponding second passage between a pair of the plurality of second heat transfer plates, the plurality of second inner fins each being formed by repeating a region with spaced-apart depressions and projections. A space is formed between each of the plurality of first heat transfer plates and a corresponding plurality of second heat transfer plates. The plate heat exchanger comprises in the space a plurality of heat transfer components connecting each of the plurality of first heat transfer plates and a corresponding plurality of second heat transfer plates, the plurality of heat transfer components being distributed between each of the first heat transfer plates and a corresponding plurality of second heat transfer plates. The region with spaced-apart depressions and projections, extending in a direction transverse to the directionThe system, into which a first fluid flows through the first passage in each of the plurality of first inner fins, comprises first spacer regions and one or more second spacer regions, the width of each of the second spacer regions being greater than the width of each of the first spacer regions. The plurality of heat transfer components are arranged in regions of the first spacer sections when projected in the direction in which the plurality of first heat transfer plates and the plurality of second heat transfer plates are stacked.
[0009] A heat transfer device according to a further embodiment of the present disclosure comprises the plate heat exchanger. Advantageous effect of the invention
[0010] In the plate heat exchanger and heat transfer device according to the embodiments of the present disclosure, the section with spaced-apart recesses and projections, extending in the direction transverse to the direction in which the first fluid flows through the first passage in each of the plurality of first inner fins, comprises the first spacer sections and the one or more second spacer sections, the width of each of the second spacer sections being greater than the width of each of the first spacer sections. The plurality of heat transfer components are arranged in the regions of the first spacer sections when projected in the direction in which the plurality of first heat transfer plates and the plurality of second heat transfer plates are stacked.Thus, the first and second heat transfer plates are connected via the heat transfer components at the positions of the first spacer sections, which are strong and narrow. The wider section of the second spacer section, where the first and second heat transfer plates are not in contact, is designed to be weaker than the first spacer section and therefore prone to breakage. Regardless of factors such as manufacturing or environmental conditions, the area susceptible to breakage is always where the first and second heat transfer plates are not in contact. List of characters Fig. Figure 1 is a schematic configuration diagram showing a heat transfer device according to embodiment 1. Fig. Figure 2 is a perspective exploded view showing a plate heat exchanger according to embodiment 1. Fig. Figure 3 is a diagram showing the plate heat exchanger according to embodiment 1 in cross-section. Fig. Figure 4 is a partial perspective view showing the configuration between two first inner ribs according to embodiment 1. Fig. Figure 5 is a perspective view showing a first inner rib according to embodiment 1. Fig. Figure 6 is an enlarged view showing part of a first heat transfer plate according to embodiment 1. Fig. Figure 7 is an enlarged view showing part of a first heat transfer plate according to modification 1 of embodiment 1. Fig. Figure 8 is a diagram showing a cross-sectional view of a plate heat exchanger according to embodiment 2. Fig. Figure 9 is a diagram showing a cross-sectional view of a plate heat exchanger according to embodiment 3. Description of embodiments
[0011] The following descriptions illustrate embodiments with reference to the drawings. In the drawings, components with the same reference numerals are identical or corresponding components, and this applies throughout the entire description. In the cross-sectional views, hatching is omitted where necessary for easy identification. Furthermore, the shapes of components throughout the description are merely examples, and the shapes of the components are not limited to those described. Design 1<Konfiguration der Wärmeübertragungsvorrichtung 100>
[0012] Fig. Figure 1 is a schematic configuration diagram showing a heat transfer device 100 according to embodiment 1. As shown in Fig. As shown in Figure 1, the heat transfer device 100 comprises a coolant circuit 100, in which a heat transfer medium, which is a first fluid, is cooled or heated, and a heat transfer medium circuit 20, through which a heat transfer medium flows into a building. The coolant circuit 10 is mounted in an outdoor unit 11. A heat transfer medium circulates from the outdoor unit 11 through the heat transfer medium circuit 20 into a building 21. <Konfiguration der Außeneinheit 11 >
[0013] The outdoor unit 11 comprises a compressor 12, a four-way valve 13, a plate heat exchanger 30, an expansion valve 14, and an outdoor heat exchanger 15. Within the outdoor unit 11, the refrigerant circuit 10 is formed by connecting the compressor 12, the four-way valve 13, the plate heat exchanger 30, the expansion valve 14, and the outdoor heat exchanger 15 in that order via refrigerant lines 16 into a closed loop configuration. The outdoor unit 11 is a heat pump device. The refrigerant, which is a separate fluid, flows in the refrigerant circuit 10.
[0014] Compressor 12 compresses the refrigerant to a high-temperature, high-pressure coolant. Various types of compressors, such as scroll compressors or rotary compressors, can be used as compressor 12.
[0015] The four-way valve 13 switches the flow directions in the coolant circuit 10 between cooling and heating operation.
[0016] The plate heat exchanger 30 acts as either an evaporator or a condenser. The plate heat exchanger 30 has heat transfer passages 38, which serve as the primary passages through which a heat transfer medium flows, and coolant passages 39, which serve as the secondary passages through which the coolant flows. The plate heat exchanger 30 exchanges heat between a heat transfer medium flowing through the heat transfer passages 38 and a coolant flowing through the coolant passages 39. In cooling mode, the plate heat exchanger 30 exchanges heat between a heat transfer medium and a coolant that has been cooled by passing through the expansion valve 14. As a result, the heat transfer medium in the plate heat exchanger 30 is cooled. In heating mode, the plate heat exchanger 30 exchanges heat between a heat transfer medium and a coolant at a high temperature and high pressure, which has been compressed by the compressor 12.As a result, the heat transfer medium in the plate heat exchanger 30 is heated.
[0017] The expansion valve 14 acts as an expansion mechanism between the plate heat exchanger 30 and the external heat exchanger 15.
[0018] The external heat exchanger 15 acts as a condenser when the plate heat exchanger 30 acts as an evaporator. The external heat exchanger 15 is an air heat exchanger configured to exchange heat between the refrigerant and the outside air.
[0019] For example, a flammable refrigerant, such as R32 or R290, which is a refrigerant with a low GWP, can be used as the refrigerant that is the second fluid in the outdoor unit 11. <Konfiguration des Wärmemittelkreises 20>
[0020] The heat transfer fluid circuit 20 comprises the plate heat exchanger 30, a circulation pump 22, and a radiator 23. The heat transfer fluid circuit 20 is formed by connecting the plate heat exchanger 30, the circulation pump 22, and the radiator 23 to form a circuit via heat transfer fluid lines 24. The heat transfer fluid circuit 20 may include a storage tank (not shown) that stores a heat transfer fluid. The heat transfer fluid, which is the first fluid, is water or brine.
[0021] The circulation pump 22 provides an output pressure that directs the flow of the heat transfer fluid through the heat transfer fluid lines 24 in a specific direction. The circulation pump 22 is installed in an indoor unit 25 in building 21. The circulation pump 22 can also be installed in the outdoor unit 11.
[0022] The radiator 23 cools or heats the interior of the building 21 using cooling energy or heat from a heat transfer medium. For example, an air conditioning unit, separate from the radiator 23, can be located in the heat transfer medium circuit 20. Additionally, the heat transfer medium circuit 20 can be used as a hot water supply device configured to provide hot water using water as the heat transfer medium. <verschiedenes>
[0023] The heat transfer device 100 is suitable for many industrial or household appliances in which the plate heat exchanger 30 is installed. For example, the heat transfer device 100 can be used in an air conditioner, an electric generator, or a food sterilizer. <Konfiguration des Plattenwärmetauschers 30>
[0024] Fig. Figure 2 is a perspective exploded view showing the plate heat exchanger 30 according to embodiment 1. Fig. Figure 2 shows an upward direction U, a downward direction D, a rightward direction R, a leftward direction L, a forward direction F, and a backward direction B. As in Fig. As shown in Figure 2, the plate heat exchanger 30 comprises a pair of side plates 31, a plurality of first heat transfer plates 32, a plurality of first inner fins 33, a plurality of second heat transfer plates 34, and a plurality of second inner fins 35. A synthetic resin or metal, such as stainless steel, copper, aluminum, or titanium, can be used as the material for various components of the plate heat exchanger 30. The first heat transfer plates 32 or the second heat transfer plates 34 can be made of a coated material.
[0025] The two side plates 31 each have a planar shape and are arranged for reinforcement on the sides of structures formed by stacking the first heat transfer plates 32, the first inner ribs 33, the second heat transfer plates 34 and the second inner ribs 35 in a predetermined sequence.
[0026] Four through-holes, namely a heat medium inlet 31a, a heat medium outlet 31b, a coolant inlet 31c and a coolant outlet 31d, are arranged at the four corners of one of the two side plates 31. Fig. Figure 2 shows the heat transfer medium inlet 31a at the upper corner closer to one end in the left-right direction, the advertising medium outlet 31b at the lower corner closer to one end in the left-right direction, the coolant inlet 31c at the lower corner closer to the other end in the left-right direction, and the coolant outlet 31b at the upper corner closer to the other end in the left-right direction. Fig. 2 is the direction in which a heat transfer fluid flows, represented by the letter X on a solid arrow, and the direction in which the coolant flows is represented by a letter Y on a dashed arrow.
[0027] The first heat transfer plates 32 each have a flat heat transfer surface. The heat transfer medium passage 38, which serves as the first passage through which a heat transfer medium flows, is formed in each pair of the first heat transfer plates 32. A heat transfer medium flows downwards through the heat transfer medium passage 38 in the vertical direction, which extends in the upward direction U and the downward direction D. A heat transfer medium can flow through the heat transfer medium passage 38 such that, for example, the heat transfer medium passage 38 is inclined relative to the vertical direction to extend from the upper position in the left direction L, where the heat transfer medium inlet 31a is located, to the lower position in the right direction R, where the coolant inlet 31c is located.
[0028] The first inner ribs 33 are each arranged in the associated heat medium passage 38 between a pair of the first heat transfer plates 32 and are each formed by repeating a section 40 with spaced-apart depressions and projections.
[0029] The second heat transfer plates 34 each have a flat heat transfer surface. The coolant passage 39, which serves as the second passage through which coolant flows, is formed in each pair of second heat transfer plates 34 between the corresponding pairs of first heat transfer plates 32. Coolant flows upwards through the coolant passage 39 in the upward direction, extending in the upward direction U and the downward direction D. Coolant can flow through the coolant passage 39 such that, for example, the coolant passage 39 is inclined relative to the upward direction to extend from the lower position in the left direction L, where the heat transfer outlet 31b is located, to the upper position in the right direction R, where the coolant outlet 31d is located.
[0030] The second inner ribs 35 are each arranged in the corresponding coolant passage 39 between a pair of the second heat transfer plates 34 and are each formed by repeating a section 50 with spaced-apart recesses and projections.
[0031] The first heat transfer plates 32 and the second heat transfer plates 34 are formed such that they each have depressions and protrusions, for example by pressing plate-like components with a substantially uniform thickness.
[0032] The first heat transfer plates 32 and the second heat transfer plates 34 can have different thicknesses as required. Increasing the thickness helps prevent corrosion of the plate heat exchanger 30 and increases its strength. Conversely, reducing the thickness lowers thermal resistance and material costs without compromising heat exchange efficiency. Therefore, it is preferable to determine the thickness of the first heat transfer plates 32 and the second heat transfer plates 34 according to the desired specifications.
[0033] Through-holes, serving as passage holes, are formed at the four corners of the first heat transfer plates 32 and the second heat transfer plates 34. In particular, a heat medium outlet hole 32a, a heat medium return hole 32b, a coolant outlet hole 32c, and a coolant return hole 32d, which serve as passage holes, are arranged in the first heat transfer plate 32. Similarly, a heat medium outlet hole 34a, a heat medium return hole 34b, a coolant outlet hole 34c, and a coolant return hole 34d, which serve as passage holes, are arranged in the second heat transfer plate 34.
[0034] The first heat transfer plates 32 and the second heat transfer plates 34 each have a planar heat transfer surface that forms the corresponding heat transfer medium passage 38 or refrigerant passage 39. Projecting sections 36 and 37, which are relative to each other, are formed on the first heat transfer plates 32 and the second heat transfer plates 34. All projecting sections 36 and 37 extend forward in the direction F.
[0035] In the case of a pair of the first heat transfer plates 32 forming a heat medium passage 38 through which a heat medium flows and which is designated by the sign X, the projection sections 36 are arranged to each occupy places around the coolant outlet hole 32c and the coolant return hole 32d, and the projection sections 37 are arranged to each occupy places around the heat medium outlet hole 32a and the heat medium return hole 32b.
[0036] In the case of a pair of the second heat transfer plates 34 forming the coolant passage 39 through which the coolant, represented by the sign Y, flows, the projection sections 36 are arranged to each occupy places around the coolant outlet hole 34c and the coolant return hole 34d, and the projection sections 37 are arranged to each occupy places around the heat medium outlet hole 34a and the heat medium return hole 34b.
[0037] Each of the first inner ribs 33 is an offset rib for promoting heat transfer, arranged between the corresponding pair of first heat transfer plates 32. The first inner ribs 33 each have a plate-like shape, the portions of which are larger in the width and height directions than in the thickness direction. The first inner ribs 33 each have a structure formed by repeating section 40 with spaced-apart depressions and projections, where a thin component extends in the right-hand direction R and the left-hand direction L, i.e., in the width direction, to form substantially right angles (see Fig. 3, Fig. 4 and Fig. 5) An upper or lower region facing a pair of the first heat transfer plates 32 in section 40, which have spaced-apart recesses and projections, is designed as a flat surface. Thus, each of the first inner ribs 33 is in surface contact with the corresponding pair of the first heat transfer plates 32 on the flat surfaces of the upper or lower regions.
[0038] Each of the second ribs 35 is an offset rib for promoting heat transfer, arranged between the corresponding pair of second heat transfer plates 34. The second inner ribs 35 each have a substantially plate-like shape, the portions of which are larger in the width and height directions than one of their portions in the thickness direction. The second inner ribs 35 each have a structure formed by repeating section 50 with spaced-apart depressions and projections, in which a thin component extends in the right-hand direction R and the left-hand direction L, i.e., in the width direction, to form substantially right angles (see Fig. 3 and Fig. 4) An upper or lower area facing a pair of the second heat transfer plates 34 in section 50 with spaced-apart recesses and projections is designed as a flat surface. Thus, each of the second inner ribs 35 is in surface contact with the corresponding pair of the second heat transfer plates 34 on the flat surfaces of the upper or lower sections.
[0039] The first inner rib 33 and the second inner rib 35 have different heat transfer areas. In particular, section 40 with spaced-apart depressions and projections differs in size from section 50 with spaced-apart depressions and projections in the first inner rib 33 and the second inner rib 35 (see Fig. 3 and Fig. 4), which is described in detail below. Fig. Figure 2 shows the first inner rib 33 similar to the second inner rib 35, to simplify the figure.
[0040] A pair of the first heat transfer plates 32, between which the first inner rib 33 is arranged, is soldered to the first inner rib 33. A pair of the second heat transfer plates 34, between which the second inner rib 35 is arranged, is soldered to the second inner rib 35. The first heat transfer plate 32 and the second heat transfer plate 34, which faces the first heat transfer plate 32, are soldered together by solder sections 61, which serve as heat transfer components, at a plurality of parts, between which a space 60 is arranged (see Fig. 3) Thus, the first heat transfer plate 32 and the second heat transfer plate 34 form a double-walled structure in which the space 60 is arranged between the plumb sections 61, which serve as heat transfer components and improve heat transfer.
[0041] On one side plate 31, the first heat transfer plate 32, the first inner rib 33, the first heat transfer plate 32, the second heat transfer plate 34, the second inner rib 35 and the second heat transfer plate 34, which are stacking components, are stacked and arranged repeatedly in this order as required, and the other side plate 31 is finally stacked on top of this to form a stacked structure. <details des plattenwärmetauschers 30>
[0042] Fig. Figure 3 is a diagram showing the plate heat exchanger 30 according to embodiment 1 in cross-section. Fig. Figure 4 is a partially perspective view showing the configuration between two inner ribs 33 according to embodiment 1. Fig. Figure 5 is a perspective view showing the first inner rib 33 according to embodiment 1.
[0043] As in the Fig. 3, Fig. 4 and Fig. As shown in Figure 5, the first inner rib 33 comprises the section 40 with spaced-apart depressions and projections. In particular, the first inner rib 33 comprises a plurality of sections 40 with spaced-apart depressions and projections, each of which extends in a direction that crosses the vertical direction extending in the upward direction U and the downward direction D, which is the direction in which a heat medium flows through the heat medium passage 38 in each of the first ribs 33, such that the sections 40 with spaced-apart depressions and projections are arranged in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.Here, the sections 40 with spaced-apart depressions and projections are arranged in the width direction, which extends in the right direction R and the left direction L, which is a direction orthogonal to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0044] Here, section 40 with spaced-apart depressions and projections has through-holes in the direction in which a heat medium flows through the heat medium passage 38 in each of the inner ribs 33, and section 40 with spaced-apart depressions and projections has a shape in which a depression and a projection are repeated in the direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33. The plate surfaces in section 40 with spaced-apart depressions and projections extend in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33, and section 40 with spaced-apart depressions and projections does not prevent a heat medium from flowing through the heat medium passage 38.
[0045] Some of the sections 40 with spaced-apart depressions and projections extending in the direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33 comprise first spaced sections 40a and second spaced sections 40b, the width of which is greater than that of the first spaced section 40a. Some of the sections 40 with spaced-apart depressions and projections extending in the direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33 comprise only the first spaced sections 40a.
[0046] The sections 40 with spaced-apart depressions and projections of the first inner rib 33 each extend at right angles, orthogonally or parallel to the direction perpendicular to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0047] An orthogonal section 41 of the section 40 with spaced-apart depressions and projections of the first inner rib 33, extending such that it connects a pair of the first heat transfer plates 32, is arranged between the orthogonal sections 41 and offset relative to them, which are adjacent to each other, under the adjacent sections 40 with spaced-apart depressions and projections in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33 (see Fig. 3).
[0048] In particular, the orthogonal area 41 of the section 40 with spaced-apart depressions and projections of the first inner rib 33, which extends in such a way as to connect a pair of the first heat transfer plates 32, is preferably arranged in the middle between the orthogonal areas 41 and offset from these, which are adjacent to each other, and is located under the adjacent sections 40 with spaced-apart depressions and projections in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0049] One or more second spacer sections 40b are arranged in each of the sections 40 with spaced-apart recesses and projections, wherein at least one of the first spacer sections 40a is arranged between them in the direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33. In particular, as shown in the Fig. 4 and Fig. As shown in Figure 5 below, two second spacer sections 40b are arranged in section 40 with adjacent recesses and projections, with nine first spacer sections 40a arranged between them in a direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33. In regions other than the bottommost regions, a second spacer section 40b is arranged in section 40 with spaced-apart recesses and projections in a direction transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0050] As in the Fig. 4 and Fig. As shown in Figure 5, the second spacer section 40b is arranged in the direction perpendicular to the direction in which a heat medium flows through the heat medium passage 38, offset from the second spacer section 40b of the section 40 with spaced-apart depressions and projections, which differs in position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0051] The section 40 with spaced-apart depressions and projections, which includes only the first spaced sections 40a, is arranged between the section 40 with spaced-apart depressions and projections, which includes the second spaced section 40b at a position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33, and the section 40 with spaced-apart depressions and projections, which includes the second spaced section 40b, which differs with respect to its position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0052] As in the Fig. 3 and Fig. As shown in Figure 4, the section 40 with spaced-apart depressions and projections, which includes the second spaced section 40b at a position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33, faces the section 40 with spaced-apart depressions and projections, which includes only the first spaced section 40a of the first inner rib 33 between a pair of the first heat transfer plates 32, which are arranged next to the adjacent pair of the second heat transfer plates 34 in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0053] As in the Fig. 4 and Fig. As shown in Figure 5, the same sides of the second spacer sections 40b, which are arranged in the first inner rib 33, are open in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0054] As in the Fig. 3, Fig. 4 and Fig. As shown in Figure 5, the value calculated by dividing the width of the first spacing section 40a by the width of the second spacing section 40b is less than 1. Preferably, the value calculated by dividing the width of the first spacing section 40a by the width of the second spacing section 40b is less than 1 and greater than 0.5. <details der lotabschnitte 61>
[0055] As in Fig. As shown in Figure 3, the space 60 is formed between the first heat transfer plate 32 and the second heat transfer plate 34. The plumb sections 61, which serve as heat transfer components connecting the first heat transfer plate 32 and the second heat transfer plate 34, between which the heat transfer components are arranged, are located in the space 60.
[0056] Any solder material can be used for the solder sections 61, provided the material has better heat transfer properties than air. Examples include metallic solder such as copper solder, silver solder, or phosphorus-deoxidized copper. Instead of the solder sections 61, metallic heat transfer components can be arranged, for example, by bonding or other methods. A highly adhesive liquid or solid material, such as grease, can also be used as a heat transfer component. Furthermore, the first heat transfer plate 32 and the second heat transfer plate 34 can be directly connected to each other without an additional component being arranged between them, for example, by spot welding or pressure joining. However, if the first heat transfer plate 32 and the second heat transfer plate 34 are directly connected to each other, the space 60 must be arranged between them.
[0057] The solder sections 61, which serve as heat transfer components, are arranged in the regions of the first spacer sections 40a when the solder sections 61 project in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. In other words, the solder sections 61, which serve as heat transfer components, do not exist in the regions of the second spacer sections 40b, where the solder sections 61 project in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. <Wirkung der Lotabschnitte 61 zwischen der erstenWärmeübertragungsplatte 32 und der zweiten Wärmeübertragungsplatte 34>
[0058] The solder sections 61, with which the first heat transfer plate 32 and the second heat transfer plate 34 are soldered together, have a high thermal conductivity and cause the thermal contact resistance between the first heat transfer plate 32 and the second heat transfer plate 34 to be reduced, thus further preventing a reduction in heat transfer.
[0059] On the other hand, the space 60, in which the first heat transfer plate 32 and the second heat transfer plate 34 are not soldered together, is open to the air. If the first heat transfer plate 32 breaks, a heat transfer medium is thus released into the air. If the position of the second spacer section 40b is projected in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked, the space 60 is always formed at the position of the second spacer section 40b between the second heat transfer plate 34 and the first heat transfer plate 32, which is adjacent to another first heat transfer plate 32. The width of the second spacer section 40b of the first inner fin 33 is greater than the width of the first spacer section 40a.If, for example, the heat transfer medium is water and a higher than usual pressure is generated due to frost in the heat transfer medium passage 38, an increase in internal pressure, or other reasons, the stress generated at the position of the second spacer section 40b is greater than the stress generated in the surrounding area. Accordingly, it is possible to always position the portion of the second heat transfer plate 32 that is intended to rupture at the position of the second spacer section 40b. The second spacer sections 40b are arranged such that they cover areas where the pressure increase is generated. Thus, it can be expected that a portion of the first heat transfer plate 32 will rupture and release heat transfer medium to the outside.Accordingly, it is possible to prevent escaping coolant from flowing into building 21 through the heat transfer circuit 20 and due to the break in the part where the first heat transfer plate 32 and the second heat transfer plate 34 are connected. <details des abschnitts 50 mit voneinander beabstandeten vertiefungen und vorsprüngen der zweiten innenrippe 35>
[0060] As in the Fig. 3 and Fig. As shown in Figure 4, section 50 with spaced-apart depressions and projections of the second inner rib 35 is formed by repeating a depression and a projection at a specific distance. A specific second spaced section 40b, as in section 40 with spaced-apart depressions and projections of the first inner rib 33, is not arranged in section 50 with spaced-apart depressions and projections of the second inner rib 35.
[0061] Section 50, with spaced-apart depressions and projections of the second inner rib 35, includes a depression and a projection that are smaller than those of section 40, with spaced-apart depressions and projections of the first inner rib 33. Here, the flat heat transfer surfaces of the first heat transfer plates 32 coincide with and are connected to the first inner rib 33, and the flat heat transfer surfaces of the second heat transfer plates 34 coincide with and are connected to the second inner rib 35.If the heat transfer medium is a high-pressure fluid and the coolant is a low-pressure fluid, the first inner rib 33, in which the recesses and projections are large and whose contact area with the first heat transfer plates 32 is large, is used for the heat transfer medium passage 38 through which the heat transfer medium flows, and the second inner rib 35, in which the recesses and projections are small and whose contact area with the second heat transfer plates 34 is small, is used as the coolant passage 39 through which the coolant flows. This ensures that each part has and maintains the necessary and sufficient strength overall.
[0062] As previously described, a fin with a small spacing, which provides good heat transfer, is used on the coolant side, which is particularly affected by pressure drop. A fin with a large spacing, which provides poor heat transfer and where the pressure drop is small, is used on the heat transfer fluid side. As a result, it is possible to balance the thermal resistance of the coolant and the water. In this way, it is possible to adjust the thermal resistance of the heat transfer fluid (the first fluid) and the coolant (the second fluid) according to the properties of the flowing fluid, leading to improved heat exchange. <weiteres>
[0063] Fig. Figure 6 is an enlarged view showing part of the first heat transfer plate 32 according to embodiment 1. As in Fig. As shown in Figure 6, the first heat transfer plate 32 and the second heat transfer plate 34 each have a shape that covers the entire area including the area where the through holes are located. <Abwandlung 1>
[0064] Fig. Figure 7 is an enlarged view showing part of a first heat transfer plate 32 according to modification 1 of embodiment 1. As in Fig. As shown in Figure 7, the first heat transfer plate 32 or the second heat transfer plate 34 can have a shape that excludes the area where a through-hole is present and covers only the area where a heat transfer medium and a coolant are adjacent. For example, the first heat transfer plate 32 or the second heat transfer plate 34 can have a shape in which the protruding area 37, which is an area around the heat transfer medium outlet hole 32a, is truncated in the first heat transfer plate 32. This allows the amount of material for the first heat transfer plate 32 and the second heat transfer plate 34 to be reduced, thus enabling the plate heat exchanger 30 to be manufactured at a low cost. <betrieb>
[0065] As previously described, the plate heat exchanger 30 is able to improve the long-term reliability of the heat transfer device 100 by preventing coolant from penetrating the housing 21 through the heat transfer medium circuit 20. Furthermore, the plate heat exchanger 30 can be manufactured cost-effectively with a simple structure, while maintaining the same thermal resistance between the heat transfer medium and the coolant, thus ensuring good heat exchange. This makes it possible, for example, to use natural coolants such as CO2, flammable hydrocarbons, or coolants with a low global warming potential (GWP), which were previously unusable due to the lack of a way to prevent coolant ingress.Furthermore, a fluid to be used is selected from an expanded range of fluids, making it possible to choose a coolant that has a high latent heat capacity and improves heat transfer. <Wirkungen der Ausführungsform 1>
[0066] According to embodiment 1, the plate heat exchanger 30 comprises the first heat transfer plates 32, each having a flat heat transfer surface, wherein the heat medium passage 38, serving as the first passage, is formed in each pair of the first heat transfer plates 32. The plate heat exchanger 30 comprises the first internal fins 33, each arranged in the corresponding heat medium passage 38 between a pair of the first heat transfer plates 32, and each formed by repeating section 40 with spaced-apart recesses and projections. The plate heat exchanger 30 comprises the second heat transfer plates 34, each having a flat heat transfer surface, wherein the coolant passage 39, serving as the second passage, is formed in each pair of the second heat transfer plates 34 between the corresponding two pairs of the first heat transfer plates 32.The plate heat exchanger 30 comprises the second inner fins 35, each arranged in the corresponding coolant passage 39 between a pair of the second heat transfer plates 34, and each formed by repeating the section 50 with spaced-apart recesses and projections. The space 60 is formed between each of the first heat transfer plates 32 and a corresponding second heat transfer plate 34. Within the space 60, the plate heat exchanger 30 includes the solder sections 61, which serve as the heat transfer components connecting each of the first heat transfer plates 32 and a corresponding second heat transfer plate 34, with the heat transfer components being distributed between each of the first heat transfer plates 32 and a corresponding second heat transfer plate 34.The section 40, with spaced-apart depressions and projections, extending in the direction transverse to the direction in which a heat transfer medium, serving as the first fluid, flows through the heat transfer medium passage 38 in each of the first inner fins 33, comprises the first spaced sections 40a and one or more of the second spaced sections 40b, the width of each of the second spaced sections 40b being greater than the width of each of the first spaced sections 40a. The perpendicular sections 61 are arranged in the regions of the first spaced sections 40a when the perpendicular sections 61 are projected in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0067] In this configuration, the first heat transfer plate 32 and the second heat transfer plate 34 are connected at the positions of the first spacer sections 40a, which are strong and each have a small width, via the perpendicular sections 61 in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. Therefore, the space 60 adjacent to the first heat transfer plate 32 is located at the position of the second spacer section 40b, which has a large width. Here, the first heat transfer plate 32 and the second heat transfer plate 34 are not in contact with each other in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. The area of the second spacer section 40b is configured to always be weaker than that of the first spacer section 40a and is prone to breakage.Thus, regardless of error factors such as manufacturing or environmental conditions, the area that can break is always an area where the first heat transfer plate 32 and the second heat transfer plate 34 are not in contact with each other. As a result, the plate heat exchanger 30 is able to improve safety by, for example, completely preventing a flammable coolant from flowing through the heat transfer circuit 20 into the building 21 without mixing the heat transfer medium and the coolant, and can be manufactured at low cost with a simple structure and good heat exchange properties.
[0068] According to embodiment 1, there are no plumb sections 61 in the areas of the one or more second spacer sections 40b when the plumb sections 61 are projected in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0069] In this configuration, the width of the second spacer section 40b is greater than the width of the first spacer section 40a, and the space 60, in which the perpendicular sections 61 are not arranged between the first heat transfer plate 32 and the second heat transfer plate 34, can be formed adjacent to the first heat transfer plate 32. The area of the second spacer section 40b can thus be designed such that it is always weaker than that of the first spacer section 40a and can break.
[0070] According to embodiment 1, the one or more second spacer sections 40b are arranged in the area 40 with spaced-apart recesses and projections, wherein at least one of the first spacer sections 40a is arranged between the one or more second spacer sections 40b in the direction that is transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0071] In this configuration, the areas of the second spacer sections 40b, which are always weaker than those of the first spacer sections 40a and which can break, are arranged in each of the first inner fins 33 of the plate heat exchanger 30 such that the second spacer sections 40b cover areas where a pressure increase is generated.
[0072] According to embodiment 1, one or more second spacer sections 40b are displaced in the direction that lies transversely to the direction in which a heat medium flows through the heat medium passage 38, namely from the second spacer section 40b of the section 40 with spaced-apart recesses and projections which differs in position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0073] In this configuration, the second spacing sections 40b, which are continuously adjacent to each other in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner fins 33, are not formed. This allows the areas of the second spacing sections 40b to be not excessively weak.
[0074] According to embodiment 1, the section 40 with spaced-apart depressions and projections, which comprises only the first spaced sections 40a, is arranged between the section 40 with spaced-apart depressions and projections, which comprises one or more second spaced sections 40b at a position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33, and the section 40 with spaced-apart depressions and projections comprises one or more second spaced sections 40b, which are different with respect to the position in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0075] In this configuration, the second spacing sections 40b, which are continuously adjacent to each other in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner fins 33, are not formed. This allows the areas of the second spacing sections 40b to be not excessively weak.
[0076] According to embodiment 1, the section 40 with spaced-apart recesses and projections, which includes the one or more spaced sections 40b at a position in the direction in which a heat medium flows through the heat medium passage 38 into each of the first inner ribs 33, faces the section 40 with spaced-apart recesses and projections, which includes only the first spaced sections 40a from one of the first inner ribs 33 between a pair of the first heat transfer plates 32 near the adjacent pair of the second heat transfer plates 34 in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0077] In this configuration, the adjacent second spacer sections 40b, which overlap when projected in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked, are not formed. This allows the areas of the second spacer sections 40b to be not excessively weak.
[0078] According to embodiment 1, equal sides of the second spacer sections 40b, which are arranged in each of the first inner ribs 33, are open in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0079] In this configuration, the first inner fins 33 each encompass the second spacer sections 40b, the same sides of which are open in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. Thus, the areas of the second spacer sections 40b that are always weaker and prone to breakage are positioned in the plate heat exchanger 30 such that the same sides are open in the direction in which the first inner fins 33 are stacked. Accordingly, it is easy to adjust the fracture resistance of the first heat transfer plates 32 at the positions of the second spacer sections 40b. Furthermore, it is easy to manufacture the first inner fins 33.
[0080] According to embodiment 1, the value calculated by dividing the width of each first spacing section 40a by the width of each of the second spacing sections 40b is less than 1.
[0081] With this configuration, it is easy to adjust the breaking strength of the first heat transfer plates 32 at the positions of the second spacer sections 40b.
[0082] According to embodiment 1, the value calculated by dividing the width of each of the first spacing sections 40a by the width of each of the second spacing sections 40b is greater than 0.5.
[0083] In this configuration, the second spacer section 40b has a certain degree of strength without being excessively weak, and it is easy to adjust the breaking ability of the first heat transfer plates 32 at the positions of the second spacer sections 40b.
[0084] According to embodiment 1, the section 40 extends with spaced-apart recesses and projections of each of the first inner ribs 33 bent at right angles and orthogonal or parallel to the direction that is transverse to the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0085] With this configuration, it is easy to form and manufacture the first inner ribs 33.
[0086] According to embodiment 1, the orthogonal area 41 of the section 40 with spaced-apart depressions and projections of each of the first inner ribs 33, which connects a pair of the first heat transfer plates 32, is arranged between the orthogonal areas 41 and offset from these, which are arranged adjacent to each other, and adjacent to the section 40 with spaced-apart depressions and projections in the direction in which the heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0087] In this configuration, two orthogonal regions 41 are arranged non-continuously adjacent to each other in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner fins 33. Furthermore, the heat medium, which has a low heat exchange rate and flows between adjacent orthogonal regions 41 located immediately upstream of each orthogonal region 41, can be subjected to heat exchange through the orthogonal region 41, leading to an increase in heat exchange.
[0088] According to embodiment 1, the orthogonal area 41 of the section 40, with spaced-apart recesses and projections of each of the first inner ribs 33, which connects a pair of the first heat transfer plates 32, is arranged in the middle between the orthogonal areas 41 and offset from these adjacent orthogonal areas 41 in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner ribs 33.
[0089] In this configuration, two orthogonal regions 41 are not continuously adjacent to each other in the direction in which a heat medium flows through the heat medium passage 38 in each of the first inner fins 33. Furthermore, the heat medium with the lowest heat exchange rate, which flows through the midpoint between the adjacent orthogonal regions 41 immediately upstream of each orthogonal region 41, can undergo heat exchange through the orthogonal region 41, leading to a further increase in heat exchange capacity.
[0090] According to embodiment 1, the heat transfer medium serving as the first fluid is water or brine.
[0091] In this configuration, for example, a frozen heat transfer medium causes a volume expansion or a pressure increase, and the first heat transfer plate 32 can break. The area of the second spacer section 40b is therefore configured to always be weaker than the area of the first spacer section 40a, which is why it can always break. If the first heat transfer plate 32 breaks at the position of the second spacer section 40b, the heat transfer medium can thus be released into space 60.
[0092] According to embodiment 1, a second fluid flowing through the coolant passage 39 is a coolant.
[0093] If, in this configuration, the first heat transfer plate 32 breaks at the position of the second spacer section 40b, the heat transfer medium can be released into room 60. Even if the coolant is a flammable coolant, and the first heat transfer plate 32 breaks at the position of the second spacer section 40b, it is therefore possible to increase safety by completely preventing the coolant, such as a flammable coolant, from flowing through the heat transfer circuit 20 into building 21 without the heat transfer medium and the coolant mixing.
[0094] According to embodiment 1, section 50 with spaced-apart depressions and projections of each of the second inner ribs 35 comprises a depression and a projection that are smaller than a depression and a projection of section 40 with spaced-apart depressions and projections of each of the first inner ribs 33.
[0095] With this configuration, section 40 with spaced-apart depressions and projections and section 50 with spaced-apart depressions and projections can be optimally formed in accordance with the respective properties, such as the viscosity of a heat transfer medium and a coolant.
[0096] According to embodiment 1, the heat transfer device 100 comprises the plate heat exchanger 30.
[0097] Since the heat transfer device 100 includes the plate heat exchanger 30, in this configuration, regardless of fault factors such as manufacturing conditions or environmental conditions, any area that breaks will always be an area where the first heat transfer plate 32 and the second heat transfer plate 34 are not in contact with each other. Design 2
[0098] Fig. Figure 8 is a diagram showing a cross-sectional view of a plate heat exchanger 30 according to embodiment 2. In embodiment 2, aspects similar to those of the previously described embodiment 1 are not described, and only the features are described.
[0099] As in Fig. As shown in Figure 8, section 40, with spaced-apart recesses and projections in each of the first inner ribs 33 between the first spaced section 40a and the second spaced section 40b, comprises third spaced sections 40c, the width of which is smaller than that of the first spaced section 40a. Four third spaced sections 40c are arranged on each of the two sides of the second spaced section 40b. < Effects of embodiment 2>
[0100] According to embodiment 2, the section 40 with spaced-apart recesses and projections of each of the first inner ribs 33 between each of the first spacer sections 40a and a corresponding one of the second spacer sections 40b comprises the third spacer section 40c, the width of which is narrower than the width of each of the first spacer sections 40a.
[0101] In this configuration, the third spacer sections 40c, which are strong and each have a small width, are arranged on both sides of the second spacer section 40b. This allows the reinforcement of both sides of the second spacer section 40b, and thus ensures that both sides of the second spacer section 40b are not excessively weak. embodiment 3
[0102] Fig. Figure 9 is a diagram showing a cross-sectional view of a plate heat exchanger 30 according to embodiment 3. In embodiment 3, aspects similar to those of the previously described embodiments 1 and 2 are not described; only the features are described.
[0103] As in Fig. As shown in Figure 9, the second spacer section 40b is located opposite the second spacer section 40b of the first inner rib 33 between a pair of the first heat transfer plates 32, and is close to the adjacent pair of the second heat transfer plates 34 in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. The respective openings of the second spacer sections 40b are opposite each other.
[0104] The section 40 with spaced-apart depressions and projections is arranged such that the section 40 with spaced-apart depressions and projections and another section 40 with spaced-apart depressions and projections of the first inner rib 33 in a pair of the first heat transfer plates 32 on the opposite side of the adjacent pair of the second heat transfer plates 34 are symmetrical in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. <Wirkungen der Ausführungsform 3>
[0105] According to embodiment 3, each of the second spacer sections 40b is opposite a corresponding second spacer section 40b of one of the first inner ribs 33, between a pair of the first heat transfer plates 32 near the adjacent pair of the second heat transfer plates 34 in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0106] In this configuration, the second spacer section 40b faces the adjacent second spacer section 40b, with a pair of the second heat transfer plates 34 positioned between them. This reduces the number of components located between the second spacer section 40b and the adjacent second spacer section 40b in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. Therefore, the area of the second spacer section 40b can be configured to be consistently weaker than that of the first spacer section 40a, allowing it to break.
[0107] According to embodiment 3, the section 40 with spaced-apart recesses and projections is arranged such that the section 40 with spaced-apart recesses and projections and another section 40 with spaced-apart recesses and projections of one of the first inner ribs 33 in a pair of the first heat transfer plates 32 on the opposite side of the adjacent pair of the second heat transfer plates 34 are symmetrical in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked.
[0108] In this configuration, the second spacer section 40b always faces the adjacent second spacer section 40b, with a pair of the second heat transfer plates 34 positioned between them. This allows for a reduction in the number of components arranged between the second spacer section 40b and the adjacent second spacer section 40b in the direction in which the first heat transfer plates 32 and the second heat transfer plates 34 are stacked. Thus, the area of the second spacer section 40b can always be configured to be weaker than that of the first spacer section 40a in order to be able to break. Reference symbol list 10 Coolant circuit, 11 Outdoor unit, 12 Compressor, 13 Four-way valve, 14 Expansion valve, 15 external heat exchangers, 16 Coolant line, 20 Heat transfer fluid circuit, 21 buildings, 22 Circulation pump, 23 Radiator, 24 Heat transfer fluid line, 25 indoor units, 30 plate heat exchangers, 31 Side panel, 31a Heat medium inlet, 31b Heat medium outlet, 31c Coolant inlet, 31d Coolant outlet, 32 first heat transfer plate, 32a Heat medium outlet hole, 32b Heat exchanger return hole, 32c Coolant outlet hole, 32d Coolant return hole, 33 first inner rib, 34 second heat transfer plate, 34a Heat medium outlet hole, 34b Heat exchanger return hole, 34c Coolant outlet hole, 34d Coolant return hole, 35 second inner rib, 36th lead section, 37th lead section, 38 Heat transfer medium passage, 39 Coolant passage, 40 sections with spaced-apart depressions and projections, 40a first spacing section, 40b second spacing section, 40c third spacing section, 41 orthogonal area, 50 sections with spaced-apart depressions and projections, 60 room, 61. Plumb line section, 100 Heat transfer device< / betrieb> < / weiteres> < / details> < / details> < / details> < / verschiedenes>
Claims
[1] Plate heat exchangers comprising: a plurality of first heat transfer plates, each having a planar heat transfer surface, wherein a first passage is formed between each pair of the plurality of first heat transfer plates; a plurality of first inner ribs, each arranged in the corresponding first passage between a pair of the plurality of first heat transfer plates, the plurality of first inner ribs being formed by repeating a section with spaced-apart depressions and projections; a plurality of second heat transfer plates, each having a planar heat transfer surface, wherein in each pair of the plurality of second heat transfer plates a second passage is formed between corresponding two pairs of the plurality of first heat transfer plates; and a plurality of second inner ribs, each arranged in the corresponding second passage between a pair of the plurality of second heat transfer plates, wherein the plurality of second inner ribs is formed by repeating a section with spaced-apart depressions and projections, wherein a space is formed between each of the plurality of first heat transfer plates and a corresponding plurality of second heat transfer plates, wherein the plate heat exchanger in the space comprises a plurality of heat transfer components connecting each of the plurality of first heat transfer plates and a corresponding plurality of second heat transfer plates, wherein the plurality of heat transfer components is distributed between each of the plurality of first heat transfer plates and a corresponding plurality of second heat transfer plates, wherein the section with spaced-apart depressions and projections, extending in a direction transverse to a direction in which a first fluid flows through the first passage in each of the plurality of first inner ribs, comprises first spaced sections and one or more second spaced sections, wherein a width of each of the second spaced sections is greater than a width of each of the first spaced sections, and wherein the majority of heat transfer components are arranged in areas of the first spacer sections, when the majority of heat transfer components are projected in a direction in which the majority of first heat transfer plates and the majority of second heat transfer plates are stacked. [2] Plate heat exchanger according to claim 1, wherein the plurality of heat transfer components does not exist in areas of the one or more second spacer sections when the plurality of heat transfer components is projected in the direction in which the plurality of the first heat transfer plates and the plurality of the second heat transfer plates are stacked. [3] Plate heat exchanger according to claim 1 or 2, wherein the one or more second spacer sections are arranged in the section with spaced-apart recesses and projections, wherein at least one of the first spacer sections is arranged between the one or more second spacer sections in the direction that is transverse to the direction in which the first fluid flows through the first passage in each of the plurality of first inner ribs. [4] Plate heat exchanger according to one of claims 1 to 3, wherein one or more second spacer sections are arranged offset in the direction transverse to the direction in which the first fluid flows through the first passage, from a further second spacer section of the section having spaced-apart recesses and projections, which differs in position in the direction in which the first fluid flows through the first passage in each of the plurality of first inner ribs. [5] Plate heat exchanger according to one of claims 1 to 4, wherein the section with spaced-apart depressions and projections, comprising only the first spacer sections, is arranged between the section with spaced-apart depressions and projections, comprising one or more second spacer sections at a position in the direction in which the first fluid flows through the first passage in each of the plurality of the first inner ribs, and the section with spaced-apart depressions and projections, comprising one or more of the second spacer sections, which are different from each other with respect to their position in the direction in which the first fluid flows through the first passage in each of the plurality of the first inner ribs. [6] Plate heat exchanger according to claim 5, wherein the section with spaced-apart depressions and projections, which includes one or more of the second spacer sections at a position in the direction in which the first fluid flows through the first passage in each of the plurality of first inner fins, faces the section with spaced-apart depressions and projections, which includes only the first spacer sections of the one or more first inner fins between a pair of the plurality of first heat transfer plates, which are near an adjacent pair of the plurality of second heat transfer plates in the direction in which the plurality of first heat transfer plates and the plurality of second heat transfer plates are stacked. [7] Plate heat exchanger according to any one of claims 1 to 6, wherein the section with spaced-apart recesses and projections of each of the plurality of first inner ribs between each of the first spaced sections and a corresponding one of the second spaced sections comprises a third spaced section whose width is narrower than the width of each of the first spaced sections. [8] Plate heat exchanger according to any one of claims 1 to 7, wherein equal sides of the second spacer sections arranged in each of the plurality of first inner fins are open in the direction in which the plurality of the first heat transfer plates and the plurality of the second heat transfer plates are stacked. [9] Plate heat exchanger according to any one of claims 1 to 8, wherein a value calculated by dividing the width of each of the first spacer sections by the width of each of the second spacer sections is less than 1. [10] Plate heat exchanger according to claim 9, wherein the value calculated by dividing the width of each of the first spacer sections by the width of each of the second spacer sections is greater than 0.
5. [11] Plate heat exchanger according to any one of claims 1 to 10, wherein each of the second spacer sections faces a corresponding second spacer section of one or more of the first inner fins, between a pair of the plurality of first heat transfer plates near an adjacent pair of the plurality of second heat transfer plates in the direction in which the plurality of first heat transfer plates and the plurality of second heat transfer plates are stacked. [12] Plate heat exchanger according to claim 11, wherein the section with offset depressions and projections is arranged such that the section with offset depressions and projections and a further section with offset depressions and projections of one of the plurality of first inner fins in a pair of the plurality of first heat transfer plates on an opposite side of an adjacent pair of the plurality of second heat transfer plates are symmetrical in the direction in which the plurality of first heat transfer plates and the plurality of second heat transfer plates are stacked. [13] Plate heat exchanger according to any one of claims 1 to 12, wherein the section with spaced-apart depressions and projections of each of the plurality of first inner ribs extends at right angles orthogonally or parallel to the direction which is transverse to the direction in which the first fluid flows through the first passage in each of the plurality of first inner ribs. [14] Plate heat exchanger according to any one of claims 1 to 13, wherein an orthogonal region of the section with spaced-apart depressions and projections of each of the plurality of first inner fins, wherein the orthogonal region connects a pair of the plurality of first heat transfer plates in the pair of the plurality of first heat transfer plates, is arranged between and offset from the adjacent orthogonal regions of an adjacent section with spaced-apart depressions and projections in the direction in which the first fluid flows through the first passage in each of the plurality of first inner fins. [15] Plate heat exchanger according to claim 14, wherein the orthogonal region of the section with spaced-apart depressions and projections of each of the plurality of first inner fins, wherein the orthogonal region connects the pair of the plurality of first heat transfer plates in the pair of the plurality of first heat transfer plates, is arranged at a midpoint between and offset from each other adjacent orthogonal regions of the section with spaced-apart depressions and projections in the direction in which the first fluid flows through the first passage in each of the plurality of first inner fins. [16] Plate heat exchanger according to any one of claims 1 to 15, wherein the first fluid is water or brine. [17] Plate heat exchanger according to any one of claims 1 to 16, wherein the second fluid flowing through the second passage is a coolant. [18] Plate heat exchanger according to any one of claims 1 to 17, wherein the section with spaced-apart depressions and projections of each of the plurality of second inner ribs comprises a depression and a projection which are smaller than a depression and a projection of the section with spaced-apart depressions and projections of each of the plurality of first inner ribs. [19] Heat transfer device comprising the plate heat exchanger according to any one of claims 1 to 18.