JP2013155983A - Plate-type heat exchanger and water heating system including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a plate-type heat exchanger that can reduce pressure loss by a simple means in comparison with a conventional one.SOLUTION: In a plate-type heat exchanger HE in which a flat flow channel 6A for circulating a fluid as a heat-exchanged object, is formed at least between a pair of heat transfer plates 3A, 3B, inflow opening parts 31a are respectively formed at one end side of the pair of heat transfer plates 3A, 3B, outflow opening parts 32a for a fluid passing through the flow channel 6A from the inflow opening part 31a side, are formed at the other end side, and the outflow opening parts 32a are opened toward the stacking direction of the pair of heat transfer plates 3A, 3B, a flow control part 7 that can suppress the fluid reaching a region 60 to pass through the region 60 and further move a downstream side, is disposed at a downstream side in the fluid flowing direction of the region 60 opposed to the outflow opening parts 32a, of the flow channel 6A.

Description

  The present invention has a configuration in which a flow path of a fluid to be heat exchanged is formed using a plurality of heat transfer plates, for example, a plate heat exchanger used for an application such as generating hot water used for hot water supply, and The present invention relates to a hot water apparatus such as a hot water supply apparatus provided with this.

  In the plate heat exchanger, a plurality of heat transfer plates are stacked in the thickness direction, and a flat flow path through which a heat exchange target fluid flows is formed between a pair of adjacent heat transfer plates. In such a heat exchanger, the fluid inflow opening is provided at one end of the pair of heat transfer plates, and the fluid outflow opening that has traveled through the flow path is provided at the other end. However, these fluid inflow and outflow openings are usually provided so as to open in the direction in which the pair of heat transfer plates are stacked (see, for example, Patent Documents 1 to 3). ). If the fluid inflow and outflow openings are provided in such a direction, the fluid inflow and outflow openings are provided when a plurality of channels are provided by stacking a plurality of pairs of heat transfer plates. There is an advantage that the plurality of stages of channels can be easily communicated with each other by facing each other.

  However, in the past, there was room for improvement as described below.

  Plate heat exchangers, like other types of heat exchangers, are desired to have a low pressure loss. Such a demand is particularly great when the plate heat exchanger is used for heating hot water such as floor heating. Since the hot water circuit for heating is considerably long and the pressure loss of the hot water circuit itself is large, in addition to this, if the pressure loss of the plate heat exchanger is also large, the heating pump This is because the load becomes considerably large and causes many disadvantages such as an increase in power consumption.

On the other hand, in the conventional plate type heat exchanger, the following phenomenon has occurred. That is, the flow path formed by the pair of heat transfer plates is flat, and the direction in which the fluid flows through the flow paths is the surface direction of each heat transfer plate. This direction is orthogonal to the direction of the fluid outflow opening (the direction in which the fluid flows out of the flow path). For this reason, even if the fluid flowing through the flow path reaches the facing region of the fluid outflow opening, most of the fluid passes through the facing region of the opening and flows further downstream. Such a flow becomes a factor causing a vortex in a region downstream of the facing region of the opening. In addition, such a vortex affects the facing area of the fluid outlet opening, and causes a large resistance when the fluid passes through the opening.
Such a phenomenon is one factor that increases the pressure loss of the plate heat exchanger. Therefore, it is desirable to appropriately eliminate such a situation.

  In addition, although patent document 3 describes performing a burring process to a heat-transfer plate, this burring process part is only what plays a role, such as positioning at the time of connecting a some heat-transfer plate. . Therefore, depending on the technical contents described in Patent Document 3, the effect of suppressing the above-described vortex flow and reducing the pressure loss cannot be expected.

JP 2010-249399 A JP 2010-054187 A JP 2005-345072 A

  The present invention has been conceived under the circumstances as described above, and a plate-type heat exchanger capable of reducing pressure loss by a simple means compared to the prior art, and a hot water apparatus provided with the same The challenge is to provide

  In order to solve the above problems, the present invention takes the following technical means.

  The plate-type heat exchanger provided by the first aspect of the present invention includes a plurality of heat transfer plates stacked in the thickness direction, and at least a pair of heat transfer plates adjacent to each other among the plurality of heat transfer plates. Between the plates, there is formed a flat channel for circulating the fluid to be heat exchanged, and the fluid inflow opening is provided at one end of the pair of heat transfer plates. The other end side is provided with an outflow opening for the fluid that has passed through the flow path from the inflow opening side, and the outflow opening is in the stacking direction of the pair of heat transfer plates. A plate-type heat exchanger that opens toward the fluid, and the fluid that has reached the region is downstream of the region facing the outflow opening in the fluid flow direction. And go further downstream It is characterized in that the flow restricting portion capable suppression is provided and.

  According to such a configuration, when the fluid subject to heat exchange flows in the flow path and reaches the region facing the outflow opening, most of the fluid proceeds further downstream than the region. This is suppressed by the flow restricting unit. As described above, when most of the fluid flowing through the flat flow channel flows downstream from the region facing the outflow opening, a vortex is generated in the downstream region, and this is the outflow opening. However, according to the present invention, it is possible to appropriately suppress such a phenomenon. As a result, the pressure loss can be reduced as compared with the prior art. This brings about an advantage that, for example, the load of the pump that supplies fluid to the plate heat exchanger is reduced, and the power consumption thereof is suppressed.

  In the present invention, preferably, the pair of heat transfer plates are provided with a first heat transfer plate provided with the outflow opening and an additional opening facing the outflow opening. One or both of the second heat transfer plate and the outflow opening and the additional opening are burring holes, and downstream of the peripheral edge of the opening as the burring hole in the fluid flow direction. A non-cylindrical burring part protruding toward the inside of the flow path is provided at the side position, and this burring part constitutes the flow restricting part.

  According to such a structure, when providing a predetermined opening part in a heat exchanger plate, a flow control part can be formed easily and appropriately by using this opening part as a burring hole. Therefore, it is suitable for reducing the manufacturing cost.

  In the present invention, preferably, both the outflow opening and the additional opening are burring holes, and a part of each of the burring portion of the outflow opening and the burring portion of the additional opening. Are overlapped in the direction in which the pair of heat transfer plates are stacked.

According to such a configuration, in the stacking direction of the heat transfer plates, a large gap (a gap through which the fluid can pass) is not generated between the two burring portions, and the fluid flow is accurately regulated. This is advantageous. From the viewpoint of increasing the strength of the burring portion, it is preferable to braze the two burring portions, but if the two burring portions are overlapped as described above, they are appropriately brazed. It is also easy to attach.

  The hot water apparatus provided by the second aspect of the present invention is a hot water apparatus provided with a heat exchanger for heating hot water, and is provided as the heat exchanger by the first aspect of the present invention. A plate heat exchanger is used.

  According to such a configuration, the same effect as described for the plate heat exchanger provided by the first aspect of the present invention can be obtained.

  In the present invention, preferably, in the plate heat exchanger, the first and second flow paths are alternately formed between the plurality of heat transfer plates, and the first flow path is heated. While the target hot water is supplied, the second flow path is supplied with a refrigerant of a heat pump so that heat can be exchanged between the refrigerant and the hot water. Among the flow paths, at least the first flow path is a flow path provided with the flow restricting portion.

  According to such a configuration, an effect of reducing at least the pressure loss of the first flow path can be obtained, and power saving of the pump that supplies hot water to the first flow path can be achieved. When the hot water device is configured as, for example, a hot water supply device for heating, it is stronger to reduce the pressure loss in the plate heat exchanger because the heating hot water circuit itself causes a large pressure loss. Although desired, the configuration described above is optimal in such cases.

  Other features and advantages of the present invention will become more apparent from the following description of embodiments of the present invention with reference to the accompanying drawings.

It is a schematic explanatory drawing which shows an example of the hot water apparatus to which this invention was applied. It is a disassembled perspective view which shows an example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing of the plate type heat exchanger shown in FIG. It is principal part plane explanatory drawing of FIG. (A)-(c) is principal part plane explanatory drawing which shows the example different from the structure shown in FIG. It is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. (A), (b) is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. (A), (b) is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing which shows the other example of the plate type heat exchanger to which this invention was applied. It is principal part sectional drawing which shows contrast with this invention.

  Hereinafter, preferred embodiments of the present invention will be specifically described with reference to the drawings.

The hot water device WH shown in FIG. 1 is a heat pump type hot water device for heating, and includes a heat pump unit U1 and a heat exchange unit U2.

  The heat exchange unit U2 includes a plate heat exchanger HE to which the present invention is applied (hereinafter, abbreviated as “heat exchanger HE” as appropriate). The heat exchanger HE includes, for example, a floor heating terminal unit. 9 is connected. The heat exchange unit U2 further includes a pump P1 for circulating hot water in a hot water circuit 10 connecting the heat exchanger HE and the floor heating terminal unit 9, and an expansion tank 11.

  The heat pump unit U1 constitutes a heat pump by using the heat exchanger HE of the heat exchange unit U2 as a condenser. This heat pump is configured to circulate refrigerant in a refrigerant circuit 20 that connects an evaporator 21, a compressor 22, a heat exchanger HE (condenser), and an expansion valve 23 provided with a fan 21a. .

  Next, details of the heat exchanger HE will be described.

  The heat exchanger HE allows the hot water to be heated by exchanging heat between the two types of fluids, ie, the heating hot water and the refrigerant. The heat exchanger HE includes a predetermined flow restricting unit 7 described later. There is a feature in that. Other basic configurations of the heat exchanger HE are the same as those conventionally known in Patent Documents 1 and 2, for example. Therefore, this point is simplified.

  As shown in FIGS. 2 and 3, the heat exchanger HE includes a top plate 4, a plurality of first and second heat transfer plates 3 </ b> A and 3 </ b> B, an end plate 50, and a bottom plate 51. These are all formed by pressing a metal plate made of stainless steel or the like, and the shape in plan view is substantially rectangular. In addition, these members are stacked in the thickness direction (the vertical direction in the present embodiment), and are joined using means such as brazing. As shown well in FIG. 2, the top plate 4 is provided with an inlet 41 and an outlet 42 for hot water to be heated, and an inlet 43 and an outlet 44 for the refrigerant. These portions are connected to pipes for hot water and refrigerant, and as means for that purpose, pipe connection members (not shown) are appropriately attached to the top plate 4. The end plate 50 is for closing openings 31 to 34 described later provided in the heat transfer plate located in the lowermost layer among the first and second heat transfer plates 3A and 3B. The bottom plate 51 is useful for increasing the strength of the heat exchanger HE.

  The plurality of first and second heat transfer plates 3A and 3B are alternately stacked one by one, whereby the hot water channel 6A and the refrigerant channel 6B are alternately formed in the vertical direction. ing. The hot water channel 6A is on the upper side of the second heat transfer plate 3B (below the first heat transfer plate 3A), and the refrigerant channel 6B is on the lower side of the second heat transfer plate 3B. (The upper side of the first heat transfer plate 3A).

  Four openings 31 to 34 are formed in the vicinity of both end portions of the first and second heat transfer plates 3A and 3B. These openings 31 to 34 are, for example, circular through holes that are opened in the direction in which the first and second heat transfer plates 3A and 3B are stacked. While the hot water supplied to the inlet 41 of the top plate 4 passes downward through the opening 31, a part of it proceeds to each of the plurality of flow channels 6A for hot water and flows through each flow channel 6A. The hot and cold water passes upward through the opening 32 and reaches the outlet 42. On the other hand, the refrigerant supplied to the inflow port 43 passes downward through the opening 33, and part of the refrigerant proceeds to each of the plurality of refrigerant flow paths 6B, and the hot water flowing through each flow path 6B. Passes upward through the opening 34 and reaches the outlet 44. When hot water and refrigerant flow through such a path, heat transfer (heat exchange) is performed between the first and second heat transfer plates 3A and 3B.

FIG. 3 shows a flow path 6A for hot water (FIG. 3 shows openings 31 and 3 of the heat exchanger HE.
2 is a cross-sectional view at position 2). The minimum combination unit of the heat transfer plates constituting one flow path 6A is a pair of first and second heat transfer plates 3A and 3B. In the pair of first and second heat transfer plates 3A and 3B which are such a minimum combination unit, the opening for flowing hot water into and out of the flow path 6A is the opening 31 of the first heat transfer plate 3A. (31a) and 32 (32a). Therefore, the opening 31a corresponds to an example of an “inflow opening for fluid” in the present invention, and the opening 32a corresponds to an example of an “outflow opening” for a fluid in the present invention. The opening 32a faces the opening 32 (32b) of the second heat transfer plate 3B, and the opening 32b corresponds to an example of the “additional opening” in the present invention.

  The hot water channel 6A is provided with a flow restricting portion 7 for reducing pressure loss. This flow restricting portion 7 is for suppressing the hot water that has reached the facing region 60 (the region below the opening 32a) of the opening 32a from passing through the region 60 and further proceeding to the downstream region 61. Part. The flow restricting portion 7 is provided by the opening 32a being a burring hole. More specifically, a burring portion (convex portion) that protrudes downward is integrally formed on the periphery of the opening portion 32a by pressing (burring), but in the present embodiment, this burring portion is This is a flow restriction unit 7. However, unlike the normal burring portion, the flow restricting portion 7 is not in a cylindrical shape but is in a planar cross-sectional arc shape (see also FIGS. 4 and 5), and is downstream of the peripheral edge of the opening 32a in the hot water flow direction. It is provided on the side (left side in FIG. 3) and is not provided on the upstream side. Preferably, as shown in the partially enlarged view of FIG. 3, the dimension S1 of the gap between the lower end tip of the flow restricting portion 7 and the second heat transfer plate 3B is configured to be as small as possible. . It can also be set as the structure which brazed the lower end front-end | tip part of the flow control part 7 to the 2nd heat-transfer plate 3B.

  As shown in FIG. 4, the flow restricting portion 7 is provided, for example, in a direction with little inclination with respect to the position where the opening 31 a is formed. In the figure, a step 39 capable of preventing the hot water from traveling around the opening 33 is formed, and most of the hot water flowing into the flow path 6A from the opening 31a is in the longitudinal direction of the flow path 6A. There is a strong tendency to proceed and reach the facing region 60 of the opening 32a as it is. Therefore, according to such a structure, the flow control effect by the flow control part 7 can be made favorable.

FIG. 5 shows an example where the flow of hot water is different from that in FIG. In FIG. 5A, means corresponding to the step 39 in FIG. 4 is not provided, and hot water flows into the periphery of the opening 33. In such a configuration, the amount of hot water traveling from the periphery of the opening 33 to the facing region 60 of the opening 32a is slightly increased. Therefore, in such a case, it is preferable that the direction of the flow restricting portion 7 is a direction that is swung toward the opening 33 in a plan view.
In FIGS. 2B and 2C, the openings 31a and 32a are provided so as to be positioned on the diagonal line of the flow path 6A. In FIG. 5B, a step 39 is provided around the opening 33 to prevent the hot water from proceeding. In this case, the hot water is in the flow path 6A with respect to the opposed region 60 of the opening 32a. There is a strong tendency to proceed in the longitudinal direction (non-diagonal direction). Therefore, in this case, the direction of the flow restricting portion 7 is not shaken obliquely. On the other hand, in FIG. 3C, the step 39 is not provided, and the amount of hot water that proceeds from the periphery of the opening 33 to the facing region 60 of the opening 32a increases. Therefore, in this case, it is preferable that the direction of the flow restricting portion 7 is a direction swung toward the opening 33.
As can be understood from these examples, the specific direction of the flow regulating unit 7 may be appropriately changed in consideration of the actual flow of hot water. Of course, it is not limited to the example shown in FIG. 4 and FIG.

In the heat exchanger HE of the present embodiment, no means corresponding to the flow restricting portion 7 described above is provided for the refrigerant flow path 6B. In the hot water circuit 10 shown in FIG. 1, since the flow path resistance of the floor heating terminal unit 9 is considerably large, it is necessary to reduce the pressure loss of the hot water flow path 6A from the viewpoint of reducing the load of the pump P1 as much as possible. In contrast, in the refrigerant circuit 20 shown in FIG. 1, such a necessity is small (however, the present invention may be applied to the refrigerant flow path 6B to provide a flow restricting portion. ). The flow path 6B for refrigerant is the same as the flow path 6A for hot water except for the point that the flow restricting portion 7 is not provided, and the description thereof is omitted.

  In the heat exchanger HE described above, the following operation is obtained.

As clearly shown in the partial enlarged view of FIG. 3, a part of the hot water flowing into the flow path 6A from the opening 31a passes through the flow path 6A in the surface direction of the first and second heat transfer plates 3A and 3B. It proceeds in the (horizontal direction) and reaches the facing region 60 of the opening 32a. On the other hand, since the flow restricting portion 7 exists on the downstream side of the facing region 60, most of the hot water described above is prevented from flowing downstream from the flow restricting portion 7. For this reason, it is difficult for a swirl of hot water to occur on the downstream side of the facing region 60 of the opening 32a, and even if a swirl occurs, the effect does not reach the facing region 60.
In the comparison shown in FIG. 13, the flow restricting unit 7 is not provided. According to such a configuration, most of the hot water that has reached the facing region 60 of the opening 32 a proceeds to the downstream region 61. Since the wall 38 of the first and second heat transfer plates 3A and 3B exists at the end of the downstream region 61 and is in a dead end state, a vortex of hot water is generated in the region 61. As a result of this eddy current also reaching the facing region 60 of the opening 32a, it becomes a great resistance when hot water passes through the opening 32a upward and flows out.
On the other hand, in the heat exchanger HE of the present embodiment, the phenomenon as described above is prevented, and an action of allowing hot water to smoothly pass through the opening 32a is obtained. Therefore, the pressure loss in the hot water channel 6A of the heat exchanger HE can be reduced. This is preferable in reducing the load of the pump P1 shown in FIG. 1 and reducing its power consumption.

  In the present embodiment, a burring portion having an arcuate plane cross section is formed on the periphery of the opening 32 a, and this is used as the flow restricting portion 7. Accordingly, it is possible to easily form the flow restricting portion 7 by burring, and it is possible to prevent a problem such as a significant increase in manufacturing cost. Since the flow restricting portion 7 is formed only on the first heat transfer plate 3A and not on the second heat transfer plate 3B, there is also an advantage that the number of steps for forming the flow restricting portion 7 can be reduced. It is done.

Moreover, according to the structure which provided the flow control part 7 only in the 1st heat-transfer plate 3A, the following advantages are also acquired.
That is, in the heat exchanger HE, a plurality of pairs of first and second heat transfer plates 3A and 3B are laminated as shown in FIG. 6, for example, in order to adjust the heat exchange capacity and height, or for other purposes. There may be a case where one heat transfer plate 3 ′ is further desired to be added above the laminated portion R1. In such a case, even if the second heat transfer plate 3B is used as it is as the heat transfer plate 3 ', there is a problem that a part of the second heat transfer plate 3B is unjustly brought into contact with the top plate 4. In addition, it is not necessary to separately use a dedicated heat transfer plate having a different configuration (there is no disadvantage as in the embodiment of FIG. 7 described later).

  7 to 12 show other embodiments of the present invention. In these drawings, elements that are the same as or similar to those in the above embodiment are given the same reference numerals as in the above embodiment.

In the embodiment shown in FIG. 7 (a), the flow restricting portion 7A is configured as a burring portion provided continuously to the periphery of the opening 32b of the second heat transfer plate 3B. The first heat transfer plate 3A is not provided with the flow restricting portion 7A. Even with such a configuration, the intended effect of the present invention can be obtained.
When the height H1 of the flow restricting portion 7A is higher than the height H2 of other portions of the second heat transfer plate 3B, as shown in FIG. As the heat transfer plate 3 ′ additionally disposed on the upper side of the stacked portion R1 of the heat transfer plates 3A and 3B, the second heat transfer plate 3B including the flow restricting portion 7A cannot be used. This is because the tip of the flow restricting portion 7A comes into contact with the top plate 4 and it is difficult to assemble the top plate 4. Therefore, in such a case, as the additional heat transfer plate 3 ′, the heat transfer plate in which the burring portion is not formed, that is, the second heat transfer plate 3B of the embodiment shown in FIGS. 1 to 6 is used. That's fine.

  In the embodiment shown in FIG. 8A, the flow restricting portion 7B is constituted by a pair of upper and lower burring portions 70, 71 connected to the peripheral edges of the openings 32a, 32b. According to such a structure, since each protrusion height of the burring parts 70 and 71 can be made low, the advantage that the burring process for forming them becomes easy is acquired. Moreover, it is also possible to set the height H3 of the burring part 71 to be equal to or lower than the upper surface height H2 of the other part of the second heat transfer plate 3B. If it does in this way, as shown in the figure (b), as 2nd heat-transfer plate 3 'additionally arranged above the lamination | stacking part R1 of 1st and 2nd heat-transfer plate 3A, 3B, 2nd heat-transfer Even if the plate 3B is used as it is, the burring portion 71 and the top plate 4 can be prevented from being unduly interfered. Therefore, as in the case of FIG. 6, it is not necessary to separately prepare a heat transfer plate having a configuration different from that of the first and second heat transfer plates 3A and 3B.

  In the embodiment shown in FIG. 9A, as in FIG. 8, the flow restricting portion 7C is configured by a pair of upper and lower burring portions 72 and 73, but these portions are close to each other (including contact). ) And overlap in the vertical direction. According to such a configuration, a gap through which hot water passes between the burring portions 72 and 73 can be prevented from being generated or hardly generated. From the viewpoint of increasing the mechanical strength, it is preferable to braze the burring portions 72 and 73. However, as described above, if part of them overlap each other, the brazing can be facilitated and optimized. Figured.

  In the present embodiment, the height H4 of the burring portion 73 is set to be equal to or lower than the height H2 of other portions of the second heat transfer plate 3B. Therefore, as shown in FIG. 9B, the second heat transfer plate 3 </ b> B can be used as it is as the heat transfer plate 3 ′ additionally disposed immediately below the top plate 4. As a result, it is also possible to eliminate the need to separately prepare a heat transfer plate having a configuration different from that of the first and second heat transfer plates 3A and 3B.

  In the embodiment shown in FIG. 10, the flow restricting portion 7D is formed by so-called step pressing. More specifically, in the present embodiment, the region on the downstream side in the hot water flow direction of the peripheral edge of the opening 32a of the first heat transfer plate 3A is inclined at a gentle angle, and the second heat transfer plate 3B. Pressed to approach. In the present invention, when the flow restricting portion is formed by press working, it is possible to adopt a processing means as in this embodiment instead of burring. Of course, as in the case of the burring process described above, the step pressing process as described above is performed on the second heat transfer plate 3B instead of the first heat transfer plate 3A, and further, the first and first It can also be set as the structure given to both of 2 heat-transfer plates 3A and 3B.

  In the embodiment shown in FIG. 11, a member 74 separate from the first and second heat transfer plates 3A and 3B is interposed and fixed on the downstream side in the hot water flow direction of the facing region 60 of the opening 32a. The member 74 is a flow restricting portion 7E. The member 74 has, for example, an arc shape in plan view. According to such a configuration, although it is necessary to use the member 74 separately, it is possible to obtain the operation intended by the present invention.

In the embodiment shown in FIG. 12, the flow restricting portion 80 is provided at a position upstream of the facing region (lower region) 68 of the hot water inflow opening 31 a in the hot water flow direction. The flow restricting portion 80 can be formed by a method similar to the forming method of the flow restricting portions 7 and 7A to 7E, and is formed by, for example, burring. According to the present embodiment, it is possible to make it difficult for hot water to generate a vortex in the upstream region 69 of the facing region 68 of the opening 31 a and to prevent the vortex from adversely affecting the facing region 68. For this reason, the effect of reducing the pressure loss can be expected.
However, in the configuration shown in the figure, when hot water flows downward into the flow path 6A from the opening 31a, most of the hot water passes through the opening 31 of the second heat transfer plate 3B and passes downward. (Flow into the other flow path 6A). Therefore, it can be said that the effect of reducing the pressure loss by providing the flow restricting portion 80 on the side of the hot water inflow opening 31a is small as compared with the configuration in which the flow restricting portion 7 is provided on the side of the hot water outflow opening 32a.
On the other hand, in the flow path 6A located in the lowermost layer, since the opening 31 of the second heat transfer plate 3B is closed by the end plate 50, the hot water flowing into the flow path 6A from the opening 31a flows as it is. The entire amount of the hot and cold water proceeds in the horizontal direction toward the opening 32a without passing through the path 6A. In such a case, the effect of reducing the pressure loss by providing the flow restricting portion 80 on the opening 31a side to prevent the swirling of hot water becomes large.
As will be understood from the present embodiment, in the present invention, in addition to providing the flow restricting portion on the opening side for hot water outflow, the flow restricting portion is further provided on the opening side for hot water inflow. You can also.

  The present invention is not limited to the contents of the above-described embodiment. The specific configuration of each part of the plate heat exchanger and the hot water apparatus according to the present invention can be variously modified within the scope intended by the present invention.

  The pair of heat transfer plates referred to in the present invention is configured to be able to form a flat flow path for circulating a fluid to be heat exchanged between them, and for fluid inflow at one end thereof. The opening may be provided, and the other end may be provided with an inflow opening that opens in the stacking direction of the pair of heat transfer plates. In the heat exchanger of the above-described embodiment, two types of flow paths for circulating hot water and a refrigerant are formed, but the present invention is not limited to this. In the present invention, for example, as in the heat exchanger described in Patent Document 3, only one type of flow path through which hot water to be heated flows is formed by the heat transfer plate, and on the outer surface of the heat transfer plate. It can also be configured as a type of heat exchanger in which the hot water is heated by the action of a heating fluid such as combustion gas. Moreover, the specific kind of the fluid used as heat exchange object is not ask | required. The hot water referred to in the present invention includes antifreeze.

  The flow restricting portion referred to in the present invention is provided on the downstream side in the fluid flow direction of the region facing the outflow opening, and the fluid that has reached the region passes through the region and further proceeds downstream. What is necessary is just to have the function which can be suppressed. The specific size and shape are not limited, and a method other than the above-described embodiment can be employed as the formation method.

  The hot water apparatus according to the present invention can use an apparatus / equipment other than a heat pump as a heat source for hot water heating. Furthermore, it can also be configured as a hot water supply device for bath hot water supply or general hot water supply instead of or in addition to heating.

WH Hot water device HE Heat exchanger (Plate type heat exchanger)
U1 heat pump units 3A, 3B first and second heat transfer plates (heat transfer plates)
6A Channel for hot water (channel)
7, 7A-7E Flow restricting portion 31a Opening (fluid inflow opening)
32a Opening (fluid outflow opening)
32b opening (additional opening)
60 opposite area (of fluid outlet)

Claims (5)

A plurality of heat transfer plates are laminated in the thickness direction, and among the plurality of heat transfer plates, a flat for circulating a fluid to be heat exchanged between at least a pair of heat transfer plates adjacent to each other. Shaped flow path,
The fluid inflow opening is provided at one end of the pair of heat transfer plates, and the fluid outflow opening that has passed through the flow path from the inflow opening is provided at the other end. Is provided,
The outflow opening is a plate heat exchanger that opens in the direction of stacking of the pair of heat transfer plates,
The flow that can suppress the fluid that has reached the region from passing through the region and proceeding further downstream is provided downstream of the flow path in the region facing the outflow opening. A plate heat exchanger, characterized in that a regulating part is provided. The plate heat exchanger according to claim 1,
The pair of heat transfer plates are a first heat transfer plate provided with the outflow opening and a second heat transfer plate provided with an additional opening facing the outflow opening. Yes,
One or both of the outflow opening and the additional opening are burring holes, and the flow path is located at the downstream side in the fluid flow direction of the periphery of the opening as the burring hole. A plate-type heat exchanger, in which a non-cylindrical burring portion projecting inward is provided, and this burring portion constitutes the flow restricting portion. The plate heat exchanger according to claim 2,
Both the outflow opening and the additional opening are burring holes, and a part of each of the burring portion of the outflow opening and the burring portion of the additional opening is the pair of heat transfer A plate heat exchanger that overlaps in the stacking direction. A hot water apparatus having a heat exchanger for hot water heating,
A hot water apparatus using the plate heat exchanger according to any one of claims 1 to 3 as the heat exchanger. The hot water device according to claim 4,
In the plate heat exchanger, first and second flow paths are alternately formed between the plurality of heat transfer plates, and hot water to be heated is supplied to the first flow path. On the other hand, the second flow path is supplied with heat pump refrigerant so that heat exchange between the refrigerant and hot water is possible.
Of the first and second flow paths, at least the first flow path is a hot water apparatus provided with the flow restricting portion.

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