JP7290030B2 - Heat exchanger - Google Patents

Description

The present disclosure relates to heat exchangers.

A vehicle is provided with a plurality of heat exchangers for exchanging heat between fluids. Such a heat exchanger includes, for example, a cooling heat exchanger for reducing the temperature of cooling water by heat exchange with a refrigerant. Objects to be cooled by cooling water are, for example, internal combustion engines and batteries.

Patent Literature 1 listed below discloses an example of the heat exchanger as described above. In this heat exchanger, a plurality of tubes connected to the tank are accommodated inside the case together with the tank. Refrigerant, which is one of the fluids to be subjected to heat exchange, is supplied from the outside into the tank and then distributed to each tube while flowing along the longitudinal direction of the tank. Cooling water, which is the other fluid to be subjected to heat exchange, flows through the space outside the tank and the tube after being supplied into the case. As a result, heat is exchanged between the refrigerant passing inside the tubes and the cooling water passing outside the tubes.

In such a heat exchanger, the channel through which the refrigerant flows and the channel through which the cooling water flows are separated by a single metal plate forming a tube or the like.

DE 102015111393 A1

The pressure of the refrigerant circulating in the refrigeration cycle is often higher than the pressure of the cooling water. If a part of the refrigeration cycle, such as an expansion valve, malfunctions, this may cause a further increase in refrigerant pressure. If the pressure of the refrigerant flowing inside the tube or tank becomes too large compared to the pressure of the cooling water flowing outside, the tube or the like will be damaged due to the pressure difference. If a tube or the like is damaged, the refrigerant leaking from the damaged portion also increases the pressure in the circulation path of the cooling water. As a result, it becomes impossible to properly cool devices such as batteries.

SUMMARY OF THE INVENTION An object of the present disclosure is to provide a heat exchanger that does not damage a cooling water circulation path even when the pressure of a refrigerant rises.

The heat exchanger according to the present disclosure is a heat exchanger (10) that exchanges heat between a refrigerant and cooling water, and includes an internal member (200) configured to allow the refrigerant to flow inside, and A case (100) that is a container that houses the internal member and that is configured to allow cooling water to flow in a space around the internal member. A coolant supply pipe (11) for supplying coolant to the internal member and a coolant discharge pipe (12) for discharging the coolant from the internal member are connected to the case. Of the portions through which the coolant flows, some of the portions whose surfaces are exposed to the outside air have priority damage portions (121, 12 , 130A, 140, 150) are provided.

In a heat exchanger having such a configuration, when the pressure of the refrigerant rises, the preferentially damaged portion is damaged before the tubes and the like constituting the internal members are damaged. The preferentially damaged portion is provided in a part of the portion through which the coolant flows, the surface of which is exposed to the outside air.

When the preferentially damaged portion is damaged, the refrigerant leaks from the preferentially damaged portion to the outside air side, so that the refrigerant does not flow into the flow path through which the cooling water flows. Since the pressure in the cooling water circulation path does not rise due to the leaked refrigerant, damage to the cooling water circulation path is prevented.

According to the present disclosure, there is provided a heat exchanger that does not damage the cooling water circulation path even when the pressure of the refrigerant rises.

FIG. 1 is a perspective view showing the appearance of the heat exchanger according to the first embodiment. FIG. 2 is an exploded view showing the internal configuration of the heat exchanger according to the first embodiment. FIG. 3 is a diagram showing the configuration of a refrigerant discharge pipe and its vicinity in the heat exchanger according to the first embodiment. FIG. 4 is a diagram showing the configuration of a refrigerant discharge pipe and its vicinity in the heat exchanger according to the first embodiment. FIG. 5 is a diagram showing the configuration of the refrigerant discharge pipe and its vicinity in the heat exchanger according to the second embodiment. FIG. 6 is a diagram showing the configuration of the refrigerant discharge pipe and its vicinity in the heat exchanger according to the third embodiment. FIG. 7 is a diagram showing the configuration of the refrigerant discharge pipe and its vicinity in the heat exchanger according to the third embodiment. FIG. 8 is a diagram showing the configuration of a refrigerant discharge pipe and its vicinity in a heat exchanger according to a fourth embodiment. FIG. 9 is a diagram showing the configuration of the refrigerant discharge pipe and its vicinity in the heat exchanger according to the fifth embodiment. FIG. 10 is a diagram showing the configuration of the refrigerant discharge pipe and its vicinity in the heat exchanger according to the sixth embodiment.

Hereinafter, this embodiment will be described with reference to the accompanying drawings. In order to facilitate understanding of the description, the same constituent elements in each drawing are denoted by the same reference numerals as much as possible, and overlapping descriptions are omitted.

A first embodiment will be described. A heat exchanger 10 according to this embodiment is mounted on a vehicle (not shown). The heat exchanger 10 is configured as a heat exchanger for exchanging heat between the refrigerant and cooling water that circulate through the vehicle.

A refrigerant, which is one of the fluids to be subjected to heat exchange, circulates through an air-conditioning refrigeration cycle (not shown) mounted on the vehicle. As the refrigerant, an air conditioning refrigerant such as R1234yf is used in this embodiment, but carbon dioxide such as R744 may be used as the refrigerant. The refrigerant passes through an expansion valve (not shown) provided in the refrigeration cycle to reduce its temperature and pressure, and then is supplied to the heat exchanger 10 as a cooling fluid. The refrigerant evaporates as it passes through the heat exchanger 10 and changes from a liquid phase to a gas phase. That is, the heat exchanger 10 in this embodiment functions as an evaporator for evaporating the refrigerant.

The other fluid with which heat is exchanged, cooling water, circulates in its path through the vehicle's internal combustion engine. LLC is used as the cooling water in this embodiment, but water may be used as the cooling water. Also, the object to be cooled by the cooling water may be a motor generator, an inverter, or the like instead of the internal combustion engine. The cooling water is supplied to the heat exchanger 10 after passing through an internal combustion engine or the like to increase its temperature.

In the heat exchanger 10, heat is exchanged between the low-temperature refrigerant and the high-temperature cooling water. The heat exchanger 10 is configured as a cooling heat exchanger for lowering the temperature of cooling water by heat exchange with a refrigerant.

As shown in FIGS. 1 and 2, the heat exchanger 10 includes a case 100 and an internal member 200. As shown in FIG.

First, the configuration of the case 100 will be described. The case 100 is a container whose entirety is generally rectangular parallelepiped. Both the refrigerant and the heat exchanger supplied from the outside are supplied to the inside of the case 100 . Heat exchange between the refrigerant and cooling water takes place inside the case 100 . The refrigerant and cooling water after heat exchange are discharged from the case 100 to the outside.

The case 100 has a container member 102 and a plate member 101 . The container member 102 is a portion that forms substantially the entire case 100, and is made of resin in this embodiment. The container member 102 is formed as a substantially rectangular parallelepiped container, one side of which is open. The plate-like member 101 is a plate-like member provided so as to close the open side surface. In this embodiment, the plate member 101 is made of aluminum.

The plate-like member 101 is partially crimped and thereby fixed to the container member 102 . Instead of such a mode, for example, a mode in which the plate member 101 is fastened and fixed to the container member 102 by bolts or the like may be used.

As shown in FIG. 2, an annular seal member OR is sandwiched between the plate member 101 and the container member 102 . The seal member OR is a packing made of rubber, for example. A seal member OR seals the space between the plate member 101 and the container member 102 in a watertight manner.

1 and 2, the horizontal direction from the plate member 101 side to the container member 102 side is the x direction, and the x axis is set along the same direction. there is The y direction is a direction perpendicular to the x direction and extends along the long side of the opening of the container member 102 from the front side to the back side of the paper surface. Axis is set. Furthermore, the direction perpendicular to both the x-direction and the y-direction and extending from the lower side to the upper side is the z-direction, and the z-axis is set along the same direction. In the following description, the x-direction, y-direction, and z-direction defined above will be used. The same applies when referring to figures other than FIGS. 1 and 2. FIG.

A plate member 101 that is part of the case 100 is provided with a coolant supply pipe 11, a coolant discharge pipe 12, a cooling water supply pipe 21, and a cooling water discharge pipe 22, respectively.

The refrigerant supply pipe 11 is a pipe for supplying a refrigerant to an internal member 200, which will be described later, and is provided as an inlet for the refrigerant. The refrigerant discharge pipe 12 is a pipe for discharging the refrigerant from the internal member 200 and is provided as an outlet for the refrigerant. The coolant that has flowed from the coolant supply pipe 11 flows inside the internal member 200 , specifically, the inside of the tank 210 , and flows through the insides of the members forming the internal member 200 . After that, the refrigerant is discharged from the tank 220 of the internal member 200 to the outside through the refrigerant discharge pipe 12 .

Both the coolant supply pipe 11 and the coolant discharge pipe 12 are provided so as to protrude in the -x direction from the plate member 101, that is, the side surface of the case 100 on the -x direction side. In this embodiment, both the coolant supply pipe 11 and the coolant discharge pipe 12 are connected to the plate member 101 via the block 130 . Alternatively, the refrigerant supply pipe 11 and the refrigerant discharge pipe 12 may be directly connected to the surface of the plate member 101 without the block 130 interposed therebetween.

The block 130 is a substantially rectangular parallelepiped member made of aluminum and joined to the surface of the plate member 101 . Inside the block 130, a flow path through which the refrigerant flows from the refrigerant supply pipe 11 to the internal member 200 and a flow path through which the refrigerant flows from the internal member 200 to the refrigerant discharge pipe 12 are formed. Block 130 corresponds to the "connecting member" in this embodiment. Instead of the above aspect, only one of the refrigerant supply pipe 11 and the refrigerant discharge pipe 12 may be connected to the case 100 via the block 130 which is a connecting member.

The coolant supply pipe 11 and the coolant discharge pipe 12 are provided in the plate member 101 at positions closer to the -y direction side than the center along the y direction. Also, the coolant supply pipe 11 is provided at a position on the −z direction side of the coolant discharge pipe 12 . The position of the coolant supply pipe 11 is a position corresponding to the tank 210 of the internal member 200 . The position of the refrigerant discharge pipe 12 is a position corresponding to the tank 220 that the internal member 200 has.

The cooling water supply pipe 21 is a pipe for supplying cooling water to the case 100 and is provided as an inlet for the cooling water. The cooling water discharge pipe 22 is a pipe for discharging the cooling water from the case 100, and is provided as an outlet for the cooling water. The cooling water that has flowed from the cooling water supply pipe 21 flows into the space inside the case 100 and around the internal member 200 . After flowing through the space, the cooling water is discharged to the outside through the cooling water discharge pipe 22 .

The cooling water supply pipe 21 and the cooling water discharge pipe 22 are provided so as to protrude in the -x direction from the side surface of the plate member 101, that is, the case 100, on the -x direction side. In this embodiment, both the cooling water supply pipe 21 and the cooling water discharge pipe 22 are directly connected to the surface of the plate member 101 . Alternatively, the cooling water supply pipe 21 and the cooling water discharge pipe 22 may be connected to the plate member 101 via the block 130 in the same manner as the coolant supply pipe 11 and the like.

The cooling water supply pipe 21 is provided in the plate member 101 at a position closer to the -y direction than the center along the y direction. In addition, the cooling water discharge pipe 22 is provided in the plate-like member 101 at a position closer to the y-direction side than the center along the y-direction.

Next, the configuration of the internal member 200 will be described with reference to FIG. The internal member 200 is, as described above, a member configured so that the coolant flows inside it. The internal member 200 has three tanks 210 , 220 , 230 , a tube 240 and fins 250 . These are all made of aluminum and are integrated by brazing each other.

Tanks 210, 220, 230 are each formed as an elongated container. Each of the tanks 210, 220, and 230 is arranged with its longitudinal direction along the x-direction, and is brazed to the plate-like member 101 at its -x-direction end.

The tank 210 is connected from the x-direction side to the portion of the plate member 101 where the coolant supply pipe 11 is provided. All of the coolant supplied from the coolant supply pipe 11 flows into the tank 210 and flows in the longitudinal direction of the tank 210, that is, in the x direction. The refrigerant is distributed to each tube 240 which will be described later.

The tank 220 is connected from the x-direction side to the portion of the plate member 101 where the refrigerant discharge pipe 12 is provided. Refrigerant after heat exchange is carried out through each tube 240 flows into the tank 220 . The refrigerant flows from the tank 220 toward the refrigerant discharge pipe 12 and is discharged from the refrigerant discharge pipe 12 to the outside.

The tank 230 is connected from the x-direction side to a portion of the plate-like member 101 closer to the y-direction side than the center. Refrigerant flows from tank 210 into tank 230 through tube 240 . After folding back in the tank 230 , the refrigerant flows through the tube 240 again into the tank 220 .

Tube 240 is a tubular member formed to have a flattened cross section. A plurality of tubes 240 are provided and are arranged so as to line up in a plurality along the longitudinal direction of the tank 210 and the like, that is, along the x direction. A constant gap is formed between the tubes 240 adjacent to each other, and a fin 250, which will be described later, is arranged in the gap. Each tube 240 is arranged with its longitudinal direction along the y direction. That is, the longitudinal direction of the tube 240 is perpendicular to the respective longitudinal directions of the tanks 210 , 220 , 230 .

The −y direction end of the tube 240 is connected to the tanks 210 and 220 . The end of the tube 240 on the y-direction side is connected to the tank 230 .

The internal space of each tube 240 is separated at the central position along the z-direction. As a result, the tube 240 has two flow paths through which the coolant passes, and these flow paths are aligned in the z direction. Of these, the channel on the −z direction side connects the tank 210 and the tank 230 . In addition, the channel on the z-direction side connects the tank 220 and the tank 230 .

With the internal member 200 configured as described above, the coolant that has flowed from the coolant supply pipe 11 into the tank 210 passes through the flow path formed in the −z direction side of the tube 240, and flows into the tank 230. flow into The refrigerant flows into the tank 220 through the flow path formed in the z-direction side portion of the tube 240 and is discharged to the outside through the refrigerant discharge pipe 12 . As a configuration for realizing such a refrigerant flow, for example, a configuration in which the tanks 210 and 220 are integrated and the respective internal spaces are separated by walls may be adopted.

The fins 250 are so-called corrugated fins formed by bending a metal plate. A plurality of fins 250 are provided and arranged in the gaps between adjacent tubes 240, but only one fin 250 is illustrated in FIG. The fin 250 is formed such that peaks 251 protruding in the x direction and valleys 252 protruding in the -x direction are alternately arranged along the z direction. Both the peak portion 251 and the valley portion 252 are formed so as to extend linearly along the y direction. Since the fins 250 having such a shape are provided in the gaps between the tubes 240, the contact area with the cooling water is increased. Thereby, heat exchange between the refrigerant and the cooling water is performed more efficiently.

As described above, the heat exchanger 10 according to the present embodiment includes the internal member 200 configured to allow the refrigerant to flow inside, and a container for accommodating the internal member 200 inside. and a case 100 configured to allow cooling water to flow in the surrounding space.

The internal member 200 includes tanks 210 , 220 , 230 in which coolant flows and a plurality of tubes 240 along the longitudinal direction thereof. Each tube 240 is a tubular member connected to tanks 210 , 220 , 230 such that its longitudinal direction is perpendicular to the longitudinal direction of tanks 210 , 220 , 230 . Further, the respective tubes 240 are stacked and spaced apart from each other so as to line up along the longitudinal direction of the tanks 210 , 220 , 230 .

When heat exchange is being performed by the heat exchanger 10 , the refrigerant supplied by a refrigerant compressor (not shown) is supplied to the refrigerant supply pipe 11 . Cooling water sent out by a cooling water compressor (not shown) is supplied to the cooling water supply pipe 21 .

The pressure of the refrigerant circulating in the refrigeration cycle is often higher than the pressure of the cooling water. If a part of the refrigeration cycle, such as an expansion valve, malfunctions, this may cause a further increase in refrigerant pressure. If the pressure of the refrigerant flowing inside the tube 240, the tank 210, etc. becomes too large compared to the pressure of the cooling water flowing outside, the tube 240 etc. will be damaged due to the pressure difference. If the tube 240 or the like is damaged, the coolant leaking from the damaged portion also increases the pressure in the circulation path of the cooling water. As a result, it becomes impossible to appropriately cool the internal combustion engine or the like, which is the object to be cooled.

Therefore, in the heat exchanger 10 according to this embodiment, the above problem is solved by devising the shape of the refrigerant discharge pipe 12 . The device will be described with reference to FIGS. 3 and 4. FIG.

FIG. 3 shows a cross section of the refrigerant discharge pipe 12 and block 130 cut along the xy plane and viewed from the z direction side. FIG. 4 shows the appearance of the refrigerant discharge pipe 12 and the block 130 when viewed from the y-direction side.

As shown in FIG. 3, the block 130 is formed with a channel 131 through which the coolant passes extending along the x direction. A counterbore portion 132 having an inner diameter larger than the inner diameter of the flow path 131 is formed in the block 130 at a position corresponding to the end of the flow path 131 in the −x direction. The refrigerant discharge pipe 12 is inserted into the counterbore portion 132 from the −x direction side and is soldered to the inner surface of the counterbore portion 132 .

A concave portion 121 is formed on the outer surface of the refrigerant discharge pipe 12 on the y-direction side. The concave portion 121 is a circular depression that is recessed in the -y direction. Therefore, the plate thickness of the refrigerant discharge pipe 12 is locally reduced in the recess 121 . As a result, when the pressure of the refrigerant passing through the inside of the refrigerant discharge pipe 12 increases, the position of the concave portion 121 in the refrigerant discharge pipe 12 is the most likely to be damaged.

In the present embodiment, in the entire portion of the heat exchanger 10 through which the refrigerant flows, the concave portion 121 is the portion that is most likely to be damaged by the pressure of the refrigerant. Therefore, when the pressure of the refrigerant rises, the recessed portion 121 of the refrigerant discharge pipe 12 is damaged earlier than any of the parts forming the internal member 200 . In other words, the plate thickness of the concave portion 121 is determined so that the concave portion 121 is damaged earlier than the tube 240, the tank 210, and the like that constitute the internal member 200. As shown in FIG. As described above, the concave portion 121 is a portion that breaks earlier than the internal member 200 when the pressure of the refrigerant rises, and corresponds to the "priority broken portion" in the present embodiment.

The position where the concave portion 121, which is the preferentially damaged portion, is provided is a portion of the portion through which the coolant flows, the surface of which is exposed to the outside air. Therefore, if the concave portion 121 is damaged when the pressure of the refrigerant rises, the refrigerant will leak from the damaged portion to the outside air side. Since the leaked refrigerant is discharged to the outside of the heat exchanger 10 without flowing into the cooling water circulation path, the cooling water circulation path does not rise. Therefore, even when the pressure of the refrigerant rises, damage to the circulation path of the cooling water is prevented.

The recessed portion 121 , which is a preferentially damaged portion, may be provided in a portion of the refrigerant discharge pipe 12 as in the present embodiment, but may be provided in a portion of the refrigerant supply pipe 11 . Moreover, the recessed portion 121 that is the preferentially damaged portion may be provided in both the coolant supply pipe 11 and the coolant discharge pipe 12 . The position where the preferentially damaged portion is provided may be a part of the portion where the coolant flows, the surface of which is exposed to the outside air.

A cross section indicated by a dotted line DL1 in FIG. 3 is a plane perpendicular to the direction in which the coolant flows and passes through the recessed portion 121, which is the preferentially damaged portion. Here, Te is the plate thickness of the concave portion 121 at the position of the cross section. Also, the equivalent diameter at the position of the cross section, that is, the equivalent diameter of the portion including the concave portion 121 is De. Further, let σe be the tensile strength of the material forming the recess 121 . It should be noted that the plate thickness does not include the thickness of the preferential corrosion layer SL, which will be described later.

Further, the plate thickness of the tank 210 is Th, the equivalent diameter of the tank 210 is Dh, and the tensile strength of the material forming the tank 210 is σh. Furthermore, the plate thickness of the tube 240 is Tt, the equivalent diameter of the tube 240 is Dt, and the tensile strength of the material forming the tube 240 is σt.

When various parameters such as Te are defined as described above, the heat exchanger 10 according to the present embodiment is configured to satisfy both the following formulas (1) and (2).
Th·σh/Dh>Te·σe/De (1)
Tt·σt/Dt>Te·σe/De (2)

Formulas (1) and (2) hold regardless of the x-coordinate of the dotted line DL1 as long as the dotted line DL1 in FIG. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

If the heat exchanger 10 is configured to satisfy both formulas (1) and (2), the recess 121 may break before the internal member 200 when the pressure of the refrigerant rises. becomes more certain. As a result, it is possible to reliably prevent the cooling water from being affected by the circulation path.

Other improvements will be explained. As shown in FIG. 3, the outer surface of the refrigerant discharge pipe 12 is covered with a preferential corrosion layer SL. The preferentially corroding layer SL is a layer formed of a material that corrodes preferentially to the material forming the refrigerant discharge pipe 12 . In this embodiment, the preferential corrosion layer SL is formed of zinc, which is a material that corrodes preferentially more easily than aluminum. Such a preferential corrosion layer SL can be formed, for example, by spraying zinc or applying a paint containing zinc. The preferential corrosion layer SL is not formed to cover the recess 121 , but is formed to cover the entire periphery of the recess 121 .

Corrosion of the refrigerant discharge pipe 12 occurs preferentially in the preferential corrosion layer SL. Therefore, while the preferentially corroded layer SL remains, the plate thickness of each portion of the refrigerant discharge pipe 12 does not change due to material corrosion. Therefore, it is possible to prevent the occurrence of a portion having a thickness smaller than that of the concave portion 121 or the thickness of the concave portion 121 from being further reduced. This allows the concave portion 121 to function as a preferential damaged portion for a long period of time.

A second embodiment will be described with reference to FIG. This embodiment differs from the first embodiment only in the aspect of the refrigerant discharge pipe 12 . Differences from the first embodiment will be mainly described below, and descriptions of common points with the first embodiment will be omitted as appropriate.

FIG. 5 shows a cross section of the refrigerant discharge pipe 12 and block 130 cut along the xy plane and viewed from the z direction. As shown in the figure, in this embodiment, the refrigerant discharge pipe 12 is not formed with the recess 121 as in the first embodiment. In this embodiment, the plate thickness of the refrigerant discharge pipe 12 as a whole is smaller than that in the first embodiment. As a result, the entire refrigerant discharge pipe 12 of the present embodiment is a portion that breaks before the internal member 200 when the pressure of the refrigerant increases. That is, in this embodiment, the entire refrigerant discharge pipe 12 corresponds to the "priority damaged portion". Even in such a mode, the same effects as those described in the first embodiment can be obtained.

A cross-section indicated by a dotted line DL2 in FIG. 5 is a plane perpendicular to the direction in which the coolant flows and passes through the coolant discharge pipe 12, which is the preferentially damaged portion. Let Te be the plate thickness of the refrigerant discharge pipe 12 at the position of the cross section, De be the equivalent diameter at the position of the cross section, and σe be the tensile strength of the material forming the refrigerant discharge pipe 12 . When Te, De, and σe are defined as above, the heat exchanger 10 is configured so as to satisfy the formulas (1) and (2) described above also in this embodiment. It should be noted that the plate thickness does not include the thickness of the preferentially corroded layer SL.

Formula (1) holds regardless of the x-coordinate of the dotted line DL2 as long as the dotted line DL2 in FIG. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

A third embodiment will be described with reference to FIGS. 6 and 7. FIG. This embodiment differs from the first embodiment only in aspects of the refrigerant discharge pipe 12 and the block 130 . Differences from the first embodiment will be mainly described below, and descriptions of common points with the first embodiment will be omitted as appropriate.

FIG. 6 shows a cross section of the refrigerant discharge pipe 12 and block 130 cut along the xz plane and viewed from the -y direction. FIG. 7 shows the external appearance of the refrigerant discharge pipe 12 and the block 130 when viewed from the z-direction side.

In this embodiment, the recess 121 is not formed in the refrigerant discharge pipe 12 . In this embodiment, a flow path 131A is formed inside the block 130 in addition to the flow path 131 . The channel 131A is branched from the middle of the channel 131A and formed to extend along the z direction. A sealing member 140 closes the end of the flow path 131A on the z-direction side. The sealing member 140 is a disk-shaped member made of aluminum and soldered to the block 130 .

The plate thickness of the sealing member 140 is smaller than the plate thickness of the block 130 around it. As a result, the sealing member 140 is a portion that breaks before the internal member 200 when the pressure of the refrigerant rises. Also, the sealing member 140 is provided on a part of the block 130 exposed to the atmosphere. That is, in the present embodiment, the sealing member 140, which is part of the block 130, corresponds to the "priority damaged portion". In this manner, even in a mode in which a portion of the block 130, which is a connection member, is provided with the preferentially damaged portion, the same effects as those described in the first embodiment can be obtained.

A cross section indicated by a dotted line DL3 in FIG. 6 is a plane perpendicular to the direction in which the coolant flows through the flow path 131 and passes through the sealing member 140, which is the preferentially damaged portion. Let Te be the plate thickness of the sealing member 140 at the position of the cross section, De be the equivalent diameter at the position of the cross section, and σe be the tensile strength of the material forming the sealing member 140 . When Te, De, and σe are defined as above, the heat exchanger 10 is configured so as to satisfy the formulas (1) and (2) described above also in this embodiment.

Formula (1) holds regardless of the x-coordinate of the dotted line DL3 as long as the dotted line DL3 in FIG. 6 passes through the sealing member 140. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

The material of the sealing member 140 may be the same material as that of the block 130 as in the present embodiment, or may be different from that of the block 130 .

In this embodiment, the preferential corrosion layer SL is formed so as to cover the surface of the block 130 on the z-direction side, that is, the surface around the sealing member 140 . The effect of forming the preferential corrosion layer SL is the same as that described in the first embodiment. Instead of such a mode, the preferential corrosion layer SL may be formed to cover the surface of the sealing member 140 instead of the surface of the block 130 . Alternatively, a preferential corrosion layer SL may be formed so as to cover the surface of each of the block 130 and the sealing member 140 .

A fourth embodiment will be described with reference to FIG. This embodiment differs from the first embodiment only in aspects of the refrigerant discharge pipe 12 and the block 130 . Differences from the first embodiment will be mainly described below, and descriptions of common points with the first embodiment will be omitted as appropriate.

FIG. 8 shows a cross section of the refrigerant discharge pipe 12 and block 130 cut along the xz plane and viewed from the -y direction.

In this embodiment, the recess 121 is not formed in the refrigerant discharge pipe 12 . In this embodiment, a small-diameter portion 122 having an outer diameter smaller than that of other portions is provided in a portion of the refrigerant discharge pipe 12 near the end portion on the x-direction side. In this embodiment, the small-diameter portion 122 is inserted through the counterbore portion 132 of the block 130 and is soldered.

A portion of the block 130 on the z-direction side of the flow path 131 has a smaller plate thickness than other portions. In FIG. 8, the part concerned is denoted by reference numeral "130A". Below, the said part is also called "thin part 130A."

In the present embodiment, the thin portion 130A is a portion that breaks before the internal member 200 when the pressure of the refrigerant increases. Also, the thin portion 130A is provided in a portion of the block 130 exposed to the atmosphere. That is, in the present embodiment, the thin portion 130A that is part of the block 130 corresponds to the "priority damaged portion". Even in such a mode, the same effects as those described in the first embodiment can be obtained.

A cross section indicated by a dotted line DL4 in FIG. 8 is a plane perpendicular to the direction in which the coolant flows through the flow path 131 and passes through the thin portion 130A, which is the preferentially damaged portion. Let Te be the plate thickness of the thin portion 130A at the position of the cross section, De be the equivalent diameter at the position of the cross section, and σe be the tensile strength of the material forming the thin portion 130A. When Te, De, and σe are defined as above, the heat exchanger 10 is configured so as to satisfy the formulas (1) and (2) described above also in this embodiment. It should be noted that the plate thickness does not include the thickness of the preferentially corroded layer SL.

Formula (1) holds regardless of the x-coordinate of the dotted line DL4 as long as the dotted line DL4 in FIG. 8 passes through the thin portion 130A. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

In this embodiment, the preferential corrosion layer SL is formed so as to cover the surface of the block 130 on the z-direction side, that is, the surface of the thin portion 130A. The effect of forming the preferential corrosion layer SL is the same as that described in the first embodiment.

A fifth embodiment will be described with reference to FIG. Differences from the first embodiment will be mainly described below, and descriptions of common points with the first embodiment will be omitted as appropriate.

In FIG. 9, the refrigerant supply pipe 11, the refrigerant discharge pipe 12, and the portions in the vicinity of these in the heat exchanger 10 are cut along the xz plane, and the cross section when viewed from the -y direction side is shown. It is shown.

In this embodiment, the recess 121 is not formed in the refrigerant discharge pipe 12 . Also, in this embodiment, the block 130 is not provided, and instead a connection plate 150 is provided.

The connection plate 150 is a generally flat plate-shaped member partly subjected to burring processing, and is made of aluminum in this embodiment. In FIG. 9, reference numerals 151 and 152 are assigned to the portions of the connection plate 150 that have undergone burring processing. Below, each part is also called "burring process part 151" and "burring process part 152."

Both the burring processed portion 151 and the burred processed portion 152 protrude in the -x direction, and circular openings are formed at the respective ends. The x-direction end of the coolant supply pipe 11 is inserted through the opening of the burring portion 151 and is soldered. The position where the burring portion 151 is formed corresponds to the tank 210 arranged inside the case 100 . In FIG. 9, a channel 101A formed in the plate-like member 101 is shown as connecting the coolant supply pipe 11 and the tank 210 .

Similarly, the x-direction end of the refrigerant discharge pipe 12 is inserted through the opening of the burring portion 152 and is soldered. The position where the burring portion 152 is formed corresponds to the tank 220 arranged inside the case 100 . FIG. 9 shows a channel 101B formed in the plate member 101 as a connection between the refrigerant discharge pipe 12 and the tank 220. As shown in FIG.

As described above, in the present embodiment, each of the coolant supply pipe 11 and the coolant discharge pipe 12 is connected to the case 100 via the connection plate 150 subjected to burring. The connection plate 150 corresponds to the "connection member" in this embodiment.

In this embodiment, the overall plate thickness of the connection plate 150 is smaller than the plate thickness of the surrounding coolant supply pipe 11 and the like. As a result, the connection plate 150 is a portion that breaks before the internal member 200 when the pressure of the refrigerant rises. Moreover, the connection plate 150 is a portion that is entirely exposed to the atmosphere. That is, in the present embodiment, the connection plate 150 corresponds to the "priority damaged portion". In this manner, even when the connection plate 150, which is a plate-shaped member subjected to burring processing, is used as a connection member and the connection member is used as a preferentially damaged portion, the same effects as those described in the first embodiment can be obtained. play.

A cross section indicated by a dotted line DL5 in FIG. 9 is a plane perpendicular to the flow direction of the coolant and a plane passing through the connection plate 150, which is the preferentially damaged portion. Let Te be the plate thickness of the connection plate 150 at the position of the cross section, De be the equivalent diameter at the position of the cross section, and σe be the tensile strength of the material forming the connection plate 150 . When Te, De, and σe are defined as above, the heat exchanger 10 is configured so as to satisfy the formulas (1) and (2) described above also in this embodiment. It should be noted that the plate thickness does not include the thickness of the preferentially corroded layer SL.

Equation (1) holds regardless of the x-coordinate of dotted line DL5 as long as dotted line DL5 in FIG. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

In this embodiment, the preferential corrosion layer SL is formed so as to cover the surface of the connection plate 150 on the −x direction side, that is, the surface opposite to the plate member 101 . The effect of forming the preferential corrosion layer SL is the same as that described in the first embodiment. The x-direction surface of the connection plate 150 is soldered to the coolant supply pipe 11 , the coolant discharge pipe 12 , and the plate member 101 .

A sixth embodiment will be described with reference to FIG. This embodiment differs from the above-described fifth embodiment only in the aspect of the connecting plate 150 provided as a connecting member. Differences from the fifth embodiment will be mainly described below, and descriptions of common points with the fifth embodiment will be omitted as appropriate.

In FIG. 10, the refrigerant supply pipe 11, the refrigerant discharge pipe 12, and the portions in the vicinity of these in the heat exchanger 10 are cut along the xz plane, and the cross section when viewed from the -y direction side is shown. It is shown.

In this embodiment, each of the burring-processed portion 151 and the burring-processed portion 152 is formed to protrude in the x direction. The coolant supply pipe 11 is inserted from the -x direction side and soldered to the burring processed portion 151 projecting in the x direction side. The tip of the burring portion 151 on the x-direction side is inserted through the inner peripheral surface of the flow path 101A of the plate member 101 and the inner peripheral surface of the tank 210, and is soldered. ing.

Similarly, the refrigerant discharge pipe 12 is inserted from the -x direction side and soldered to the burring processed portion 152 projecting in the x direction side. The tip of the burring portion 152 on the x-direction side is inserted through the inner peripheral surface of the flow path 101B of the plate-like member 101 and the inner peripheral surface of the tank 220, and is soldered. ing.

Also in the present embodiment, the overall plate thickness of the connection plate 150 is smaller than the plate thickness of the surrounding coolant supply pipe 11 and the like. As a result, the connection plate 150 is a portion that breaks before the internal member 200 when the pressure of the refrigerant rises. Also, the connection plate 150 is a portion that is exposed to the atmosphere in its substantially entirety. In other words, the connection plate 150 corresponds to the "priority damaged portion" in this embodiment as well.

A cross section indicated by a dotted line DL6 in FIG. 10 is a plane perpendicular to the flow direction of the coolant and a plane passing through the connection plate 150, which is the preferentially damaged portion. Let Te be the plate thickness of the connection plate 150 at the position of the cross section, De be the equivalent diameter at the position of the cross section, and σe be the tensile strength of the material forming the connection plate 150 . When Te, De, and σe are defined as above, the heat exchanger 10 is configured so as to satisfy the formulas (1) and (2) described above also in this embodiment. It should be noted that the plate thickness does not include the thickness of the preferentially corroded layer SL.

Formula (1) holds regardless of the x-coordinate of dotted line DL6 as long as dotted line DL6 in FIG. The formula (1) holds regardless of the measurement position of the plate thickness of the tank 210, and holds even when Th, Dh, and σh are those of the tank 220 or the tank 230 instead of the tank 210. Similarly, Equation (2) holds regardless of the measurement position of the thickness of the tube 240 or the like.

In this embodiment, the preferential corrosion layer SL is formed so as to cover the surface of the connection plate 150 on the x-direction side, that is, the surface on the plate member 101 side. The effect of forming the preferential corrosion layer SL is the same as that described in the first embodiment. The surface of the connection plate 150 on the −x direction side is soldered to the coolant supply pipe 11 and the coolant discharge pipe 12 . The surface of the connection plate 150 on the x-direction side is soldered to the plate member 101 and the tanks 210 and 220 .

The present embodiment has been described above with reference to specific examples. However, the present disclosure is not limited to these specific examples. Design modifications to these specific examples by those skilled in the art are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each specific example described above and its arrangement, conditions, shape, etc. are not limited to those illustrated and can be changed as appropriate. As long as there is no technical contradiction, the combination of the elements included in the specific examples described above can be changed as appropriate.

10: Heat exchanger 100: Case 11: Refrigerant supply pipe 12: Refrigerant discharge pipe 121: Recess 130A: Thin portion 140: Sealing member 150: Connection plate 200: Internal member

Claims (5)

A heat exchanger (10) for exchanging heat between a refrigerant and cooling water,
an internal member (200) configured to allow the coolant to flow inside;
a case (100) that is a container that houses the internal member inside and that is configured so that the cooling water flows in a space around the internal member;
Said case includes:
a refrigerant supply pipe (11) for supplying the refrigerant to the internal member;
A refrigerant discharge pipe (12) for discharging the refrigerant from the internal member is connected,
Of the portion where the coolant flows, a part of the surface exposed to the outside air has
A preferentially damaged portion (121, 12, 130A, 140, 150) is provided, which is a portion that is damaged before the internal member when the pressure of the refrigerant rises,
The internal member is
tanks (210, 220, 230) in which the refrigerant flows inside along the longitudinal direction;
Tubular members connected to the tank such that their longitudinal direction is perpendicular to the longitudinal direction of the tank, and are stacked in spaced relation to each other along the longitudinal direction of the tank. a plurality of tubes (240), each comprising:
Let the plate thickness of the tank be Th, the equivalent diameter of the tank be Dh, the tensile strength of the material constituting the tank be σh,
Let the plate thickness of the tube be Tt, the equivalent diameter of the tube be Dt, the tensile strength of the material constituting the tube be σt,
When the plate thickness of the preferentially damaged portion is Te, the equivalent diameter of the portion including the preferentially damaged portion is De, and the tensile strength of the material constituting the preferentially damaged portion is σe,
Th·σh/Dh>Te·σe/De, and
A heat exchanger configured to satisfy both Tt·σt/Dt>Te·σe/De . Said case includes:
At least one of the refrigerant supply pipe and the refrigerant discharge pipe is connected via a connection member (130, 150),
2. The heat exchanger according to claim 1 , wherein said preferential failure portion is provided in said connection member. 3. The heat exchanger according to claim 2 , wherein said connection member (150) is a plate-shaped member subjected to burring. 2. The heat exchanger according to claim 1 , wherein said preferentially damaged portion is provided in at least one of said refrigerant supply pipe and said refrigerant discharge pipe. The preferential damaged part or its surrounding part,
5. A heat exchanger according to any preceding claim, covered by a preferentially corroding layer (SL) formed by a preferentially corroding material.

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