JP7444656B2 - refrigerant flow divider - Google Patents

Description

The present invention relates to a refrigerant flow divider that divides inflow refrigerant into a plurality of channels.

Conventionally, a heat exchanger used as a refrigerant evaporator in a refrigeration cycle, for example, may include a plurality of heat transfer tubes. In this case, a refrigerant flow divider may be used to divide the refrigerant flowing from the inflow pipe to each heat transfer tube (for example, see Patent Document 1).

The refrigerant flow divider of Patent Document 1 includes a first body in which a refrigerant supply path and a throttle portion are formed, and a second body in which a refrigerant flow collision portion and first and second flow dividers are formed. They are constructed by fitting them together and integrating them. The constricted portion is formed by reducing the flow path diameter at the downstream end of the refrigerant supply path via the tapered surface. On the other hand, the refrigerant flow collision part of the second vessel is disposed so as to face the downstream end opening of the refrigerant supply path, and has a hemispherical concave surface. The first and second branch channels are open to the outside of the refrigerant flow collision section. The refrigerant flowing through the refrigerant supply path passes through the throttle section, collides with the refrigerant flow collision section, and then branches into the first and second branch channels.

Japanese Patent Application Publication No. 11-257801

By the way, in the refrigerant flow divider of Patent Document 1, the first and second flow dividers are provided on both the left and right sides of the refrigerant stirring chamber, so in order to ensure a sufficient volume of the refrigerant stirring chamber, the first , the interval between the second branch channels becomes wider. This leads to an increase in the size of the refrigerant flow divider, which in turn causes a deterioration in the layout of the refrigerant flow divider.

The present invention has been made in view of this point, and an object thereof is to suppress the expansion of the size of the refrigerant flow divider and improve the layout of the refrigerant flow divider.

In order to achieve the above object, a first invention provides a refrigerant flow divider that divides refrigerant flowing from a refrigerant supply pipe into first and second refrigerant outlet pipes, a supply path to which the refrigerant supply pipe is connected; a constriction section that extends linearly from the downstream end of the supply path and has a smaller diameter than the supply path; and a refrigerant stirring chamber that communicates with the downstream end of the constriction section and stirs the refrigerant that has flowed from the constriction section. and a refrigerant collision surface that is arranged to face the downstream end of the throttle part at a predetermined distance and collide with the refrigerant flowing out from the throttle part, and an upstream end that opens into the wall surface of the refrigerant stirring chamber. On the other hand, a first branch channel having a downstream end communicating with the first refrigerant outflow pipe, and an upstream end communicating with the wall surface of the refrigerant stirring chamber at a portion of the wall surface of the refrigerant stirring chamber that is remote from the upstream end of the first branch channel. a second branch channel which is open and whose downstream end communicates with the second refrigerant outflow pipe; and a first branch channel into which the upstream end of the first refrigerant outflow pipe, which is formed to have a larger diameter than the first branch channel, is inserted. The refrigerant stirring chamber includes an outflow side piping connection hole and a second outflow side piping connection hole into which the upstream end of the second refrigerant outflow pipe formed to have a larger diameter than the second branch flow path is inserted. The direction of inflow of the refrigerant into the refrigerant stirring chamber is orthogonal to the extension of the axis of the first branch channel, and the direction of inflow of the refrigerant into the refrigerant stirring chamber is orthogonal to the extension of the axis of the second branch channel. The downstream end of the first outflow side piping connection hole and the downstream end of the second outflow side piping connection hole are open to a side surface of the refrigerant flow divider corresponding to one radial side of the refrigerant stirring chamber . It is characterized by the presence of

According to this configuration, the refrigerant flowing through the refrigerant supply pipe flows into the supply path and then into the throttle section. Since the constriction extends linearly, the refrigerant not only flows through the constriction at a high flow rate, but also controls the flow direction when it flows out from the constriction. In particular, by controlling the outflow direction of the refrigerant at a high flow rate, the controllability of the outflow direction becomes better. The refrigerant flowing into the refrigerant stirring chamber from the constriction portion collides with the refrigerant collision surface with force, so that the liquid phase refrigerant and the gas phase refrigerant are well stirred in the refrigerant stirring chamber. After being stirred, the refrigerant in the refrigerant stirring chamber is divided into a first refrigerant outflow pipe and a second refrigerant outflow pipe via the first branching channel and the second branching channel, respectively.

Further, the first outflow side piping connection hole into which the first refrigerant outflow pipe is inserted and the second outflow side piping connection hole into which the second refrigerant outflow pipe is inserted are arranged in the radial direction of the refrigerant stirring chamber with respect to the refrigerant stirring chamber. It opens on the side of the refrigerant flow divider corresponding to one side. Further, the first branch passage communicating with the first outlet pipe connection hole and the second branch passage communicating with the second outlet pipe connection hole are both open to the wall surface of the refrigerant stirring chamber, and the first Since the diameter is smaller than that of the second outflow side piping connection hole, the first branch channel and the second branch channel can be brought closer to each other. This suppresses the dimensional expansion of the refrigerant flow divider in the refrigerant flow direction.

In a second invention, the first outflow side piping connection hole extends in a direction intersecting an extension of the axis of the first branch flow path, and the second outflow side piping connection hole extends in the second branch flow path. It is characterized by extending in a direction intersecting the extension line of the axis of.

According to this configuration, the diameters of the first outflow side piping connection hole and the second outflow side piping connection hole are adjusted to the diameters of the first outflow side piping connection hole and the second outflow side piping connection hole while keeping the first division flow path and the second division flow path close to each other. It can be made larger than the diameter of the tract.

A third aspect of the invention is that an extension of the axis of the first branch channel is located within the opening of the first outflow side piping connection hole, and an extension of the axis of the second branch channel is located within the opening of the first outlet pipe connection hole. It is characterized in that it is located within the opening of the second outflow side piping connection hole.

That is, it is conceivable to form the first branch channel by drilling using a rotary tool or the like. In this case, first, the first outflow side piping connection hole can be formed, and then the first branch flow path can be formed using a rotary tool. At this time, since the extension line of the axis of the first branch flow path is located within the opening of the first outflow side piping connection hole, the rotary tool is connected to the first outflow side piping from the opening of the first outflow side piping connection hole. By inserting it into the hole and proceeding in that state, the first branch channel can be easily formed. Similarly, the second branch channel can also be easily formed.

A fourth invention is characterized in that the first branch channel and the second branch channel are formed in a straight line.

According to this configuration, the first branch channel and the second branch channel can be easily formed using a rotary tool.

A fifth invention is characterized in that the refrigerant collision surface is arranged on an extension of the axis of the throttle part from the downstream end of the throttle part, and has a circular shape.

According to this configuration, the refrigerant flowing out from the throttle part collides with the center of the refrigerant collision surface, so that the flow is less likely to be biased, and the liquid phase refrigerant and the gas phase refrigerant can be stirred well.

A sixth invention is characterized in that the cross section of the refrigerant stirring chamber is circular, and the diameter of the refrigerant stirring chamber is set larger than the diameters of the first branch channel and the second branch channel. .

According to this configuration, a sufficient volume of the refrigerant stirring chamber can be ensured.

A seventh aspect of the invention is that the upstream ends of the first branch channel and the second branch channel are opened between the downstream end of the throttle section and the coolant collision surface on a wall surface of the refrigerant stirring chamber. It is characterized by

An eighth aspect of the present invention is that the upstream ends of the first branch channel and the second branch channel are opened closer to the throttle section than a central portion between the downstream end of the throttle section and the refrigerant collision surface. It is characterized by the fact that

According to this configuration, the upstream ends of the first branch channel and the second branch channel are separated from the refrigerant collision surface, so that the refrigerant that has collided with the refrigerant collision surface and is sufficiently stirred is transferred to the first branch channel and the second branch channel. It can be made to flow into the upstream end of the second branch channel.

According to the present invention, the first outflow side pipe connection hole into which the first refrigerant outflow pipe is inserted and the second outflow side pipe connection hole into which the second refrigerant outflow pipe is inserted are located on one side in the radial direction of the refrigerant stirring chamber. The first and second branch channels, which are open on the corresponding side surfaces and have a smaller diameter than the first and second outlet pipe connection holes, can be brought close to each other and communicated with the refrigerant stirring chamber. It is possible to suppress the size expansion of the refrigerant flow direction of the refrigerant flow divider, and it is possible to improve the layout of the refrigerant flow divider.

FIG. 1 is a circuit configuration diagram of a battery cooling device including a refrigerant flow divider according to an embodiment of the present invention. FIG. 3 is a cross-sectional view of a refrigerant flow divider. It is a sectional view showing the state before fixing a 1st flow divider constituent member to a 2nd flow divider constituent member. It is a top view of a 2nd flow divider component. It is a side view of a 2nd flow divider component. FIG. 3 is a rear view of the second flow divider component. 7 is a sectional view taken along the line VII-VII in FIG. 6. FIG.

Hereinafter, embodiments of the present invention will be described in detail based on the drawings. Note that the following description of preferred embodiments is essentially just an example, and is not intended to limit the present invention, its applications, or its uses.

FIG. 1 is a circuit configuration diagram of a battery cooling device 100 including a refrigerant flow divider 1 according to an embodiment of the present invention. The battery cooling device 100 is, for example, a device for cooling a battery 200 mounted in an electric vehicle, a hybrid vehicle (including a plug-in type), or the like. Although not shown, the battery 200 is for supplying electric power to the motor for driving the automobile. In the case of a hybrid vehicle, the battery 200 can be charged by regenerative control of the driving motor or by driving a generator by the engine. In the case of an electric vehicle and a plug-in type hybrid vehicle, the battery 200 can be charged from a commercial power source (not shown) or by regenerative control of the driving motor. The temperature of the battery 200 increases during charging and discharging. In order to suppress this temperature rise, the battery 200 can be cooled by the battery cooling device 100.

(Configuration of battery cooling device 100)
The battery cooling device 100 includes at least a compressor 101, a condenser 102, a receiver tank 103, a battery cooler expansion valve 104, a battery cooler 105, and an accumulator 106. In this embodiment, the battery cooling device 100 is configured to also perform air conditioning in the vehicle interior, and therefore the battery cooling device 100 includes an evaporator 107 as a cooling heat exchanger that cools air conditioning air, and expansion valve 108.

Compressor 101 is composed of an electric compressor. The high-temperature, high-pressure refrigerant discharged from the compressor 101 flows into the condenser 102 . External air is blown into the capacitor 102 by a fan 102a. The refrigerant that has passed through the condenser 102 flows into the receiver tank 103, and then flows into one or both of the bypass pipe 100a and the battery cooler side pipe 100b.

A battery cooler side gate valve 100c is provided in the battery cooler side piping 100b. This battery cooler side gate valve 100c is a valve for opening and closing the battery cooler side piping 100b. A battery cooler expansion valve 104 is provided downstream of the battery cooler side gate valve 100c in the battery cooler side piping 100b. The refrigerant that has passed through the battery cooler expansion valve 104 is depressurized. A dispersion flow divider 1 according to the present invention is provided downstream of the battery cooler expansion valve 104 in the battery cooler side piping 100b.

The separator flow divider 1 is for dividing the refrigerant flowing from the battery cooler side pipe (refrigerant supply pipe) 100b into the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g. That is, the battery cooler 105 is composed of a heat exchanger (evaporator) that supplies cold heat to the battery 200 to cool the battery 200, but the battery cooler 105 includes a plurality of tubes (not shown). It is provided. A separator flow divider 1 is provided to divide the refrigerant into each tube. In this example, a case will be described in which the refrigerant is divided into two streams, but the refrigerant can also be divided into three or more streams. Further, the separator flow divider 1 may divide the refrigerant equally between the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g, or the amount of the refrigerant diverted to one side may be larger than the amount of diversion to the other side. The flow may be divided as follows.

The battery cooler side pipe 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g may all have the same diameter or may have different diameters. Further, the battery cooler side piping 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g are made of, for example, aluminum alloy piping members. Furthermore, the cross sections of the battery cooler side pipe 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g are approximately circular.

A bypass side gate valve 100d is provided in the bypass pipe 100a. This bypass side gate valve 100d is a valve for opening and closing the bypass piping 100a. Bypass piping 100a is connected to evaporator 107. An air conditioning expansion valve 108 is provided downstream of the bypass side gate valve 100d in the bypass piping 100a. The refrigerant flowing out of the evaporator 107 flows into the accurator 106 and then is sucked into the compressor 101. Note that air conditioning air is blown to the evaporator 107 by a blower 120. After the air-conditioning air is cooled by the evaporator 107, it is supplied to the vehicle interior.

Therefore, by opening and closing the battery cooler side gate valve 100c and the bypass side gate valve 100d, there are modes in which the refrigerant flows only to the battery cooler 105, an operation in which the refrigerant flows only to the evaporator 107, and a mode in which the refrigerant flows only to the battery cooler 105 and the evaporator 107. You can switch to any mode between the two modes.

(Configuration of refrigerant flow divider 1)
As shown in FIGS. 2 and 3, the refrigerant flow divider 1 includes a first flow divider component 10 and a second flow divider component 20, and has four side surfaces, a top surface, and a bottom surface. There is. The first flow divider component 10 and the second flow divider component 20 are made of, for example, an aluminum alloy block material. The first flow divider component 10 includes a base 11 and a protruding cylindrical portion 12 that protrudes from the base 11. The cross-sectional shape of the protruding cylindrical portion 12 is circular. The base 11 and the protruding cylindrical part 12 may be integrally molded, or the base 11 and the protruding cylindrical part 12 may be formed from separate members and then combined to be integrated.

A supply side piping connection hole 11a is formed in the base 11, into which the downstream end of the battery cooler side piping 100b is inserted and connected. The cross-sectional shape of the supply side piping connection hole 11a is circular. The outer peripheral surface of the battery cooler side piping 100b is brazed to the inner peripheral surface of the supply side piping connection hole 11a over the entire circumference.

The base portion 11 is provided with a supply path 11b that communicates with the back side (downstream side in the refrigerant flow direction) of the supply side piping connection hole 11a. The supply side piping connection hole 11 a is open on the upper surface of the base 11 . The cross-sectional shape of the supply passage 11b is circular, which is smaller than the cross-sectional shape of the supply-side piping connection hole 11a. The supply path 11b extends straight, and the axis of the supply path 11b and the axis of the supply side piping connection hole 11a coincide. A step portion 11c is formed at the boundary between the supply path 11b and the supply side piping connection hole 11a. The downstream end of the battery cooler side piping 100b is inserted into the supply side piping connection hole 11a and comes into contact with the stepped portion 11c, thereby setting the insertion depth. The battery cooler side piping 100b is inserted into the supply side piping connection hole 11a and connected to the supply path 11b.

The downstream end of the supply path 11b is configured with a tapered surface 11d. The tapered surface 11d is formed so as to decrease in diameter toward the downstream side in the coolant flow direction. The axis of the tapered surface 11d and the axis of the supply path 11b match.

The first flow divider component 10 is provided with a constricted portion 12a that extends linearly from the downstream end of the supply path 11b and has a diameter smaller than that of the portion of the supply path 11b other than the tapered surface 11d. Specifically, a constricted portion 12a is provided inside the protruding cylindrical portion 12 of the first flow divider component 10. The downstream end of the constricted portion 12a opens at the center of the distal end surface of the protruding cylindrical portion 12. The cross-sectional shape of the constricted portion 12a is circular, and the downstream end of the constricted portion 12a that opens at the distal end surface of the protruding cylindrical portion 12 is also circular. The diameter of the constricted portion 12a is set to be equal from its upstream end to its downstream end. The length of the constricted portion 12a is set longer than the length including the tapered surface 11d of the supply path 11b. As a result, the constricted portion 12a has a shape in which the same inner diameter continues over a predetermined length.

Comparing the length of the constricted portion 12a and the diameter of the constricted portion 12a, the length is longer. The length of the constricted portion 12a can be set to, for example, 7 mm or more, and preferably 10 mm or more. Further, the inner diameter of the constricted portion 12a can be set so that the flow rate of refrigerant per unit area is within a range of 1.0 to 4.0 g/s·mm ² , for example. By setting within this range, the liquid phase refrigerant and the gas phase refrigerant can be mixed well in the refrigerant stirring chamber described later, and pressure loss can be reduced. Note that a part of the constricted portion 12a may be formed inside the base portion 11.

An annular groove 12b is formed on the outer circumferential surface of the protruding cylindrical portion 12. An O-ring 13 as a sealing material made of rubber or the like is fitted into the annular groove 12b.

The second flow divider component 20 has a fitting hole 21 into which the protruding cylindrical portion 12 fits. The fitting hole 21 opens on the upper surface of the second flow divider component 20, and has a circular cross-sectional shape. The length of the fitting hole 21 is set to be approximately equal to the protruding length of the protruding cylindrical portion 12 . Therefore, when the protruding cylindrical portion 12 is inserted into the fitting hole 21 and fitted, the lower surface of the base 11 of the first flow divider component 10 comes into contact with the upper surface of the second flow divider component 20. In this state, the first flow divider component 10 and the second flow divider component 20 can be fastened together with bolts or the like (not shown). FIG. 4 shows a screw hole 20a into which the bolt is screwed. When the protruding cylindrical portion 12 is inserted into the fitting hole 21, the space between the two is sealed by the O-ring 13.

The second flow divider component 20 is provided with a refrigerant stirring chamber 22 on the back side of the fitting hole 21 . The refrigerant stirring chamber 22 communicates with the inner side of the fitting hole 21 . The cross-sectional shape of the refrigerant stirring chamber 22 is a circle smaller than the cross-sectional shape of the fitting hole 21. Therefore, the diameter of the fitting hole 21 is set larger than the diameter of the refrigerant stirring chamber 22, and a stepped portion 20b is formed at the boundary between the fitting hole 21 and the refrigerant stirring chamber 22. The step portion 20b can be configured with a tapered surface. Further, as shown in FIG. 4, since the cross-sectional shape of the refrigerant stirring chamber 22 is smaller than the cross-sectional shape of the fitting hole 21, when forming the refrigerant stirring chamber 22 and the fitting hole 21, for example, a rotary tool is used to form the refrigerant stirring chamber 22 and the fitting hole 21. The refrigerant stirring chamber 22 can be formed first and the fitting hole 21 can be formed later, or the fitting hole 21 can be formed first and the refrigerant stirring chamber 22 can be formed later.

By fixing the first flow divider component 10 to the second flow divider component 20, the downstream end of the throttle section 12a and the refrigerant stirring chamber 22 communicate with each other. The refrigerant stirring chamber 22 forms a space for stirring the refrigerant flowing in from the constricted portion 12a. The length of the refrigerant stirring chamber 22 in the axial direction can be set to be approximately the same as the length of the throttle part 12a, but may be longer or shorter than the length of the throttle part 12a. Specifically, as shown in FIG. 2, the axial length B of the refrigerant stirring chamber 22 can be set to 10 mm or more, preferably 15 mm or more.

The diameter of the refrigerant stirring chamber 22 is set to be sufficiently larger than the diameter of the constricted part 12a, so that a sufficient space can be secured in the refrigerant stirring chamber 22 to stir the refrigerant flowing in from the constricted part 12a. It has become. Since the refrigerant that has flowed in from the throttle portion 12a flows through the battery cooler expansion valve 104, it may become a gas-liquid two-layer refrigerant in which a liquid phase refrigerant and a gas phase refrigerant are mixed. By stirring this gas-liquid two-layer refrigerant in the refrigerant stirring chamber 22, the liquid phase refrigerant and the gas phase refrigerant can be mixed.

The second flow divider component 20 is provided with a refrigerant collision surface 24 against which the refrigerant flowing out from the throttle portion 12a collides. The refrigerant collision surface 24 is arranged to face the downstream end of the constriction portion 12a with a predetermined distance therebetween. The refrigerant collision surface 24 has a circular shape. The refrigerant collision surface 24 is arranged on an extension of the axis of the throttle section 12a from the downstream end of the throttle section 12a. The downstream end of the throttle part 12a is arranged so that an extension of the axis of the throttle part 12a passes through the center of the refrigerant collision surface 24. The refrigerant collision surface 24 may be configured as a flat surface or may be configured as a curved surface. When the refrigerant collision surface 24 is a flat surface, the refrigerant collision surface 24 and the extension line of the axis of the throttle portion 12a are substantially perpendicular to each other.

The second flow divider component 20 is provided with a first flow divider 25 and a second flow divider 26 . The first branch channel 25 and the second branch channel 26 extend linearly. Therefore, the first branch channel 25 and the second branch channel 26 can be formed using a rotary tool such as a drill. The diameter of the refrigerant stirring chamber 22 is set larger than the diameters of the first branch channel 25 and the second branch channel 26. This makes it possible to secure a sufficient volume of the refrigerant stirring chamber 22. Note that the first branch channel 25 and the second branch channel 26 have approximately the same diameter.

Furthermore, the upstream ends of the first branch channel 25 and the second branch channel 26 are each in communication with a portion of the refrigerant stirring chamber 22 that is remote from the refrigerant collision surface 24 . That is, the upstream ends of the first branch channel 25 and the second branch channel 26 open between the downstream end of the throttle section 12 a on the wall surface of the refrigerant stirring chamber 22 and the refrigerant collision surface 24 . More specifically, the upstream ends of the first branch channel 25 and the second branch channel 26 are opened closer to the throttle section 12a than the center between the downstream end of the throttle section 12a and the refrigerant collision surface 24. are doing. Thereby, the refrigerant collision surface 24 and the upstream ends of the first branch channel 25 and the second branch channel 26 can be separated. As shown in FIG. 2, the separation distance A between the refrigerant collision surface 24 and the center portions of the upstream ends of the first branch channel 25 and the second branch channel 26 can be set to 9 mm or more and 13.5 mm or less. Note that the upstream ends of the first branch channel 25 and the second branch channel 26 may be opened at the center between the downstream end of the constriction part 12a and the refrigerant collision surface 24, or the It may be open on the side closer to the collision surface 24.

The upstream ends of the first branch channel 25 and the second branch channel 26 are arranged at intervals on the wall surface of the refrigerant stirring chamber 22 around an extension of the axis of the throttle section 12a. That is, the upstream end of the first branch channel 25 and the upstream end of the second branch channel 26 are arranged at intervals from each other in the circumferential direction of the wall surface of the refrigerant stirring chamber 22, and are spaced apart by a predetermined distance in the circumferential direction. ing. As shown in FIG. 7, the first branch channel 25 and the second branch channel 26 are closest to each other at their upstream ends, and the distance between them becomes longer as they approach their downstream ends. In this way, by bringing the upstream ends of the first branch channel 25 and the second branch channel 26 close to each other, it is possible to downsize the refrigerant diverter 1.

The second flow divider component 20 is formed with a first outflow side pipe connection hole 20c into which the upstream end of the first refrigerant outflow pipe 100f is inserted and connected. The cross-sectional shape of the first outflow side piping connection hole 20c is circular. The axis X1 of the first outflow side piping connection hole 20c and the axis X2 of the first branch flow path 25 are in a positional relationship that intersect with each other. Further, the downstream end of the first branch flow path 25 communicates with a portion of the first outflow side piping connection hole 20c that is radially away from the axis X1. The outer peripheral surface of the first refrigerant outflow pipe 100f is brazed to the inner peripheral surface of the first outflow side pipe connection hole 20c over the entire circumference. Thereby, the downstream end of the first branch flow path 25 and the upstream end of the first refrigerant outflow pipe 100f communicate with each other. The outer diameter of the first refrigerant outflow pipe 100f is set to be larger than that of the first branch flow path 25. In other words, the first refrigerant outflow pipe 100f is a pipe formed to have a larger diameter than the first branch flow path 25.

An extension of the axis X2 of the first branch flow path 25 is located within the downstream end opening of the first outflow side piping connection hole 20c. That is, the first branch channel 25 can be formed by drilling using a rotary tool or the like. In this case, first, the first outflow side piping connection hole 20c can be formed using a rotating tool, and then the first branch flow path 25 can be formed using another rotating tool. The rotary tool that forms the first branch flow path 25 has a smaller diameter than the rotary tool that forms the first outlet pipe connection hole 20c.

When forming the first branch channel 25 with a rotary tool, since the extension line of the axis X2 of the first branch channel 25 is located within the downstream end opening of the first outlet pipe connection hole 20c, the rotary tool is used to form the first branch channel 25. The first branch flow path 25 can be easily formed by inserting into the first outflow side piping connection hole 20c from the downstream end opening of the outflow side piping connection hole 20c and proceeding in that state. In other words, the diameter, position, angle, etc. of the first branch channel 25 are set so that the rotary tool forming the first branch channel 25 does not come into contact with the peripheral edge of the downstream end opening of the first outlet pipe connection hole 20c. There is.

Further, the second flow divider component 20 is formed with a second outflow side pipe connection hole 20d into which the upstream end of the second refrigerant outflow pipe 100g is inserted and connected. The cross-sectional shape of the second outflow side piping connection hole 20d is circular. The axis X3 of the second outflow side piping connection hole 20d and the axis X4 of the second branch flow path 26 are in a positional relationship that intersect with each other. Further, the downstream end of the second branch flow path 26 communicates with a portion of the second outflow side piping connection hole 20d that is radially away from the axis X3. The outer peripheral surface of the second refrigerant outflow pipe 100g is brazed to the inner peripheral surface of the second outflow side pipe connection hole 20d over the entire circumference. Thereby, the downstream end of the second branch flow path 26 and the upstream end of the second refrigerant outflow pipe 100g communicate with each other. The outer diameter of the second refrigerant outflow pipe 100g is set to be larger than that of the second branch flow path 26. In other words, the second refrigerant outflow pipe 100g is a pipe formed to have a larger diameter than the second branch flow path 26.

An extension of the axis X4 of the second branch flow path 26 is located within the downstream end opening of the second outflow side piping connection hole 20d. Thereby, similarly to the case where the first branch channel 25 is formed, the second branch channel 26 can be easily formed.

Further, the axis X1 of the first outflow side piping connection hole 20c and the axis X3 of the second outflow side piping connection hole 20d are parallel to each other and are arranged on the same plane. Furthermore, the axis X2 of the first branch channel 25 and the axis X4 of the second branch channel 26 have a positional relationship that intersects with each other, and are arranged on the same plane. The downstream end opening of the first branch channel 25 and the downstream end opening of the second branch channel 26 are located between the axis X1 of the first outlet pipe connection hole 20c and the axis X3 of the second outlet pipe connection hole 20d. are doing.

The downstream end of the first outflow side piping connection hole 20c and the downstream end of the second outflow side piping connection hole 20d are open to a side surface corresponding to one radial side of the refrigerant stirring chamber 22 in the refrigerant flow divider 1. . That is, in this embodiment, since the cross section of the refrigerant flow divider 1 is rectangular as shown in FIG. 7, it has four side surfaces 1a, 1b, 1c, and 1d. Among the four side surfaces 1a, 1b, 1c, and 1d, the side surface 1a located above FIG. 7 is a side surface corresponding to one side in the radial direction of the refrigerant stirring chamber 22. Note that the side surface 1c is a side surface corresponding to the other radial side of the refrigerant stirring chamber 22.

On the side surface 1a of the refrigerant flow divider 1, a downstream end opening of the first outflow side piping connection hole 20c and a downstream end opening of the second outflow side piping connection hole 20d are formed at intervals from each other. In this way, by opening the downstream end of the first outflow side piping connection hole 20c and the downstream end of the second outflow side piping connection hole 20d on the same side surface 1a, the first refrigerant outflow pipe 100f and the second refrigerant Since the outflow pipe 100g can be assembled to the refrigerant flow divider 1 from the same direction, the assembly work efficiency is improved.

(Operations and effects of embodiments)
Therefore, as shown in FIG. 3, when the gas-liquid two-layer refrigerant flows into the supply path 11b from the battery cooler side piping 100b, the gas-liquid two-layer refrigerant can be caused to flow into the throttle part 12a. Since the constricted part 12a extends linearly and has a predetermined length, the refrigerant not only increases the flow velocity by flowing through the constricted part 12a, but also the outflow direction when flowing out from the constricted part 12a. be controlled. In particular, by controlling the outflow direction of the refrigerant at a high flow rate, the controllability of the outflow direction becomes better. The refrigerant flowing into the refrigerant stirring chamber 22 from the constriction portion 12a collides with the refrigerant collision surface 24 with force, so that the liquid phase refrigerant and the gas phase refrigerant are well stirred in the refrigerant stirring chamber 22. After being stirred, the refrigerant in the refrigerant stirring chamber 22 is uniformly divided into the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g via the first branching channel 25 and the second branching channel 26, respectively.

Furthermore, if the piping located immediately upstream of the refrigerant flow divider 1 is bent, the flow velocity distribution of the refrigerant flowing into the refrigerant flow divider 1 will be biased, but in this embodiment, the constricted portion 12a is straight. Since the refrigerant has a shape, it is possible to reduce the deviation in the flow velocity distribution of the refrigerant while flowing inside the constricted portion 12a. Thereby, regardless of the shape of the pipe located immediately upstream of the refrigerant flow divider 1, the refrigerant flow can be made uniform.

Further, as shown in FIG. 7, the first outflow side piping connection hole 20c and the second outflow side piping connection hole 20d correspond to one side in the radial direction of the refrigerant stirring chamber 22 with respect to the refrigerant stirring chamber 22. It opens on the side surface 1a of the flow divider 1. Further, the first branch passage 25 communicating with the first outlet pipe connection hole 20c and the second branch passage 26 communicating with the second outlet pipe connection hole 20d are both opened in the wall surface of the refrigerant stirring chamber 22. Since the diameter is smaller than that of the first and second outlet pipe connecting holes 20c and 20d, the first branch channel 25 and the second branch channel 26 can be brought close to each other. Thereby, the size expansion of the refrigerant flow divider 1 in the refrigerant flow direction is suppressed.

The embodiments described above are merely illustrative in all respects and should not be interpreted in a limiting manner. Furthermore, all modifications and changes that come within the scope of equivalents of the claims are intended to be within the scope of the present invention. The refrigerant flow divider 1 can be applied not only to the battery cooling device 100 but also to the case where refrigerant is divided into tubes forming a heat exchanger of an air conditioner. Further, the first branch channel 25, the second branch channel 26, the third branch channel 27, and the fourth branch channel 28 can extend in any direction. Moreover, the number of branch channels may be three, or may be five or more.

As explained above, the refrigerant flow divider according to the present invention can be used, for example, in a battery cooling device or an air conditioner.

1 Refrigerant flow divider 10 First flow divider component 11b Supply path 12 Projecting tube portion 12a Throttle portion 20 Second flow divider component 21 Fitting hole 22 Refrigerant stirring chamber 24 Refrigerant collision surface 25 First flow divider 26 Second flow divider 100b Battery cooler side piping (refrigerant supply pipe)
100f First refrigerant outflow pipe 100g Second refrigerant outflow pipe

Claims (8)

A refrigerant flow divider that divides refrigerant flowing from a refrigerant supply pipe into first and second refrigerant outflow pipes,
a supply path to which the refrigerant supply pipe is connected;
a constriction portion extending linearly from a downstream end of the supply path and having a diameter smaller than an inner diameter of the supply path;
a refrigerant stirring chamber that communicates with a downstream end of the throttle section and stirs the refrigerant flowing from the throttle section;
a refrigerant collision surface that is arranged to face the downstream end of the constriction part with a predetermined distance therebetween, and on which the refrigerant flowing out from the constriction part collides;
a first branch channel having an upstream end opening to a wall surface of the refrigerant stirring chamber and a downstream end communicating with the first refrigerant outflow pipe;
A second branch channel whose upstream end opens to the wall surface of the refrigerant stirring chamber at a portion of the wall surface of the refrigerant stirring chamber that is remote from the upstream end of the first branch channel, and whose downstream end communicates with the second refrigerant outflow pipe. and,
a first outflow side pipe connection hole into which an upstream end of the first refrigerant outflow pipe formed to have a larger diameter than the first branch flow path is inserted;
a second outflow side piping connection hole into which an upstream end of the second refrigerant outflow pipe formed to have a larger diameter than the second branch flow path is inserted;
The refrigerant stirring chamber has a substantially cylindrical shape with a diameter larger than the diameter of the constricted portion, the diameter of the first branch path, and the diameter of the second branch path,
The direction in which the refrigerant flows into the refrigerant stirring chamber is perpendicular to the extension line of the axis of the first branch flow path,
The direction in which the refrigerant flows into the refrigerant stirring chamber is perpendicular to the extension line of the axis of the second branch flow path,
The downstream ends of both the first outflow side piping connection hole and the second outflow side piping connection hole are opened in a side wall surface of the refrigerant flow divider corresponding to one radial side of the refrigerant stirring chamber. A refrigerant flow divider featuring: The refrigerant flow divider according to claim 1,
The first outflow side piping connection hole extends in a direction intersecting an extension of the axis of the first branch flow path,
The refrigerant flow divider, wherein the second outlet pipe connection hole extends in a direction intersecting an extension of the axis of the second flow flow path. The refrigerant flow divider according to claim 1 or 2,
An extension of the axis of the first branch flow path is located within the opening of the first outflow side piping connection hole,
A refrigerant flow divider, wherein an extension of the axis of the second flow flow path is located within the opening of the second outlet pipe connection hole. The refrigerant flow divider according to claim 3,
A refrigerant flow divider, wherein the first branch flow path and the second branch flow path are formed in a straight line. The refrigerant flow divider according to any one of claims 1 to 4,
The refrigerant flow divider is characterized in that the refrigerant collision surface is arranged on an extension line of the axis of the throttle part from the downstream end of the throttle part and has a circular shape. The refrigerant flow divider according to any one of claims 1 to 5,
A refrigerant flow divider characterized in that a diameter of the refrigerant stirring chamber is set larger than diameters of the first and second flow paths. The refrigerant flow divider according to any one of claims 1 to 6,
The upstream ends of the first branch channel and the second branch channel are opened between the downstream end of the constriction part and the refrigerant collision surface on the wall surface of the refrigerant stirring chamber. vessel. The refrigerant flow divider according to claim 7,
The upstream ends of the first branch channel and the second branch channel are characterized in that they open closer to the throttle section than the center between the downstream end of the throttle section and the refrigerant collision surface. Refrigerant flow divider.

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