JPH0886591A - Heat exchanger and refrigerant evaporator - Google Patents

Abstract

PURPOSE: To provide an accumulated type refrigerant evaporator capable of enhancing cooling capacity by uniformly distributing liquid refrigerant to each of a plurality of tubes and eliminating variation in temperatures of air blown between the tubes. CONSTITUTION: A refrigerant distributing pipe 5 having a plurality of supply holes 24-27 provided in correspondence with each of tubes 12 is inserted into an interior of an inlet tank 15 in such a manner as to penetrate each of inlet tank portions 13 of an accumulated type refrigerant evaporator. The refrigerant distributing pipe 5 is provided with a partition plate 23 in an interior thereof and with a guiding wall 6 at an outlet side end portion of an inlet pipe 2 so that an annular refrigerant passage consisting of a normal flow refrigerant passage 28, a U-turn flow refrigerant passage 30, a reverse flow refrigerant passage 29 and a U-turn flow refrigerant passage 34 is formed. In the refrigerant distributing pipe 5, height difference of a gas-liquid interface (R) caused by inertia of the liquid refrigerant is alleviated and variation in flow rates of the refrigerant flowing through the supply holes 24-27 into each of the tubes 12 is reduced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant evaporator, a refrigerant condenser, a refrigerant subcooler, a heater core, a radiator, an oil cooler, etc., which can uniformly distribute an inflowing heat medium to a plurality of tubes. The present invention relates to a heat exchanger, in particular, a tube part for joining a pair of molding plates to heat-exchange and evaporate a refrigerant in a gas-liquid two-phase state, and a refrigerant channel in which a tank part is formed at one end of the tube part The present invention relates to a laminated refrigerant evaporator formed by laminating a plurality of tubes.

[0002]

2. Description of the Related Art Conventionally, for example, as shown in FIGS. 15 and 16, a tube portion 101 for evaporating a refrigerant by exchanging heat with air, an inlet tank portion 102 communicating with an inlet end portion of the tube portion 101, And a laminated refrigerant evaporator in which a plurality of refrigerant flow pipes 104 having an outlet tank portion 103 communicating with the outlet end of the tube portion 101 and corrugated fins 105 are alternately laminated (for example, US Pat. No. 3,976, US Pat. No. 3,976). No. 128) 100 is known.

The laminated refrigerant evaporator 100 of this conventional example is
A pipe 107 having a supply hole 106 drilled corresponding to each of the plurality of tube portions 101 is inserted into the inlet tank 108 in a state of penetrating the plurality of inlet tank portions 102, and at the same time, the inlet pipe 109 is inserted into the pipe 107. By directly introducing the refrigerant, the refrigerant is evenly distributed to each of the plurality of tube portions 101. In addition, pipe 1
In the inside of 07, the refrigerant passage 11 in which the gas-liquid two-phase refrigerant flowing from the inlet pipe 109 flows from the inlet side to the inner side
0 is formed. Further, 111 in the drawing is an outlet tank, and 112 is an outlet pipe.

[0004]

However, in the laminated refrigerant evaporator 100 of the conventional example, as shown in FIG. 16, the inertia force of the liquid refrigerant is increased, especially when the circulation amount of the refrigerant in the refrigeration cycle is large. As a result, the gas-liquid interface R between the liquid refrigerant and the gas refrigerant becomes higher on the inner side of the refrigerant passage 110 of the pipe 107 than on the inlet side.

Therefore, the liquid refrigerant having a large cooling capacity is supplied to the supply hole 1 on the inner side of the supply hole 106 on the inlet side of the pipe 107.
Since 06 will flow out more, pipe 1
Tube part 10 communicating with the supply hole 106 on the inlet side of 07
The flow rate of the refrigerant becomes uneven between the tube portion 101 communicating from 1 to the supply hole 106 on the inner side of the pipe 107.

As a result, heat exchange between the refrigerant and the air is not uniformly performed from the inlet side to the inner side of the plurality of tube portions 101, and the two tubes adjacent to each other across the width direction of the laminated refrigerant evaporator 100. A temperature distribution is created in the air blown out from between the parts 101. That is, there is a problem that the heat exchange efficiency between the refrigerant and the air decreases due to the variation in the temperature of the blown air.

It is an object of the present invention to provide a heat exchanger capable of uniformly distributing a heat medium to each of a plurality of tube portions to improve heat exchange efficiency. It is in. The object of the invention as set forth in claim 7 is to eliminate the adverse effect of the inertial force of the liquid refrigerant, to uniformly distribute the liquid refrigerant to each of the plurality of tube portions, and to control the temperature of the blown air blown out between the plurality of tube portions. It is an object of the present invention to provide a refrigerant evaporator capable of eliminating variations and improving cooling capacity.

[0008]

According to a first aspect of the present invention, a plurality of tube portions arranged in parallel and an inlet end portion of these tube portions are connected, and the inside of the plurality of tube portions is connected. An inlet tank partitioned into a plurality of tank portions that communicate with each other, a first heat medium passage that is inserted into the inlet tank in a state of penetrating the plurality of tank portions, and through which a heat medium flows, and the first heat medium passage. In the extension direction of the inlet tank to communicate with both ends of the heat medium passage and to a second heat medium passage through which the heat medium flows in the opposite direction to the heat medium flowing in the first heat medium passage. A technical means having a partition means for dividing was adopted.

According to a second aspect of the present invention, in addition to the heat exchanger according to the first aspect, one end of the partition means is open and the other end is closed, and each of the plurality of tube portions is provided on the outer circumference. A heat medium distribution pipe having a plurality of supply holes opened corresponding to the first heat medium passage and the second heat medium passage in an extension direction of the inlet tank. It is characterized in that it has a partition part that divides it into.

In addition, the plurality of supply holes are provided with a pipe wall of the heat medium distribution pipe along the first heat medium passage and a pipe wall of the heat medium distribution pipe along the second heat medium passage. It may be formed on both. Further, on one end side of the heat medium distribution pipe,
A guide portion may be provided to introduce the heat medium flowing out from the second heat medium passage into the first heat medium passage.

According to a fifth aspect of the present invention, in addition to the heat exchanger according to the first aspect, the partition means is a partition member having a substantially T-shaped cross section, and the partition member is the partition member. The first heat medium passage and the second heat medium passage are hung down from an upper side portion that closes a part of the inlet end portion of each of the plurality of tube portions and a central portion of the upper side portion, and the internal space of the inlet tank is provided.
It has a partition part for partitioning the heat medium passage and the heat medium passage in the extension direction of the inlet tank.

According to a sixth aspect of the present invention, in addition to the heat exchanger according to the first aspect, the partition means is a partition member having a tubular cross section, and the partition member is the inlet tank. A partition portion that partitions the internal space of the first heat medium passage and the second heat medium passage, and the partition portion is formed in the partition portion and communicates with both ends of the first and second heat medium passages, respectively. And has a third heat medium passage divided in the extension direction of the inlet tank and the first and second heat medium passages.

According to a seventh aspect of the present invention, a plurality of tube portions arranged in parallel and a plurality of tube portions connected to the inlet end portions of the tube portions, the interior of which communicates with each of the plurality of tube portions. An inlet tank divided into a tank portion, and inserted into the inlet tank while penetrating the plurality of tank portions, one end is opened and the other end is closed, and the outer periphery corresponds to each of the plurality of tube portions. And a refrigerant distribution pipe having a plurality of supply holes that are opened, wherein the refrigerant distribution pipe has a first refrigerant passage through which a heat medium flows, and a first refrigerant passage of the first refrigerant passage. A technical means is adopted in which a partition plate is provided which communicates at both ends and divides the inside into a second refrigerant passage through which the refrigerant flows in the opposite direction from the refrigerant flowing inside the first refrigerant passage.

[0014]

According to the first aspect of the invention, the heat medium flowing into the inlet tank is forwardly passed through the first heat medium passage divided by the partition means penetrating the plurality of tank portions. After flowing, it flows in the opposite direction through the second heat medium passage divided by the partition means. In this way, by removing the blockage part from the flow of the heat medium in the inlet tank and circulating the heat medium in the inlet tank, the heat medium flows into the plurality of tube portions corresponding to each of these tank portions from the plurality of tank portions. The flow rate of the heat medium becomes uniform.

According to the second aspect of the invention, the heat medium reaching one end of the heat medium distribution pipe first reaches the other end of the heat medium distribution pipe through the first heat medium passage. The heat medium that has reached the one end of the second heat medium passage from the other end of the heat medium distribution pipe through the second heat medium passage that is partitioned from the first heat medium passage by the partition portion is again the first heat medium passage. Flows into the heat medium passage. In this way, by removing the blockage portion from the flow of the heat medium in the heat medium distribution pipe and circulating the heat medium in the heat medium distribution pipe, these are supplied from a plurality of supply holes formed on the outer periphery of the heat medium distribution pipe. The flow rate of the heat medium flowing into the plurality of tube portions corresponding to each of the holes becomes uniform.

According to the fifth aspect of the present invention, the heat medium flowing into the inlet tank flows in the forward direction through the first heat medium passage of the partition member having a substantially T-shaped cross section. After that, the second partition which is separated from the first heat medium passage by the partition section
Flows in the opposite direction through the heat carrier passages of the. In this way, by removing the blockage part from the flow of the heat medium in the inlet tank and circulating the heat medium in the inlet tank, the heat medium flows into the plurality of tube portions corresponding to each of these tank portions from the plurality of tank portions. The flow rate of the heat medium becomes uniform. Then, by closing a part of the inlet end of each of the plurality of tube portions by the upper side of the partition member, the opening area of each inlet end of the plurality of tube portions is reduced, and the uniform distribution performance of the heat medium is achieved. Increase.

According to the sixth aspect of the present invention, the heat medium flowing into the inlet tank passes through the first heat medium passage and the third heat medium passage of the partition member having a cylindrical cross section. After flowing in the forward direction, it flows in the opposite direction through the second heat medium passage or the third heat medium passage that is partitioned from the first and third heat medium passages by the partition portion. In this way, by removing the blockage part from the flow of the heat medium in the inlet tank and circulating the heat medium in the inlet tank, the heat medium flows into the plurality of tube portions corresponding to each of these tank portions from the plurality of tank portions. The flow rate of the heat medium becomes uniform.

According to the invention described in claim 7, the refrigerant having reached one end of the refrigerant distribution pipe first reaches the other end of the refrigerant distribution pipe through the first refrigerant passage. Then, the refrigerant that has reached the one end of the second refrigerant passage from the other end of the refrigerant distribution pipe through the second refrigerant passage again flows into the first refrigerant passage. In this way, by circulating the refrigerant in the refrigerant distribution pipe by removing the blocked portion from the flow of the refrigerant in the refrigerant distribution pipe,
From the plurality of supply holes formed on the outer circumference of the refrigerant distribution pipe, the flow rate of the refrigerant flowing into the plurality of tube portions corresponding to each of the supply holes becomes uniform. Therefore, even if the refrigerant in the gas-liquid two-phase state flows into the refrigerant distribution pipe, by flowing the refrigerant in the gas-liquid two-phase state so as to circulate in the refrigerant distribution pipe,
The height difference of the gas-liquid interface due to the inertial force of the liquid refrigerant is mitigated, and variations in the flow rate of the liquid refrigerant from the plurality of supply holes are suppressed.

[0019]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a heat exchanger of the present invention will be described based on an embodiment in which it is applied to a laminated refrigerant evaporator of an air conditioner for a vehicle.

[Structure of First Embodiment] FIGS. 1 to 4 show a first embodiment of the present invention, and FIG. 1 is a view showing the entire structure of a laminated refrigerant evaporator.

The laminated refrigerant evaporator 1 is housed in a duct (not shown) of an air conditioner for a vehicle, and has a gas-liquid two-phase state refrigerant (gas-liquid mixed refrigerant) and a blower (not shown). Is a laminated heat exchanger in which the refrigerant in a gas-liquid two-phase state is used as a gas refrigerant (vaporized refrigerant) by exchanging heat with the air sent by (1). In addition, the laminated refrigerant evaporator 1 is
A refrigeration cycle (all not shown) is configured with the refrigerant compressor, the refrigerant condenser, the pressure reducing means, the gas-liquid separating means, the refrigerant pipe, and the like.

This laminated refrigerant evaporator 1 has an inlet pipe 2,
It is composed of an outlet pipe 3, a heat exchanger body 4, a refrigerant distribution pipe 5, and the like. An inlet end of the inlet pipe 2 is connected to an outlet of an expansion valve forming a pressure reducing means, an outlet end thereof is connected to an inlet end of a refrigerant distribution pipe 5, and a refrigerant in a gas-liquid two-phase state flows inside. In this example, the refrigerant guide wall 6 to be described later is assembled to the inner passage wall at the outlet end of the inlet pipe 2 by using a joining means such as brazing. Also, the outlet pipe 3
Is assembled to the upper end of the heat exchanger body 4 using a joining means such as brazing, and returns the gas refrigerant flowing out from the heat exchanger body 4 to the suction port of the refrigerant compressor.

The heat exchanger body 4 comprises a pair of molding plates 7
And a plurality of corrugated fins 9 arranged between two adjacent refrigerant flow passages 8 are alternately laminated and integrally brazed and assembled in a furnace. ing. The molding plate 7 is formed in a shallow dish shape by pressing a clad material in which a brazing material is applied to both surfaces of a metal plate such as a thin plate-shaped aluminum alloy. The side plates 10 that reinforce the heat exchanger body 4 are attached to the outer sides of the outermost corrugated fins 9 by using joining means such as brazing. A circular through hole 11 into which the refrigerant distribution pipe 5 is inserted is formed at the lower end of the side plate 10 on the inlet side. The lower end of the side plate 10 on the outlet side is
The position corresponding to the refrigerant distribution pipe 5 is closed.

The refrigerant flow pipes 8 are arranged in a plurality of rows in the stacking direction (horizontal direction) of the heat exchanger body 4. Then, the refrigerant flow tube 8 has a flat tube portion 12 for exchanging heat between the refrigerant and air, and a cup-shaped inlet tank portion 13 communicating with an inlet end portion (lower end portion in the vertical direction) of the tube portion 12. , And a cup-shaped outlet tank portion 14 that communicates with the outlet end portion of the tube portion 12 (upper end portion in the vertical direction).
Further, the inlet tank 15 is composed of the plurality of inlet tank portions 13 arranged in the stacking direction, and the outlet tank 16 is composed of the plurality of outlet tank portions 14 arranged in the stacking direction.

Each of the plurality of inlet tank portions 13 and the plurality of outlet tank portions 14 is a tube portion 1 respectively.
Every two communicate. Further, the inlet tank portion 13 has a partition wall 17 that partitions the adjacent inlet tank portion 13, and the partition wall 17 is composed of two molding plates 7. A circular through hole 18 into which the refrigerant distribution pipe 5 is inserted is formed in the partition wall 17. In addition,
Through hole 18 in the inlet tank portion 13 of the forming plate 7 on the back side
Is closed by a flat plate portion 19 at the lower end of the side plate 10 on the back side.

The refrigerant distribution pipe 5 is a partition means of the present invention, and is a heat medium distribution pipe composed of a pipe 21, a cap 22, a partition plate 23 and the like. The pipe 21 is formed into a cylindrical shape by bending a clad material in which a brazing material is applied to both surfaces of a thin plate-shaped metal plate such as an aluminum alloy. In this pipe 21, the inlet pipe 2 is connected to the opening portion on the inlet side using a joining means such as brazing, and the cap 22 is connected to the opening portion on the inner side using a joining means such as brazing.

On the outer periphery of the pipe 21, a plurality of circular supply holes 24, 25 for distributing the refrigerant are formed for each of the tube portions 12. These supply holes 2
Nos. 4 and 25 are opened for each of the plurality of inlet tank parts 13, and are perforated in the pipe walls on both sides of the pipe 21 so that the hole diameter and the hole shape are all the same. In addition, a plurality of supply holes 2
Nos. 4 and 25 are formed at positions that are ½ of the total height of the pipe 21 in the cylinder direction and the front-rear direction (horizontal direction). If the plurality of supply holes 24 and 25 have the same hole diameter, hole shape, and height, the height can be freely changed at any position of the entire height of the pipe 21.

The cap 22 is formed into a substantially hemispherical shape by pressing a thin plate-shaped metal plate such as an aluminum alloy, and is a closing means for closing an opening portion on the back side of the pipe 21. Similarly, circular supply holes 26 and 27 for distributing the refrigerant are formed only in the tube portion 12 on the innermost side. The apex of the cap 22 may or may not be joined to the flat plate portion 19 of the back side plate 10.
Further, although the apex of the cap 22 is in contact with the flat plate portion 19 of the rear side plate 10 in this example, it may be separated from the rear side plate 10.

The partition plate 23 is a partition portion of the present invention, and is formed in a flat plate shape by a thin plate-like metal plate such as aluminum alloy. This partition plate 23 is a pipe 21.
Positioned by being inserted into one or two fitting grooves (not shown) formed on the inner circumference of the pipe 2
It is assembled in the unit 1 by using a joining means such as brazing. The partition plate 23 divides the internal space of the refrigerant distribution pipe 5 formed by the pipe 21 and the cap 22 into two parts to form a forward refrigerant passage 28 and a backward refrigerant passage 29.

The forward direction refrigerant passage 28 is the first heat medium passage and the first refrigerant passage of the present invention, and is one side of the partition plate 23 and the refrigerant distribution pipe 5 in the horizontal direction (for example, a laminated refrigerant evaporator). 1 is formed between the upstream side and the front side in the flow direction of air, and the refrigerant in the gas-liquid two-phase state flows through the inside from the inlet side of the refrigerant distribution pipe 5 to the inner side (forward direction). The reverse direction refrigerant passage 29 is the second heat medium passage and the second refrigerant passage of the present invention, and is the other side of the partition plate 23 and the refrigerant distribution pipe 5 in the horizontal direction (for example, the air of the laminated refrigerant evaporator 1). Between the downstream side and the rear side in the flow direction of the refrigerant, the refrigerant in the gas-liquid two-phase state flows through the inside from the inner side of the refrigerant distribution pipe 5 toward the inlet side (reverse direction). The outlet of the forward coolant passage 28 and the inlet of the reverse coolant passage 29 are formed between the inner periphery of the cap 22 and the end of the partition plate 23 on the inner side of the U-turn coolant passage 3.
It communicates through 0.

The refrigerant guide wall 6 is a guide portion of the present invention, and is a portion that acts like a jet pump, an injector, etc., and the pressure at the outlet of the reverse direction refrigerant passage 29 is determined from the pressure at the inlet of the forward direction refrigerant passage 28. Also, the reverse direction refrigerant passage 29
It works so that the refrigerant therein flows into the forward direction refrigerant passage 28. The refrigerant guide wall 6 includes a throttle portion 31 that narrows the passage at the outlet side end portion of the inlet pipe 2, an arcuate recess 32 formed on the outlet side of the backward refrigerant passage 29, and an outlet side end portion of the inlet pipe 2. The other side of the horizontal direction (for example, the laminated refrigerant evaporator 1
It is composed of an arc-shaped joint portion 33 and the like joined to the downstream side and the rear side in the air flow direction.

A U-turn refrigerant passage 34 that connects the inlet of the forward refrigerant passage 28 and the outlet of the backward refrigerant passage 29 is formed between the wall surface of the recess 32 and the inlet end of the partition plate 23. ing. The inside of the refrigerant guide wall 6 may be hollow. Further, the U-turn refrigerant passage 34 functions as a merging portion that joins the refrigerant from the outlet of the reverse refrigerant passage 29 to the inlet of the forward refrigerant passage 28.

[Operation of First Embodiment] Next, the operation of the laminated refrigerant evaporator 1 of this embodiment will be briefly described with reference to FIGS. 1 to 4.

The gas-liquid two-phase refrigerant flowing from the expansion valve into the inlet pipe 2 is further atomized when passing through the throttle portion 31 of the refrigerant guide wall 6 at the outlet side end of the inlet pipe 2. Is guided along the inclined wall of the narrowed portion 31 into the forward refrigerant passage 28 formed between the pipe wall on one side of the pipe 21 of the refrigerant distribution pipe 5 and the one end surface of the partition plate 23.

The refrigerant in the gas-liquid two-phase state introduced into the forward direction refrigerant passage 28 is supplied from the plurality of supply holes 24 formed in the pipe wall on one side of the pipe 21 to the plurality of inlet tanks of the inlet tank 15. It flows into the part 13. The gas-liquid two-phase refrigerant that has not flowed out of these supply holes 24 flows into the U-turn refrigerant passage 30 in the cap 22 from the tip of the pipe 21, and the two refrigerants formed on the pipe wall of the cap 22 are introduced. It flows out from the supply holes 26 and 27 into the innermost inlet tank portion 13 of the inlet tank 15.

The gas-liquid two-phase refrigerant that has not flown out from the two supply holes 26 and 27 is between the cap 22 and the other side wall of the pipe 21 of the refrigerant distribution pipe 5 and the other end surface of the partition plate 23. Flows into the reverse direction refrigerant passage 29 formed in.
The gas-liquid two-phase state refrigerant that has flowed into the reverse direction refrigerant passage 29 flows out into the plurality of inlet tank portions 13 of the inlet tank 15 through the plurality of supply holes 25 formed in the pipe wall on the other side of the pipe 21. . The gas-liquid two-phase refrigerant that has not flowed out of these supply holes 25 is formed between the inlet end of the partition plate 23 and the wall surface of the recess 32 of the refrigerant guide wall 6 at the inlet end of the pipe 21. After passing through the U-turn refrigerant passage 34, the refrigerant flows again into the forward refrigerant passage 28.

Therefore, the partition plate 2 is provided in the refrigerant distribution pipe 5.
3 and the refrigerant guide wall 6 is provided at the end portion on the inlet side of the inlet pipe 2, so that the forward refrigerant passage 28 is provided in the refrigerant distribution pipe 5.
An annular refrigerant passage is formed which includes the U-turn refrigerant passage 30, the reverse refrigerant passage 29, the U-turn refrigerant passage 34, and the forward refrigerant passage 28. As a result, it is possible to eliminate a blocking portion of the flow of the refrigerant at the rear end portion (tip portion) of the refrigerant distribution pipe 5, so that the height difference of the gas-liquid interface R due to the inertial force of the liquid refrigerant is mitigated and the refrigerant distribution The height of the gas-liquid interface R in the pipe 5 is kept constant from the inlet side to the inner side of the refrigerant distribution pipe 5.

On the other hand, the supply holes 24 to 27 of the refrigerant distribution pipe 5
The refrigerant in the gas-liquid two-phase state that has flowed into the plurality of inlet tank portions 13 of the inlet tank 15 from each inlet tank portion 13 is partitioned by the partition wall 17,
Flows into each tube portion 12 communicating with the. The refrigerant in the gas-liquid two-phase state that has flowed into each tube portion 12 exchanges heat with the air passing outside while passing through each tube portion 12, and evaporates and vaporizes. Then, the gas refrigerant evaporated in each tube portion 12 is supplied to the plurality of outlet tank portions 14 of the outlet tank 16.
It flows in and is collected, and is sucked into the suction port of the refrigerant compressor through the outlet pipe 3.

[Effects of First Embodiment] As described above, in the laminated refrigerant evaporator 1, the partition plate 23 is provided in the refrigerant distribution pipe 5, and the refrigerant guide wall 6 is provided at the inlet side end of the inlet pipe 2. By providing the refrigerant distribution pipe 5, it is possible to eliminate a blocking portion of the flow of the refrigerant at the rear end portion (tip portion) of the refrigerant distribution pipe 5, so that the influence of the inertial force of the liquid refrigerant can be suppressed. As a result, the height of the gas-liquid interface R in the refrigerant distribution pipe 5 can be kept constant from the inlet side to the back side of the refrigerant distribution pipe 5, so that the refrigerant distribution pipe 5
The flow rate of the liquid refrigerant passing through each of the supply holes 24 to 27 formed in the tube wall becomes uniform.

Therefore, the liquid refrigerant having a large cooling capacity is supplied from each of the supply holes 24 to 27 of the refrigerant distribution pipe 5 to each of the inlet tank portions 1.
Since it is uniformly distributed in the heat exchanger main body 4, the flow rate of the liquid refrigerant flowing in all the tube portions 12 in the width direction of the heat exchanger body 4 becomes uniform. As a result, the refrigerant flowing in all the tube portions 12 arranged in the width direction uniformly exchanges heat with the air, and the air blown out from the heat exchanger body 4 (air after heat exchange with the refrigerant). The temperature distribution of can be eliminated. That is, it is possible to prevent variations in the temperature of the blown air, so that it is possible to prevent a decrease in heat exchange efficiency between the refrigerant and the air, and thus it is possible to prevent a decrease in the cooling capacity of the laminated refrigerant evaporator 1.

[Second Embodiment] FIGS. 5 to 7 show a second embodiment of the present invention. FIG. 5 is a view showing a laminated refrigerant evaporator, and FIGS. It is the figure which showed the principal part of a refrigerant evaporator.

In this embodiment, the refrigerant distribution pipe 5 in which the inlet pipe 2 is integrally formed is adopted. Even in this case, after the refrigerant guide wall 6 and the partition plate 23 are inserted into the pipe 21 from the rear end of the pipe 21 of the refrigerant distribution pipe 5, the opening portion of the rear end of the pipe 21 is opened by the cap 22. It should be blocked. Alternatively, after the refrigerant guide wall 6 and the partition plate 23 are attached to a flat metal plate, the metal plate may be bent to form the refrigerant distribution pipe 5 of this example.

[Structure of Third Embodiment] FIGS. 8 to 11 show a third embodiment of the present invention, FIG. 8 shows a laminated refrigerant evaporator, and FIGS. 9 and 10 show the same. It is the figure which showed the principal part of the lamination type refrigerant evaporator.

Around the inlet tank portion 13 of the pair of molding plates 7 forming the refrigerant flow pipe 8 of the laminated refrigerant evaporator 1 of this embodiment, an outward burring portion projecting outward in a flange shape. 39 is integrally molded. A partition member 40 is inserted into the inlet tank 15 connected to the inlet pipe 2 of the laminated refrigerant evaporator 1 so as to penetrate the plurality of inlet tank portions 13.

The partitioning member 40 is a partitioning means of the present invention, and is formed by extruding a metal material made of aluminum alloy so as to have a substantially T-shaped cross section. An arc-shaped upper side portion 41 that closes a part of each inlet end of the portion 12, and a flat plate-shaped partition wall 42 that hangs from the central portion of the upper side portion 41.
have.

Between the upper side portion 41 and the inlet tank 15,
A plurality of supply holes 43a and 43b are formed. The partition wall 42 is a partition portion that partitions the internal space of the inlet tank 15 into a forward refrigerant passage 44 and a backward refrigerant passage 45, and separates the forward refrigerant passage 44 and the backward refrigerant passage 45 from the inlet tank 1.
It is divided in the extension direction of 5. The supply hole 43a communicates with the forward coolant passage 44, and the supply hole 43b communicates with the reverse coolant passage 45. The forward refrigerant passage 44 is a first heat medium passage (first refrigerant passage), and the reverse refrigerant passage 45 is a second heat medium passage (second refrigerant passage).

The outlet of the forward coolant passage 44 and the inlet of the reverse coolant passage 45 are communicated between the rear end of the inlet tank 15 and the rear end of the partition wall 42 of the partition member 40. A U-turn refrigerant passage 46 is formed. Further, between the inlet side end of the inlet tank 15 and the inlet side end of the partition wall 42 of the partition member 40, the reverse direction refrigerant passage 4 is provided.
U for communicating the outlet of No. 5 with the inlet of the forward coolant passage 44
A turn refrigerant passage 47 is formed. The U-turn refrigerant passage 47 functions as a merging portion that joins the refrigerant from the outlet of the backward refrigerant passage 45 to the inlet of the forward refrigerant passage 44.

A refrigerant guide wall 6 having the same shape as that of the first embodiment is attached to the inner passage wall at the outlet end of the inlet pipe 2 by using a joining means such as brazing. This refrigerant guide wall 6 is provided from the outlet end of the inlet pipe 2 to the inlet tank 1
There is an inclined wall (throttle portion) 49 that guides the refrigerant so that the refrigerant flowing into the inside of the refrigerant 5 is more likely to be biased toward the forward refrigerant passage 44 side than the backward refrigerant passage 45. Instead of the coolant guide wall 6, a guide portion such as a coolant guide plate having a hollow inside of the coolant guide wall 6 may be provided.

[Effects of Third Embodiment] FIG. 11 is a view showing the gas-liquid interface R of the refrigerant in the gas-liquid two-phase state in the inlet tank 15 of the laminated refrigerant evaporator 1.

As described above, in the laminated refrigerant evaporator 1 of this embodiment, the partition member 40 is inserted into the inlet tank 15 so that the refrigerant flow in the inlet tank 15 does not have a blockage portion, and the inlet tank 15 can be removed. By circulating the refrigerant in the inside, as shown in FIG. 11, since the height of the gas-liquid interface R in the inlet tank 15 can be made uniform, the liquid refrigerant supplied into each tube portion 12 The flow rate can be made uniform. Therefore, it is possible to make the temperature of the air coming out between the corrugated fins 9 uniform and improve the refrigerating capacity of the laminated refrigerant evaporator 1.

Further, in the laminated refrigerant evaporator 1 of this embodiment, as in the first embodiment, the number of the supply holes 24 to 27 which are 1 to 2 times the number of the tube portions 12 are formed in the refrigerant distribution pipe. Instead, by closing a part of the inlet end of the tube portion 12 with the upper side portion 41 of the partition member 40, the opening area of the inlet side end of the tube portion 12 is reduced. As a result, it is possible to reduce the imbalance in the flow rate of the liquid refrigerant due to the pressure difference in each inlet tank portion 13 of the inlet tank 15, and thus to improve the uniform distribution performance of the liquid refrigerant supplied into each tube portion 12. be able to.

At the time of stacking the refrigerant flow path pipes 8 composed of a pair of molding plates 7, the partition member 40 is inserted into the inlet tank 15 so as to pass through the plurality of inlet tank portions 13 to thereby form the plurality of molding plates 7. Mutual positioning is possible. That is, the brazing surface 35 (see FIG. 10) of the forming plate 7 is not displaced so much that it is displaced. Therefore, conventionally, it is possible to omit the caulking process for positioning the inlet tank portions of the adjacent molding plates.

[Fourth Embodiment] FIGS. 12 to 14 show a fourth embodiment of the present invention. FIG. 12 is a view showing a laminated refrigerant evaporator, and FIGS. It is the figure which showed the principal part of a refrigerant evaporator.

As in the third embodiment, an outward burring portion 39 is provided around the inlet tank portion 13 of the pair of molding plates 7 constituting the refrigerant flow pipe 8 of the laminated refrigerant evaporator 1 of this embodiment. It is integrally molded. A partition member 50 is inserted into the inlet tank 15 connected to the inlet pipe 2 of the laminated refrigerant evaporator 1 so as to penetrate the plurality of inlet tank portions 13.

The partition member 50 is a partitioning means of the present invention, and is formed by extruding a metal material made of an aluminum alloy so as to have a substantially trapezoidal tubular cross section. An arc-shaped ceiling wall portion 51 that closes a part of each inlet end of the portion 12, and a V-shaped partition wall 5 extended from both side portions of the ceiling wall portion 51.
Have two.

Between the ceiling wall portion 51 and the inlet tank 15,
A plurality of supply holes 53a and 53b are formed. The partition wall 52 is a partition part that partitions the internal space of the inlet tank 15 into the forward refrigerant passages 54 and 55 and the backward refrigerant passage 56. The supply hole 53a communicates with the forward coolant passage 54, and the supply hole 53b communicates with the reverse coolant passage 56. The forward coolant passage 54 is a first heat medium passage (first coolant passage), the reverse coolant passage 56 is a second heat medium passage (second coolant passage), and the forward coolant passage 55 is Third
Of the heat medium passage.

Between the rear end of the inlet tank 15 and the rear end of the partition wall 52 of the partition member 50, the outlets of the forward coolant passages 54 and 55 and the inlet of the reverse coolant passage 56 are provided. A U-turn refrigerant passage 57 is formed to communicate with each other. Further, the end portion of the inlet tank 15 on the inlet side and the partition member 5
A U-turn refrigerant passage 58 that connects the outlet of the backward refrigerant passage 56 and the inlets of the forward refrigerant passages 54 and 55 is formed between the end of the partition wall 52 of 0 and the inlet side.

A refrigerant guide wall 6 having the same shape as that of the third embodiment is attached to the inner passage wall at the outlet end of the inlet pipe 2 by using a joining means such as brazing. This refrigerant guide wall 6 is provided from the outlet end of the inlet pipe 2 to the inlet tank 1
There is an inclined wall (throttle portion) 59 that guides the refrigerant so that the refrigerant flowing into the inside of the refrigerant 5 is more likely to be biased toward the forward refrigerant passages 54, 55 than the backward refrigerant passage 56.

In the laminated refrigerant evaporator 1 of this embodiment, the partition member 50 is inserted into the inlet tank 15 to eliminate the blocking portion from the refrigerant flow in the inlet tank 15.
By circulating the refrigerant in the inlet tank 15, the same effect as the third embodiment can be achieved. Also,
In addition to the forward coolant passage 54 and the reverse coolant passage 56, by providing a forward coolant passage 55 that does not communicate with each tube portion 12 in the partition member 50, the forward coolant passage 55 from the outlet side end of the inlet pipe 2 is provided. It is possible to directly guide the refrigerant to the reverse direction refrigerant passage 56 via. Therefore, the liquid refrigerant flows into the tube portions 12 substantially evenly through the supply holes 53a and 53b that communicate with the forward refrigerant passage 54 and the backward refrigerant passage 56, respectively.

[Modification] Although the present invention is applied to the laminated refrigerant evaporator 1 in this embodiment, the present invention is applied to another heat exchanger such as a refrigerant condenser, a heater core, a radiator or an oil cooler. Is also good. Further, the present invention may be applied not only to the laminated heat exchanger as in this embodiment, but also to a corrugated fin tube heat exchanger and a plate fin tube heat exchanger.

In this embodiment, the pipe 2 of the refrigerant distribution pipe 5 is
Although the opening portion at the rear end portion of 1 is closed by the cap 22, the opening portion at the rear end portion of the pipe 21 of the refrigerant distribution pipe 5 may be closed by the side wall (partition wall 17) of the inlet tank portion 13. . Further, the opening portion at the rear end of the pipe 21 of the refrigerant distribution pipe 5 may be closed by the flat plate portion 19 of the side plate 10.

In this embodiment, the pipe 2 of the refrigerant distribution pipe 5 is
1, the cap 22, the partition plate 23, and the refrigerant guide wall 6 are made of a metal such as an aluminum alloy, but they are made of resin or the like, and after being inserted into the inlet tank 15 after integral brazing, the inlet pipe 2 May be assembled by screwing through a sealing material such as an O-ring.

In this embodiment, the partition member 40 having a substantially T-shaped cross section or the partition member 50 having a substantially trapezoidal tubular cross section was inserted into the inlet tank 15 as the partition means. A partition having a V-shaped cross section, a substantially E-shaped cross section, a substantially K-shaped cross section, a substantially M-shaped cross section, a substantially N-shaped cross section, a substantially S-shaped cross section, a substantially mouth-shaped cross section. The member may be inserted into the inlet tank 15.

[0064]

According to the first aspect of the present invention, the heat medium having a uniform flow rate can be distributed from the inlet tank to each of the plurality of tube portions by eliminating the closed portion of the refrigerant flow in the inlet tank. Therefore, heat exchange efficiency can be improved by uniformly exchanging heat in each tube portion.

According to a second aspect of the present invention, the heat medium distribution pipe is eliminated from the closed portion of the flow of the refrigerant, so that the heat medium having a uniform flow rate from each supply hole of the heat medium distribution pipe to each of the plurality of tube portions. The heat exchange efficiency can be improved by uniformly exchanging heat in each tube portion.

According to the fifth aspect of the present invention, by eliminating the closed portion of the flow of the refrigerant in the inlet tank, a uniform flow rate is provided between the inlet tank and the upper side of the partition member to each of the plurality of tube portions. Since the heat medium can be distributed,
The heat exchange efficiency can be improved by uniformly exchanging heat in each tube portion.

According to the sixth aspect of the present invention, by eliminating the closed portion of the flow of the refrigerant in the inlet tank, a uniform flow rate of the heat medium is provided between the inlet tank and the partition member to each of the plurality of tube portions. Since heat can be distributed, heat exchange efficiency can be improved by uniformly performing heat exchange in each tube portion.

According to the seventh aspect of the present invention, the adverse effect of the inertial force of the liquid refrigerant can be eliminated by eliminating the closed portion of the refrigerant flow in the refrigerant distribution pipe. Accordingly, since it is possible to distribute the liquid refrigerant at a uniform flow rate from each supply hole of the refrigerant distribution pipe to each of the plurality of tube portions, the heat exchange between the refrigerant and air is uniformly performed in each tube portion. The cooling capacity can be improved by eliminating the temperature distribution of the air blown out from between the plurality of tube portions.

[Brief description of drawings]

FIG. 1 is a partial sectional view showing a laminated refrigerant evaporator according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG.

3 is a sectional view taken along line BB of FIG.

FIG. 4 is an exploded view showing the pipe of the first embodiment of the present invention.

FIG. 5 is a partial sectional view showing a laminated refrigerant evaporator according to a second embodiment of the present invention.

FIG. 6 is a sectional view taken along the line CC of FIG. 5;

7 is a cross-sectional view taken along the line DD of FIG.

FIG. 8 is a partial sectional view showing a laminated refrigerant evaporator according to a third embodiment of the present invention.

9 is a sectional view taken along line EE of FIGS. 8 and 11. FIG.

10 is a sectional view taken along line FF of FIGS. 8 and 11. FIG.

FIG. 11 is a partial cross-sectional view showing a gas-liquid interface of a refrigerant in a gas-liquid two-phase state in an inlet tank of a laminated refrigerant evaporator according to a third embodiment of the present invention.

FIG. 12 is a partial sectional view showing a laminated refrigerant evaporator according to a fourth embodiment of the present invention.

13 is a sectional view taken along line GG of FIG.

14 is a cross-sectional view taken along line HH of FIG.

FIG. 15 is a partial cross-sectional view showing a conventional laminated refrigerant evaporator.

FIG. 16 is a cross-sectional view showing a conventional pipe.

[Explanation of symbols]

1 Laminated Refrigerant Evaporator (Heat Exchanger) 2 Inlet Pipe 3 Outlet Pipe 4 Heat Exchanger Main Body 5 Refrigerant Distribution Pipe (Partitioning Means, Heat Medium Distribution Pipe) 6 Refrigerant Guide Wall (Guide) 12 Tube 13 Inlet Tank 15 inlet tank 21 pipe 22 cap 23 partition plate 24 supply hole 25 supply hole 26 supply hole 27 supply hole 28 forward coolant passage (first heat medium passage, first coolant passage) 29 reverse coolant passage (second Heat medium passage, second refrigerant passage) 30 U-turn refrigerant passage 31 Throttling portion 34 U-turn refrigerant passage 40 Partition member (partitioning means) 41 Upper side portion 42 Partition wall (partition portion) 44 Forward refrigerant passage (first heat) Medium passage, first refrigerant passage) 45 Reverse refrigerant passage (second heat medium passage, second refrigerant passage) 46 U-turn refrigerant passage 47 U-turn refrigerant passage 49 Inclined wall 50 Partitioning member (partitioning means) 51 Top wall part 52 Partition wall (partitioning part) 54 Forward refrigerant passage (first heat medium passage, first refrigerant passage) 55 Forward refrigerant passage (third heat medium passage) 56 Reverse direction refrigerant passage (second heat medium passage, second refrigerant passage) 57 U-turn refrigerant passage 58 U-turn refrigerant passage 59 Inclined wall

Claims (7)

[Claims] 1. A plurality of tube parts arranged in parallel, and (b) a plurality of tanks connected to the inlet ends of these tube parts, the interior of which communicates with each of the plurality of tube parts. An inlet tank divided into parts, and (c) a first heat medium passage which is inserted into the inlet tank in a state of penetrating the plurality of tank portions and through which a heat medium flows, and the first heat medium passage. Means for communicating with each other at both ends and for dividing the inside into a second heat medium passage in which the heat medium flows in the opposite direction to the heat medium flowing in the first heat medium passage in the extension direction of the inlet tank. And a heat exchanger equipped with. 2. The heat exchanger according to claim 1, wherein the partitioning means has a plurality of supply openings, one end of which is open and the other end of which is closed, and an outer periphery of which is opened corresponding to each of the plurality of tube portions. A heat medium distribution pipe having a hole, wherein the heat medium distribution pipe includes the first heat medium passage and the second heat medium passage.
A heat exchanger having a partition part for partitioning the heat medium passage of the above in the extension direction of the inlet tank. 3. The heat exchanger according to claim 2, wherein the plurality of supply holes are provided in a pipe wall of the heat medium distribution pipe and the second heat medium passage along the first heat medium passage. The heat exchanger is formed on both the pipe wall of the heat medium distribution pipe along the heat exchanger. 4. The heat exchanger according to claim 2, wherein the heat medium distribution pipe has a heat medium flowing out from the second heat medium passage on one end side of the heat medium distribution pipe. A heat exchanger having a guide portion introduced into a passage. 5. The heat exchanger according to claim 1, wherein the partition means is a partition member having a substantially T-shaped cross section, and the partition member is an inlet end of each of the plurality of tube portions. An upper side portion that closes a part of the portion and a central portion of the upper side portion, and extends through the inner space of the inlet tank through the first heat medium passage and the second heat medium passage in the extension direction of the inlet tank. A heat exchanger characterized by having a partition part that divides into. 6. The heat exchanger according to claim 1, wherein the partitioning means is a partitioning member having a tubular cross section, and the partitioning member defines an internal space of the inlet tank with the first heat exchanger. A partition portion that divides the medium passage and the second heat medium passage, and the first and second partition portions formed in the partition portion.
A heat having a third heat medium passage, which communicates with both ends of the second heat medium passage and is divided in the extension direction of the first and second heat medium passages and the inlet tank. Exchanger. 7. A plurality of tube parts arranged in parallel, and an inlet connected to the inlet end parts of these tube parts, the inside being divided into a plurality of tank parts communicating with each of the plurality of tube parts. A tank and a plurality of feeds inserted into the inlet tank in a state of penetrating the plurality of tank portions, having one end opened and the other end closed, and an outer periphery corresponding to each of the plurality of tube portions opened. A refrigerant evaporator comprising a refrigerant distribution pipe having holes, wherein the refrigerant distribution pipe communicates with a first refrigerant passage through which a heat medium flows inside and at both ends of the first refrigerant passage, A refrigerant evaporator is also provided, which is provided with a partition plate that divides the inside into a refrigerant flowing in the first refrigerant passage and a second refrigerant passage in which the refrigerant flows in the opposite direction.