JPH10300270A - Refrigerant evaporator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a refrigerant from excessively flowing into a refrigerant channel pipe which is arranged at the most outlet pipe side. SOLUTION: A refrigerant evaporator is constituted by laminating a tube element 50 and a plurality of tube elements 4. A first refrigerant channel pipe 52 of the tube element 50 is arranged to be the most outlet pipe side in the flow of a refrigerant, and the tube element 50 is arranged at the extreme edge of the refrigerant evaporator. A rib 54 is formed on the outer wall surface of the first refrigerant channel pipe 52, and the first refrigerant channel pipe 52 is divided into a refrigerant thin channels. As a result, the refrigerant channel area of the first refrigerant channel pipe 52 is smaller than the refrigerant channel area of the other refrigerant channel pipes for constituting a downstream, first channel pipe group 31a. The pressure loss of the first refrigerant channel pipe 52 is larger than that of other refrigerant channel pipes, thus preventing the refrigerant from excessively flowing into the first refrigerant channel pipe 52.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant evaporator for evaporating a refrigerant by exchanging heat between air and refrigerant in a gas-liquid two-phase state flowing from a pressure reducing means.

[0002]

2. Description of the Related Art Conventionally, as one of the refrigerant evaporators, which is a component of a refrigeration cycle of an air conditioner for a vehicle, a refrigerant flow path is provided above and below a plurality of refrigerant flow pipes stacked in a width direction. Refrigerant evaporators having an upper tank and a lower tank in communication with a pipe are generally known. As one of such refrigerant evaporators, there is a refrigerant evaporator described in Japanese Patent Application No. 8-182307 filed by the present inventors as shown in FIGS.

The refrigerant evaporator 100 is constructed by alternately stacking refrigerant flow pipes 102 and 103 having the same refrigerant flow area and corrugated fins 104. Upper tanks 105, 10 communicating with the respective refrigerant flow pipes 102, 103 are provided at upper and lower portions of the respective refrigerant flow pipes 102, 103.
6 and lower tanks 107 and 108 are provided,
An inlet pipe 109 is connected to the lower tank 108 on the leeward side, and an outlet pipe 110 is connected to the upper tank 105 on the leeward side. Inlet piping 109
Gas-liquid two-phase refrigerant flowing from the
8 and the outlet pipe 11 through the refrigerant flow pipes 102 and 103.
Flowed out of zero.

The upper (lower) tanks 105, 106
The refrigerant flowing into (107, 108) flows in the upper (lower) tanks 105, 106 (107, 108) in one direction, is distributed to the respective refrigerant flow pipes 102, 103, and passes through the refrigerant evaporator 100. It flows into the lower (upper) tanks 107, 108 (105, 106) while exchanging heat with air.

[0005]

In such a refrigerant evaporator 100, the liquid refrigerant is supplied to the upper tank 105, 1
06 while flowing in one direction.
3 is distributed to the upper tank 10 by its gravity.
Near side of 5, 106 (upstream side of refrigerant flowing in tank)
It is easy to flow down to the refrigerant flow pipes 102 and 103 connected to the pipe, and it is difficult to flow toward the downstream side. on the other hand,
Each refrigerant flow pipe 102, 1
03 flows into the refrigerant evaporation passages 102 and 103 after the refrigerant flows into the inner side of the lower tanks 107 and 108 (downstream of the refrigerant flowing in the tanks). It is easy to flow into the refrigerant flow pipes 102 and 103 connected to the inner side of 107 and 108.

[0006] In particular, in the refrigerant evaporator 100 shown in FIG.
Since the refrigerant flows up through the plurality of refrigerant flow pipes 103 on the 10 side, the outlet pipe 1 of the refrigerant flow pipes 103 is the most outlet pipe.
The refrigerant easily flows into the refrigerant flow pipe 103 on the 10 side, and the refrigerant excessively flows into the refrigerant flow pipe 103 easily. Therefore, the liquid refrigerant does not completely evaporate in the refrigerant flow pipe 103 closest to the outlet pipe 110 among the refrigerant flow pipes 103, and the superheated steam (superheated gas) is reliably formed.
It was not possible. As a result, the refrigerant evaporator 10
The temperature of the refrigerant after passing through the refrigerant evaporator 100 decreases, and the expansion valve (not shown) provided on the upstream side of the refrigerant evaporator 100 performs control to reduce the amount of refrigerant flowing into the refrigerant evaporator 100. The ability could be reduced.

To solve such a problem, for example, the refrigerant flow path closest to the outlet pipe is increased so as to increase the pressure loss (hereinafter, abbreviated as pressure loss) of the refrigerant in the refrigerant flow path pipe closest to the outlet pipe. By changing the shape of the inner fin provided in the pipe, it is possible to prevent the refrigerant from excessively flowing into the refrigerant flow pipe, but the number of parts for forming the refrigerant evaporator increases, and the refrigerant evaporates. This causes a problem that productivity in manufacturing the container is reduced.

Therefore, according to the present invention, in a refrigerant evaporator having an upper tank and a lower tank communicating with a refrigerant flow pipe, the refrigerant which is the most outlet pipe side of the refrigerant flow pipe group without lowering the productivity. It is an object of the present invention to provide a refrigerant evaporator that can prevent the refrigerant from excessively flowing into the flow path pipe.

[0009]

According to the present invention, the refrigerant flow pipe group (31a) is disposed closer to the outlet pipe (16) than substantially half in the flow direction of the refrigerant. The protrusion (5) is provided on the pipe wall surface of the refrigerant flow pipe (52).
4) is formed, and the refrigerant flow path area in the refrigerant flow path pipe (52) in which the protruding portion (54) is formed is the same as that of the other refrigerant flow path pipes (31a) constituting the refrigerant flow path pipe group (31a). ) Is smaller than the area of the refrigerant flow path in the above. Therefore, in the refrigerant flow pipe group (31a), the pressure loss at the time when the refrigerant passes through the refrigerant flow pipe (52) disposed closer to the outlet pipe (16) than substantially half in the flow direction of the refrigerant is: The pressure loss is larger than the pressure loss in the other refrigerant flow pipes (31) constituting the refrigerant flow pipe group (31a). For this reason, in the refrigerant flow pipe group (31a) in which the refrigerant flows upward, the refrigerant flow pipes (31a), which are more likely to flow in the refrigerant and are disposed closer to the outlet pipe (16) than substantially half in the flow direction of the refrigerant. 52) It is possible to prevent the refrigerant from excessively flowing into it. As a result, the refrigerant passing through the refrigerant flow pipe (52) disposed closer to the outlet pipe (16) in the flow direction of the refrigerant than substantially half of the refrigerant flow pipe group (31a) can be reliably turned into superheated steam. it can. In particular, in the present invention, by forming the protruding portion (54) on the pipe wall surface, the refrigerant flow path pipe group (31) is compared with the other refrigerant flow path pipes (31) constituting the refrigerant flow path pipe group (31a). 31a), a special member for increasing the pressure loss because the area of the refrigerant flow path of the refrigerant flow path pipe (52) disposed closer to the outlet pipe (16) than the half in the flow direction of the refrigerant is reduced. There is no need to provide Therefore, the refrigerant does not excessively flow into the refrigerant flow pipe (52) disposed closer to the outlet pipe (16) in the flow direction of the refrigerant than substantially half of the refrigerant flow pipe group (31a) without lowering the productivity. Can be prevented. In addition, since the projecting portion (54) is formed on the pipe wall surface of the coolant channel pipe (52) having a reduced coolant channel area, depending on the appearance,
Other refrigerant flow pipes (3) constituting the refrigerant flow pipe group (31a)
1) can be easily distinguished, and erroneous assembly can be easily prevented.

Further, according to the second aspect of the present invention, in the refrigerant flow pipe group, the protrusion is formed in the refrigerant flow pipe arranged closest to the outlet pipe in the flow direction of the refrigerant. Of the refrigerant flow tube groups, the refrigerant is the easiest to flow,
It is possible to prevent the refrigerant from excessively flowing into the refrigerant flow pipe arranged closest to the outlet pipe in the flow direction of the refrigerant. According to the third aspect of the present invention, among the first refrigerant flow pipe group (31a) disposed on the outlet pipe (16) side, the first refrigerant flow pipe group (31a) is disposed on the outlet pipe (16) side in the flow direction of the refrigerant. Protrusion (5) formed on the pipe wall surface of the first refrigerant flow pipe (52)
According to 4), the refrigerant flow passage area in the first refrigerant flow passage tube (52) is equal to the refrigerant flow passage area in the other first refrigerant flow passage tubes (31) constituting the first refrigerant flow passage tube group (31a). Is smaller than. Therefore, the pressure loss when the refrigerant passes through the first refrigerant flow path pipe (52) disposed closest to the outlet pipe (16) in the flow direction of the refrigerant causes the first refrigerant flow path pipe group (31a) to pass through. It is larger than the pressure loss in the other first refrigerant flow pipe (31) that constitutes the first refrigerant flow pipe (31).
Therefore, the first refrigerant flow pipe group (31) disposed on the outlet pipe (16) side, in which the refrigerant flows upward from below.
In a), it is possible to prevent the refrigerant from excessively flowing into the first refrigerant flow path pipe (52) which is located closest to the outlet pipe (16) in the flow direction of the refrigerant, in which the refrigerant easily flows.
As a result, the refrigerant passing through the first refrigerant flow pipe (52) disposed closest to the outlet pipe (16) can be reliably turned into superheated steam. In particular, in the present invention, the first refrigerant flow is formed by forming the projection (54) on the pipe wall surface of the first refrigerant flow pipe (52) which is arranged closest to the outlet pipe (16) in the flow direction of the refrigerant. The refrigerant flow passage area of the first refrigerant flow passage pipe (52) disposed closest to the outlet pipe (16) is smaller than that of the other first refrigerant flow passage pipes (31) constituting the flow path group (31a). Since the size is reduced, there is no need to provide a special member for increasing the pressure loss. Therefore, the most outlet pipe (16) in the flow direction of the refrigerant without lowering the productivity.
Excessive inflow of the refrigerant into the first refrigerant flow pipe (52) arranged on the side can be prevented.

Further, according to the fourth aspect of the present invention, since the outlet pipe (16) is connected to one end of the first upper tank (34), the outlet pipe (16) having the projection (54) formed on the pipe wall surface is formed. The one refrigerant flow pipe (52) is disposed at the outermost end of the plurality of first refrigerant flow pipes (31, 52) that are stacked. Therefore, the first refrigerant flow pipe (5) in which the protrusion (54) is formed.
After laminating a plurality of first refrigerant flow pipes (31) having a refrigerant flow area larger than 2), a first refrigerant flow pipe (52) having a projecting portion (54) formed on the pipe wall surface is arranged. Thus, the refrigerant evaporator (1) can be assembled, and the assembling step (the first refrigerant flow pipe (31,
52) can be facilitated.
Further, when the first refrigerant flow pipes (31, 52) are laminated,
It is possible to prevent the position of the first refrigerant flow pipe (52) in which the protruding portion (54) is formed from being erroneously arranged, thereby improving the productivity.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described with reference to FIGS. A refrigerant evaporator (hereinafter, abbreviated as a refrigerant evaporator) 1 of a right and left split type is, for example, a laminated heat exchanger that forms an evaporator of a refrigeration cycle of a vehicle air conditioner, and has a refrigerant flowing inside and an air passing outside. Are exchanged with each other to evaporate and evaporate the refrigerant, thereby cooling the air. This refrigerant evaporator 1
Is mounted, for example, in an air conditioning duct (unit case) installed in front of the vehicle cabin so as to be orthogonal to the direction of air flow. And the refrigerant evaporator 1
Is a leeward heat exchange section (heat exchanger body, evaporator body) 2, which is arranged on the leeward side (downstream side, rear side) in the air flow direction,
And a leeward heat exchange part (heat exchanger main body, evaporator main body) 3 disposed adjacent to the leeward side (upstream side, front side) of the air flow direction from the leeward side heat exchange part 2.

Downwind heat exchange section 2 and upwind heat exchange section 3
A plurality of tube elements 4 and a plurality of tube elements 50 stacked in a width direction (horizontal direction) orthogonal to a flow direction of air;
And a plurality of corrugated fins 5 arranged between the tube elements 50 to enhance the heat exchange efficiency (heat transfer efficiency) between the refrigerant and the air, and to reinforce the leeward heat exchange part 2 and the leeward heat exchange part 3. From an end plate 6 and a side plate 7, an accumulator 15a connected to an inlet pipe 15 for allowing the refrigerant to flow into the refrigerant evaporator 1, and an accumulator 16a connected to an outlet pipe 16 for allowing the refrigerant to flow from the refrigerant evaporator 1. And they are brazed together in the furnace.

Next, the tube elements 4 and 50 will be described in detail. A plurality of leeward heat exchange units 2 are laminated.
In addition, the tube element 4 constituting the windward heat exchange part 3 is formed by opposingly joining a pair of molded plates 4a formed by press molding a thin plate-shaped aluminum alloy having excellent thermal conductivity. One of the molding plates 4a has a substantially rectangular joint 11 joined to the other molding plate 4a by brazing, and this joint 1
1 is divided into two I-shaped concave portions 12 and 13
4 and the like are formed.

When the pair of forming plates 4a are joined to each other, the second refrigerant flow pipe 21 is formed by the space between the I-shaped recesses 12 on the leeward side, and the first refrigerant flow pipe 21 is formed by the space between the I-shaped recesses 13 on the windward side. A refrigerant flow tube 31 is formed. The second refrigerant flow pipe 21 is provided on the upstream side of the first refrigerant flow pipe 31 in the flow direction of the refrigerant, and exchanges heat with air mainly in a gas-liquid two-phase refrigerant having a large liquid phase component. And a refrigerant flow pipe for evaporating and evaporating the refrigerant. In addition, the second of the tube element 4
Inner fins 21c as heat transfer promoting portions for distributing the refrigerant widely in the width direction of the second refrigerant flow channel 21 are arranged in the refrigerant flow channel 21.

The first refrigerant flow pipe 31 is connected to the second refrigerant flow pipe 2
A refrigerant flow pipe provided downstream of the refrigerant flow direction 1 in the flow direction of the refrigerant and exchanging heat between air and refrigerant mainly in a gas-liquid two-phase state having a large amount of gas phase components to evaporate the refrigerant. The first refrigerant flow pipe 31 of the tube element 4 contains the first refrigerant.
An inner fin 31c is provided as a heat transfer promoting portion for extending the refrigerant flow pipe 31 widely in the width direction of the passage.

A second upper tank portion 22 is formed above the second refrigerant flow tube 21 (for example, in the top direction), and a second lower tank portion is formed below the second refrigerant flow tube 21 (for example, in the ground direction). 23 are formed. The second refrigerant flow pipe 21, the second upper tank part 22, and the second lower tank part 23 constitute a leeward refrigerant flow path 20. On the other hand, a first upper tank part 32 is formed above the first refrigerant flow pipe 31 (for example, in the top direction), and a first lower tank part 33 is formed below the first refrigerant flow pipe 31 (for example, in the ground direction). Are formed. 1st refrigerant flow pipe 31, 1st upper tank part 32, 1st lower tank part 33
This constitutes the windward channel 30.

The second upper tank portion 22 and the second lower tank portion 23 are formed with elliptical communication holes 221 and 231 for communicating with the adjacent leeward flow passage 20 respectively. The first upper tank portion 32 and the first lower tank portion 33 are respectively formed with elliptical communication holes 321 and 331 for communicating with the inside of the adjacent windward channel 30. Therefore, the upper half and the lower half of the forming plate 4a are symmetrical, and the leeward half and the leeward half are symmetrical.

Next, the tube element 50 will be described. The tube element 50 that constitutes the leeward heat exchange section 2 and the leeward heat exchange section 3 together with the stacked plurality of tube elements 4 is the outermost end of the leeward heat exchange section 2 and the leeward heat exchange section 3 (FIG. 2). (Left side in the middle), and is disposed at a position closest to the outlet pipe 16 (left side in FIG. 2) in the flow direction of the refrigerant. Tube element 50
Is formed such that one of the pair of forming plates 4a constituting the tube element 4 and an end plate 51 made of an aluminum alloy are opposed to each other. The tube element 50 is provided on the molding plate 4.
a and the outer peripheral portion of the end plate 51 is opposed to each other, through which the refrigerant can pass. The first refrigerant flow pipe 52 is located on the windward side in the air flow direction.
Is formed, and a second side on the leeward side in the air flow direction is formed.
A refrigerant flow pipe 53 is formed.

An end plate 51 and a forming plate 4a, which extend linearly over substantially the entire length in the flow direction of the refrigerant, are joined to the wall surfaces of the first refrigerant flow pipe 52 and the second refrigerant flow pipe 53, respectively. At this time, the I-shaped recesses 13 and 12
A plurality of ribs (protrusions in the claims) 54 and 55 protruding so as to be joined to each other are formed at a pitch of about 7 mm. The first refrigerant flow pipe 52 and the second refrigerant flow pipe 53 are divided into refrigerant narrow flow paths by the ribs 54 and 55,
The area of the refrigerant flow passage through which the refrigerant in the first refrigerant flow pipe 52 and the second refrigerant flow pipe 53 can pass is the refrigerant flow path in the first refrigerant flow pipe 21 and the second refrigerant flow pipe 31 of the tube element 4. It is smaller than the area.

A second upper tank portion 56 is formed above the second refrigerant flow tube 53 (for example, in the top direction), and a second lower tank portion 56 is formed below the second refrigerant flow tube 53 (for example, in the ground direction). (Not shown) are formed. Above the first refrigerant flow pipe 52 (for example, in the top direction), the first upper tank 5
7 is formed, and a first lower tank portion 58 is formed below the first refrigerant flow pipe 53 (for example, in the ground direction).

An elliptical opening 571 communicating with the accumulator 16a is provided at the upper end of the end plate 51 facing the communication hole 321 when the molding plate 4a is joined to the molding plate 4a. 51
An elliptical opening 59 communicating with the accumulator 15a is formed at the lower end portion. At the upper end of the leeward heat exchange section 2, a plurality of second upper tank sections 22 are stacked in the direction in which the leeward flow paths 20 are arranged (stacking direction). A second upper tank portion 56 is disposed at an end (the leftmost end in FIG. 2). As shown in FIG. 2, the second upper tank 24 is formed by the stacked second upper tank portion 22 and second upper tank portion 56. At the lower end of the leeward heat exchange section 2, a plurality of second lower tank sections 23 are stacked in the direction in which the leeward flow paths 20 are arranged (stacking direction). The second lower tank portion of the tube element 50 is disposed at the outermost end (the leftmost end in FIG. 2). As shown in FIG. 5, a second lower tank 25 is formed by the stacked second lower tank section 23 and the second lower tank section of the tube element 50.

A plurality of second lower tank portions 23 are provided substantially at the center in the width direction (stacking direction) of the second lower tank 25.
Separator 27 is provided for dividing the lower tank into two lower tank groups 23a and 23b (see FIGS. 2 and 5). The separator 27 is a partition wall formed by not providing the communication hole 231 on the side wall of the second lower tank portion 23 of the two leeward passages 20 arranged substantially at the center. By the separator 27, the plurality of second refrigerant flow pipes 2
The first and second refrigerant flow pipes 53 are arranged between the upstream second refrigerant flow pipe group 21a (see FIG. 5) disposed on the inlet pipe 15 side and the refrigerant more than the upstream second refrigerant flow pipe group 21a. It is divided into two by a downstream second refrigerant flow tube group 21b (see FIG. 5) disposed on the downstream side of the flow, and the separator 27 also functions as a dividing means of the leeward refrigerant flow passage.

On the other hand, a plurality of first upper tank sections 32 are stacked on the upper end of the windward heat exchange section 3 in the direction in which the windward flow paths 30 are arranged (stacking direction). A first upper tank portion 57 is disposed at an outermost end (the leftmost end in FIG. 2) of the portion 32. First stacked upper tank portion 3
2. The first upper tank portion 57 forms the first upper tank 34 as shown in FIG. At the lower end of the windward heat exchange section 3, a plurality of first lower tank sections 33 are stacked in the direction in which the windward flow paths 30 are arranged (stacking direction). A first lower tank portion 58 is disposed at the outermost end (the leftmost end in FIG. 2). As shown in FIG. 2, the second lower tank 35 is formed by the first lower tank portion 33 and the first lower tank portion 58 that are stacked.

A plurality of first upper tanks 32 are provided substantially at the center of the first upper tank 34 in the width direction (lamination direction).
With two upper tank groups 32a, 32b (see FIG. 5).
Is provided. The separator 36 is connected to the second refrigerant flow pipe 2 of the leeward heat exchange section 2.
It is provided so as to be divided into two at substantially the same position as 1. The separator 36 is provided on the side wall of the first upper tank portion 32 of the two windward passages 30 arranged adjacent to the substantially central portion.
This is a partition wall formed by not providing 21.
Due to the separator 36, the plurality of first refrigerant flow pipes 31 and the first refrigerant flow pipes 52 are connected to the first refrigerant flow pipe group 31a (see FIG. The upstream-side first refrigerant flow path pipe group 31b (see FIG. 5) disposed on the upstream side of the flow of the refrigerant with respect to the flow path group 31a is divided into two parts. Works as well.

The lower tank group 23a constitutes a refrigerant inlet of the refrigerant evaporator 1, and an opening 5 is formed in the second lower tank of the tube element 50 arranged closest to the outlet pipe 16.
9, an accumulator 15a is connected. The accumulator 15a is connected to an inlet pipe 15 (see FIGS. 2 and 5) that connects the leeward heat exchange section 2 of the refrigerant evaporator 1 and a pressure reducing device (for example, an expansion valve, a capillary tube, or an orifice) not shown. .

The upper end tank section group 32a constitutes a refrigerant outlet of the refrigerant evaporator 1, and the first upper tank section 57 of the tube element 50 arranged closest to the outlet pipe 16 is provided with an opening 571. The accumulator 16a is connected. The outlet pipe 16 that connects the windward heat exchange section 3 of the refrigerant evaporator 1 and the suction port of a refrigerant compressor (compressor) not shown is connected to the accumulator 16a. Therefore, the inlet pipe 15 and the outlet pipe 16 are taken out from one side (left side in FIG. 2) of the refrigerant evaporator 1, for example, toward the engine room.

The side plate 7 and the end plate 6 attached to the right side of the refrigerant evaporator 1 will be described. The end plate 6 is a metal plate such as an aluminum alloy, and includes the leeward heat exchange unit 2 and the leeward heat exchange unit 3.
2 is joined to the side from which the inlet pipe 15 and the outlet pipe 16 are not taken out, that is, the rightmost end in FIG. At the upper end and lower end of this end plate 6,
The communication hole 231 of the rightmost second lower tank portion 23 of the lower tank portion group 23b and the communication hole 321 of the rightmost first upper tank portion 32 of the upper tank portion group 32b.
Are formed respectively.

The side plate 7 is a metal plate made of an aluminum alloy or the like integrally formed by press molding, and a communication passage 44 is provided between the end plate 6 and the side plate 7.
Is formed. The communication passage 44 communicates the lower tank group 23b of the second lower tank 25 with the upper tank group 32b of the first upper tank 34, and the second lower tank 25
A one-way flow path for flowing the refrigerant in one direction from the first upper tank 34 is formed.

On the other hand, the side of the leeward heat exchange section 2 and the leeward heat exchange section 3 from which the inlet pipe 15 and the outlet pipe 16 are taken out, that is, the side on which the tube element 50 is disposed (closest to the left end in FIG. 2). The side plate 60 having the same shape as the side plate 7 is joined to the tube element 50 with the corrugated fin 5 interposed therebetween.

Here, a leeward side refrigerant flow path D is formed inside the leeward side heat exchange section 2 by the separator 27, and a leeward side refrigerant flow path E is formed inside the leeward side heat exchange section 3 by the separator 36. Is done. As shown in FIG. 5, the leeward-side refrigerant flow path D of the leeward-side heat exchange unit 2 transfers the refrigerant flowing from the inlet pipe 15 to the second lower tank group 23 a of the plurality of second lower tank units 23 → The upstream side second refrigerant flow path group 21a of the plurality of second refrigerant flow pipes 21 → the plurality of second upper tanks 2
2 → downstream second refrigerant flow path group 21b of the plurality of second refrigerant flow pipes 21 → communication path via the second lower tank part group 23b of the plurality of second lower tank parts 23 The refrigerant flow path leads to 44.

As shown in FIG. 5, the upstream-side refrigerant flow path E transfers the refrigerant flowing from the communication passage 44 to the first upper tank group 32b of the plurality of first upper tanks 32 → the plurality of first upper tank groups. Upstream first refrigerant flow pipe group 3 of one refrigerant flow pipe 31
1b → a plurality of first lower tank portions 33 → a downstream first refrigerant flow tube group 31a among the plurality of first refrigerant flow tubes 31 → a first upper tank portion among the plurality of first upper tank portions 32. Group 3
The refrigerant flow path leads to the outlet pipe 16 via 2a.

Next, the operation and effect of the refrigerant evaporator 1 of this embodiment will be briefly described. The low-temperature, low-pressure gas-liquid two-phase refrigerant adiabatically expanded when passing through the pressure reducing device flows into the second lower tank portion group 23 a of the plurality of second lower tank portions 23 through the inlet pipe 15. I do. The refrigerant flowing into the second lower tank part group 23a is distributed to the upstream second refrigerant flow path group 21a among the plurality of second medium flow path pipes 21. The refrigerant flowing in the upstream-side second refrigerant flow path group 21a exchanges heat with air, evaporates and evaporates, and becomes a gas-liquid two-phase refrigerant having a large amount of liquid phase components.
Flow into 2.

In the second upper tank 24, the refrigerant flowing into each of the second upper tank portions 22, which is located on the back side in the flow direction of the refrigerant, flows into the second side of the plurality of second refrigerant flow pipes 21. The refrigerant is distributed to the refrigerant flow tube group 21b. The refrigerant flowing in the downstream second refrigerant flow pipe group 21b exchanges heat with air to evaporate and evaporate to become a gas-liquid two-phase refrigerant having a little more liquid-phase component, and a plurality of second lower tank portions 23, flows into the second lower tank part group 23b, and flows into the first upper tank part group 32b of the windward heat exchange part 3 through the communication path 44. The refrigerant flowing into the first upper tank section group 32b is distributed to the upstream first refrigerant flow pipe group 31b among the plurality of first refrigerant flow pipes 31. The refrigerant flowing in the upstream first first refrigerant flow pipe group 31b exchanges heat with air, evaporates and evaporates, becomes a gas-liquid two-phase refrigerant having a large amount of gas components, and becomes a plurality of first lower tank portions. It flows into 33.

Subsequently, the refrigerant that has flowed into each of the first lower tank portions 33 that are located on the back side in the flow direction of the refrigerant flows into the downstream first refrigerant flow tube group of the plurality of first refrigerant flow tubes 31. 3
1a. The refrigerant flowing in the downstream first refrigerant flow pipe group 31a exchanges heat with air to evaporate and become superheated vapor (superheated gas), and the first upper tank of the plurality of first upper tank portions 32 After flowing into the group 32a, it flows out from the outlet pipe 16. The superheated steam flowing out of the outlet pipe 16 is drawn into a suction port of the refrigerant compressor through a refrigerant pipe (not shown).

By the way, as shown in the section of the prior art, when the refrigerant is passed from the lower tank portion to the upper tank portion so that the refrigerant flows upward from below in each refrigerant flow pipe, FIG. As shown in FIG. 9, among the refrigerant flowing in the lower tank group, the liquid refrigerant flows toward the back side more than almost half of the lower tank group due to its inertial force, and the gas refrigerant easily flows toward the front side. ing.

However, according to the present invention, the first refrigerant flow pipe 52 of the tube element 50 disposed at the innermost side of the downstream first refrigerant flow pipe group 31a, that is, at the side of the outlet pipe 16 is the rib. The first refrigerant flow path pipe 52 is divided into refrigerant narrow flow paths, and the refrigerant flow path area of the first refrigerant flow path pipe 52 is different from that of the other first refrigerant flow path pipes 31 constituting the downstream first refrigerant flow path pipe group 31a. It is smaller than the road area. Therefore, the pressure loss in the first refrigerant flow pipe 52 is larger than the pressure loss in the first refrigerant flow pipe 31. For this reason, in the downstream-side first refrigerant flow pipe group 31a, in particular, it is possible to prevent the refrigerant from flowing into the first refrigerant flow pipe 52, which is the liquid refrigerant easily flowing into the first refrigerant flow pipe 52 disposed closest to the outlet pipe 16 side. can do.

As a result, the refrigerant passing through the first refrigerant flow pipe 52 can be reliably turned into superheated vapor, and the refrigerant evaporates due to the excessive flow of the refrigerant into the first refrigerant flow pipe 52 of the tube element 50. The refrigerant temperature after passing through the vessel 1 can be prevented from lowering. As a result, the amount of refrigerant flowing into the refrigerant evaporator 1 by the expansion valve can be properly controlled, and a decrease in the capacity of the refrigerant evaporator 1 can be prevented.

Further, as described above, the tube element 50
By preventing the refrigerant from flowing into the first refrigerant flow pipe group 31a downstream, the distribution of the refrigerant flowing into each first refrigerant flow pipe 31 can be made closer to a uniform state, and the refrigerant evaporator The temperature distribution of the air passing through 1 can be made uniform. Hereinafter, the most outlet pipe 1 according to the present embodiment will be described.
The experimental result which shows the effect of preventing the refrigerant | coolant from excessive inflow into the tube element 50 arrange | positioned at 6 side is shown. FIG. 6A is a diagram showing the air temperature distribution near the windward side of the refrigerant evaporator to which the present invention is applied, and FIG. 6B is described in the section of the prior art, which is used as a comparative product of the present invention. Of the refrigerant evaporator,
It is a figure showing the air temperature distribution near the windward side. FIG.
The upper, lower, left and right dimensions correspond to the upper, lower, left and right dimensions of the windward heat exchange part in the refrigerant evaporator 1 of FIG. 2, and show the air temperature distribution near the refrigerant evaporator 1 on the windward side. In FIG. 6C, the solid line indicates the distribution of the air temperature at the portion indicated by the line BB in FIG. 6A, and the dashed line indicates the air temperature at the portion indicated by the line CC in FIG. 6B. Are shown respectively. As the experimental conditions, the air flowing through the air conditioning duct had a temperature of 27 ° C., a humidity of 50%, and an air flow of 4
50 m ³ / h.

As shown in FIG. 6 (a), in a portion (right half in the figure) on the downstream side of the first refrigerant flow pipe group 31a on the outlet pipe 16 side, in the refrigerant evaporator to which the present invention is applied, The temperature was lower (10 ° C.) than that of the comparative product, and the heat exchange property was improved. In particular, according to the present embodiment, by forming the ribs 54 and 55 on the end plate 51 constituting the tube element 50, the pressure loss when the refrigerant passes through the first refrigerant flow pipe 52 is reduced by the other first plate. The pressure loss can be increased as compared with the pressure loss in the refrigerant flow pipe 31. Therefore, it is possible to prevent the refrigerant from excessively flowing into the tube element 50 disposed closest to the outlet pipe 16 without newly providing any member for increasing the pressure loss in the first refrigerant flow path 54, There is no decrease in productivity due to an increase in the number of parts. At the same time, the outer shape of the tube element 50 can be made different from the outer shape of the tube element 4, so that the tube element 50 and the tube element 4 can be easily distinguished by the outer shape, Misassembly of the tube element 4 and the tube element 50 can be easily prevented.

Since the outlet pipe 16 of the refrigerant evaporator 1 is connected to the outermost ends of the leeward heat exchanger 2 and the leeward heat exchanger 3, the tube element 50 is connected to the leeward heat exchanger 2 and the leeward heat exchanger 2. It is arranged at the outermost end of the windward heat exchanger 3. Therefore, after laminating all the tube elements 4,
By further laminating the tube element 50,
Since the leeward heat exchanger 2 and the leeward heat exchanger 3 can be temporarily assembled, erroneous assembly of the tube element 4 and the tube element 50 can be prevented. It can also be prevented from being arranged at the position, and the productivity can be improved.

In the above-described embodiment, the ribs 54 and 55 are formed so as to extend linearly over substantially the entire length in the flow direction of the refrigerant. However, for example, a cross rib or the like may be used. Any shape may be used as long as the pressure loss of the refrigerant flow tube 52 can be increased, and the shape of the rib is not particularly limited. Further, in the present embodiment, as an example of the ribs 54 and 55, a form in which the ribs are formed at a pitch of about 7 mm has been described, but the size of the pitch is not limited to this.
However, in order to make the pressure resistance of the tube element 50 sufficient, the pitch between the ribs 54 and 55 is desirably 10 mm or less.

Further, in the present embodiment, the form in which the ribs 54 and 55 are formed on the wall surfaces of the first refrigerant flow pipe 52 and the second refrigerant flow pipe 53 of the tube element 50 has been described, but the pressure loss is increased. May be formed on the first refrigerant flow pipe 52, which is the refrigerant flow pipe closest to the outlet pipe 16 in the flow of the refrigerant, and the rib is formed only on the pipe wall surface of the first refrigerant flow pipe 52. It may be formed.

In this embodiment, the inlet pipe 15 and the outlet pipe 16 are provided on one side of the refrigerant evaporator 1, and the tube element 50 is arranged at the outermost end of the refrigerant evaporator 1. The position where the tube element 50 in which the ribs 54 and 55 are formed on the pipe wall surface is disposed at a position closer to the outlet pipe side than substantially half in the refrigerant flow direction in the refrigerant flow pipe group in which the refrigerant flows upward. Any position may be used as long as it is arranged. Further, for example, not only the position closest to the outlet pipe side, but also the second, third,.
The refrigerant evaporator may be a refrigerant evaporator provided with a tube element having ribs formed therein. Of the refrigerant flow pipe group in which the refrigerant flows upward, the refrigerant evaporator is disposed closer to the outlet pipe side than substantially half in the flow direction of the refrigerant. In such a position, a configuration in which a plurality of tube elements having ribs formed thereon may be provided.

Further, in the above-described embodiment, the present invention is applied to the refrigerant evaporator 1 in which the leeward heat exchange part 2 and the leeward heat exchange part 3 are divided into two parts by the separators 27 and 36. However, the number of divisions of the first refrigerant flow pipe and the second refrigerant flow pipe by the separator in the refrigerant evaporator to which the present invention can be applied is not particularly limited. Also, the present invention is applicable to a refrigerant evaporator that is not divided by a separator, as long as it has an upper tank and a lower tank connected to the upper and lower ends of the refrigerant flow pipe.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view taken along a plane perpendicular to the direction of flow of a refrigerant at a portion on the outlet pipe side of a refrigerant evaporator in the present invention.

FIG. 2 is a perspective view of a refrigerant evaporator according to the present invention.

FIG. 3 is a perspective view showing a pair of forming plates constituting a tube element.

FIG. 4 is a view showing an end plate which is a part of a tube element in which a rib is formed on a pipe wall surface.
FIG. 4A is a front view of the end plate, and FIG. 4B is a cross-sectional view taken along line AA of FIG.

FIG. 5 is a view showing a flow direction of a refrigerant in a refrigerant evaporator in the present invention.

FIG. 6 is a diagram showing the effect of the present invention, and FIG.
FIG. 6B is a diagram showing the air temperature distribution near the windward side of the refrigerant evaporator in the present embodiment, and FIG. 6B is a diagram showing the air temperature distribution near the windward side of a refrigerant evaporator as a comparative product of the present invention. FIG. 6C shows a portion indicated by line BB in FIG. 6A and a portion C-B in FIG.
It is a figure which shows the air temperature in the part shown by C line.

FIG. 7 is a perspective view of a conventional refrigerant evaporator.

FIG. 8 is a cross-sectional view taken along a plane perpendicular to the flow direction of the refrigerant at a portion on the outlet pipe side of the refrigerant evaporator in the related art.

FIG. 9 is a diagram showing the behavior of the refrigerant when the refrigerant flows up the refrigerant flow pipe from the lower tank to the upper tank.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Refrigerant evaporator 15 Inlet pipe 16 Outlet pipe 21 Second refrigerant flow pipe 24 Second upper tank 25 Second lower tank 31 First refrigerant flow pipe 31a Downstream first refrigerant flow pipe group 32 Upwind upper tank section 34 First upper tank 35 Second lower tank 44 Communication pipe 52 First refrigerant flow pipe 53 Second refrigerant flow pipe

Claims (4)

[Claims] 1. A plurality of refrigerant flow pipes (31), which extend in the up-down direction and in which the refrigerant flows upward in the interior, are stacked substantially perpendicular to the flow direction of the external air; An upper tank (34) connected to the lower end side of the refrigerant flow pipe (31) and extending in the laminating direction of the refrigerant flow pipe (31);
The outlet pipe (1) through which the refrigerant that has passed through 1) flows out
6) a refrigerant evaporator that evaporates a refrigerant passing through the plurality of refrigerant flow pipes (31) and cools external air passing between the plurality of refrigerant flow pipes (31). Of the refrigerant flow pipes (31a) formed by laminating the refrigerant flow pipes (31) of the refrigerant flow pipes disposed closer to the outlet pipe (16) than substantially half in the flow direction of the refrigerant. A protrusion is formed on the pipe wall surface of the passage pipe, and the refrigerant flow path area of the refrigerant flow path pipe on which the protrusion is formed is the same as that of the other refrigerant flow path pipes constituting the refrigerant flow path pipe group. A refrigerant evaporator characterized in that the refrigerant evaporator is smaller than a refrigerant flow passage area. 2. The refrigerant flow pipe group, wherein the protruding portion is formed on a refrigerant flow pipe arranged closest to the outlet pipe side in the flow direction of the refrigerant. The refrigerant evaporator according to claim 1. 3. A first cooling medium flows in the inside, and a plurality of first cooling mediums are stacked in a vertical direction and stacked in a direction substantially perpendicular to the flow direction of the external air.
The refrigerant flow pipes (31, 52) are connected to the upper ends of the stacked first refrigerant flow pipes (31, 52), and the first refrigerant flow pipes (31, 52) are connected.
A first upper tank (34) extending in the stacking direction of the first refrigerant flow pipe and lower ends of the plurality of first refrigerant flow pipes (31, 52) are connected to each other. A first tank (34, 35) having a first lower tank (35) extending in a vertical direction; a refrigerant flowing through the first tank (34, 35); Second refrigerant flow pipes (21, 53) adjacent to the refrigerant flow pipes (31, 52) downstream in the external air flow direction, and upper end sides of the plurality of second refrigerant flow pipes (21, 53) And a second tank (24, 24, 24) extending in the stacking direction of the second refrigerant flow pipes (21, 53).
25) and a communication path (44) for communicating the first refrigerant flow pipe (31, 52) with the second refrigerant flow pipe (21, 53).
And an inlet pipe (15) connected to the second tank (24, 25) to allow the refrigerant to flow into the second refrigerant flow pipe (21, 53); and connected to the first upper tank (34). An outlet pipe (16) through which the refrigerant having passed through the plurality of first refrigerant flow pipes (31, 52) flows out to the outside; and the first refrigerant flow pipes (31, 52) and Evaporating the refrigerant flowing inside the second refrigerant flow pipe (21, 53);
In the refrigerant evaporator (1) for cooling external air flowing between the first refrigerant flow pipe (31, 52) and the second refrigerant flow pipe (21, 53), the plurality of first refrigerant flow paths Among the pipes (31, 52), the first refrigerant flow pipe group (31) disposed on the outlet pipe (16) side.
In a), the refrigerant flows upward from below, and
The refrigerant flows out of the outlet pipe (16) through the first upper tank, and is disposed closest to the outlet pipe (16) in the flow direction of the refrigerant in the first refrigerant flow pipe group (31a). A projection (54) is formed on the pipe wall surface of the first refrigerant flow pipe (52), and the projection (54) is arranged on the first outlet pipe (16) side in the flow direction of the refrigerant. The refrigerant flow path area in the refrigerant flow path pipe (52) is smaller than the refrigerant flow path area in the other first refrigerant flow path pipes (31) constituting the first refrigerant flow path pipe group (31a). A refrigerant evaporator. 4. The refrigerant evaporator according to claim 1, wherein the outlet pipe (16) is connected to one end of the first upper tank (34). .