JP2936775B2 - Heat exchanger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger such as a refrigerant evaporator, a refrigerant condenser, a heater core, a radiator or an oil cooler.

[0002]

2. Description of the Related Art Conventionally, as shown in FIGS. 4 and 5, a tube portion 101 for evaporating a refrigerant and a plurality of refrigerant flow tubes 103 having an inlet tank portion 102 at one end of the tube portion 101 are provided. In the laminated heat exchanger 100, a pipe 105 having a supply hole 104 for evenly distributing a refrigerant for each of a plurality of tube portions 101 is disposed in an inlet tank portion 102 (for example, Japanese Utility Model Publication No. 53-53).
No. 45875) has been proposed.

In the laminated heat exchanger 100, the difference between the inner diameter of the opening 107 formed in the partition wall 106 and the outer diameter of the pipe 105 is less than 0.1 mm, and the inlet is formed. There is no gap between the partition wall 106 of the tank 102 and the pipe 105.

The reason for this is that if the space between the partition wall 106 of the inlet tank 102 and the pipe 105 is not sealed by brazing without any gap, the object of uniformly distributing the refrigerant to the plurality of tube parts 101 by the pipe 105 is achieved. Because they cannot do it.

[0005]

However, in a case where there is no gap between the partition wall 106 of the inlet tank 102 and the pipe 105, a plurality of refrigerant flow pipes 103 are stacked as shown in FIG. Later, the pipe 105 is connected to each opening 10.
7 is inserted into the inlet tank section 102 of the plurality of refrigerant flow pipes 103 so as to penetrate the refrigerant pipes 7. Alternatively, as shown in FIG. 5, the outer periphery of the pipe 105 is divided into the partition wall 106 regardless of the method of inserting the core plate 108 constituting the refrigerant flow path tube 103 into the pipe 105 one by one. , And the assembling of the inlet tank portion 102 of the refrigerant flow pipe 103 and the pipe 105 could not be easily performed.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a heat exchanger that can easily assemble a tank and a pipe and that reliably seals the outer periphery of the pipe and a plurality of partition walls of the tank.

[0007]

SUMMARY OF THE INVENTION According to the present invention, a plurality of tubes are arranged in parallel, and a heat medium flowing therethrough is exchanged with heat. The tubes are connected to ends of the tubes. A tank having a plurality of partition walls partitioned into a plurality of tank portions communicating with each of the plurality of tube portions, and a tank having openings in these partition walls; And a pipe inserted into the tank through each opening of the plurality of partition walls, and the pipe has a dimension set from each opening of the plurality of partition walls. The technical means is formed by a tubular member having a diameter which is only small and whose diameter is increased by the differential pressure between the internal pressure and the external pressure.

[0008]

[Function] Since the diameter of the pipe is smaller than each opening of the plurality of partition walls by the set dimension, the pipe is inserted into the tank so as to penetrate each opening of the plurality of partition walls that divides the tank into a plurality of tank sections. At this time, the outer periphery of the pipe is inserted into the tank without being caught by the plurality of partition walls.

When a heat medium or the like is caused to flow into the pipe after the pipe is assembled in the tank, the internal and external pressures of the pipe are reduced by the pressure loss when the heat medium and the like pass through the supply holes formed on the outer periphery of the pipe. , A differential pressure occurs. Due to this pressure difference, the diameter of the pipe increases by more than the set dimension, and the outer periphery of the pipe and the plurality of partition walls come into close contact with each other. Therefore, the heat medium flowing into a certain tank portion from the supply hole of the pipe does not flow into another adjacent tank portion from between the outer periphery of the pipe and the plurality of partition walls. Therefore, the heat medium flowing into the pipe is evenly distributed for each of the plurality of tube portions.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A heat exchanger according to the present invention will be described with reference to one embodiment shown in FIGS. 1 to 3 are views showing a laminated refrigerant evaporator. The laminated refrigerant evaporator 1 uses the gas-liquid mixed refrigerant as a refrigerant gas by exchanging heat between the gas-liquid mixed refrigerant flowing into the inside and air passing outside.

The laminated refrigerant evaporator 1 has a refrigerant flow pipe 3 formed by joining a pair of molded plates 2 and a corrugated fin 4 disposed between two adjacent refrigerant flow pipes 3. Are laminated in the width direction of the laminated refrigerant evaporator 1 and brazed in a furnace to be assembled.

The molding plate 2 is formed in a shallow dish shape by pressing a clad plate in which a brazing material is adhered to both surfaces of a thin plate-shaped aluminum alloy.

At one end of the refrigerant flow pipe 3, a cup-shaped inlet tank 5 and a cup-shaped outlet tank (not shown) are formed as the tank of the present invention. Also,
Between the inlet tank 5 and the outlet tank, the inlet tank 5 and the outlet tank communicate with each other in a substantially U-shape, and a flat dish-shaped tube 6 for exchanging heat between the refrigerant flowing therein and air.
Are formed.

The plurality of inlet tanks 5 form an inlet tank 7 as the tank of the present invention. Further, the plurality of inlet tanks 5 have a plurality of partition walls 8 that communicate with each one of the tube portions 6 and partition adjacent inlet tanks 5. On these partition walls 8,
An opening 10 into which a cylindrical pipe 9 is inserted is formed. Furthermore, the inlet tank 5 located at the most upstream side
The seal between the pipe and the pipe 9 is sealed by a packing material 12 held in a hard annular member 11.

A supply hole 13 for distributing the refrigerant to one tube portion 6 is formed on the outer periphery of the pipe 9. The pipe 9 is made of a material (for example, synthetic rubber, resin, aluminum, etc.) whose outer diameter is liable to increase due to elastic deformation or plastic deformation due to the differential pressure between the internal pressure and the external pressure when the gas-liquid mixed refrigerant passes through the supply hole 13. And the like (for example, 1.5 mm in the case of nylon resin (trade name) and 0.015 mm in the case of aluminum).

In this embodiment, as shown in FIG. 1, when the opening diameter of the opening 10 of the partition wall 8 is φD 1 and the outer diameter of the pipe 9 is φD 2, 0.1 mm ≦ D 1 −D 2
The opening 10 of the partition wall 8 and the pipe 9 are formed so as to satisfy (set dimensions) ≦ 2.0 mm. Note that D1
When -D2 <0.1 mm, the pipe 9 was difficult to be inserted into the opening 10 of the partition wall 8 and was therefore removed. Also, D
In the case of 1-D2> 2.0 mm, the strength of the pipe 9 was reduced, so that it was removed.

Further, when the opening diameter of the supply hole 13 is φd, the supply hole 13 is formed so as to satisfy 0.1 mm ≦ d ≦ 3.0 mm. In the case of d <0.1 mm, the gas-liquid mixed refrigerant is difficult to discharge from inside the pipe 9 and is therefore excluded. When d> 3.0 mm, the gas-liquid mixed refrigerant
Since the pressure difference between the internal pressure and the external pressure when discharging from the inside does not increase so much, it was decided to remove it.

The operation of the laminated refrigerant evaporator 1 according to the present embodiment will be described with reference to FIGS. As shown in FIG. 1, the laminated refrigerant evaporator 1 has an opening diameter (φD 1) of the opening 10 of the partition wall 8 and an outer diameter (φD 2) of the pipe 9.
It is formed so as to satisfy 1 mm ≦ D 1 −D 2 (set dimension) ≦ 2.0 mm.

That is, since the set dimension, which is the difference between the opening diameter of the opening 10 of the partition wall 8 and the outer diameter of the pipe 9, is at least 0.1 mm, a plurality of refrigerant flow pipes 3 are laminated and integrated. After fitting, when fitting the pipe 9 into the inlet tank 7 so as to penetrate each opening 10 of the plurality of partition walls 8,
The pipe 9 can be inserted smoothly without being caught on the partition wall 8 by the outer periphery. Therefore, the inlet tank 7
The operation of assembling the pipe 9 into the pipe becomes extremely simple.

When the cooling operation is performed by incorporating the manufactured laminated refrigerant evaporator 1 into a refrigeration cycle, a gas-liquid mixed refrigerant flows into the pipe 9. The gas-liquid mixed refrigerant flowing into the pipe 9 flows from the plurality of supply holes 13 into the respective inlet tank portions 5 corresponding to the supply holes 13, and further flows into the respective tube portions 6.

At this time, as shown in FIG.
The opening diameter (φd) of No. 3 is formed so as to satisfy 0.1 mm ≦ d ≦ 3.0 mm. For this reason, when the gas-liquid mixed refrigerant is discharged from the supply hole 13 of the pipe 9, the internal pressure of the pipe 9 and the external pressure are reduced by the pressure loss when the gas-liquid mixed refrigerant passes through the supply hole 13 of the pipe 9. A differential pressure is generated with the pressure. Since the outer diameter of the pipe 9 elastically expands beyond a set size due to the difference between the inner and outer pressures, the plurality of partition walls 8 and the outer peripheral surface of the pipe 9 are tightly sealed and securely sealed. 7 does not leak from between the partition wall 8 and the pipe 9 and flow into the adjacent inlet tank 5.

Therefore, the gas-liquid mixed refrigerant that has flowed into the pipe 9 is evenly distributed to each of the plurality of tube portions 6, so that uniform heat exchange can be performed for each of the plurality of tube portions 6. For this reason, it is possible to suppress a decrease in heat exchange efficiency in each of the tube portions 6.

Here, an experiment was conducted to examine the degree of expansion when the gas-liquid mixed refrigerant passes through the supply hole 13 of the pipe 9. The dimensions used in this experiment will be described later. When the outer diameter (φD2) of the pipe 9 is 15 mm and the set dimension is 0.5 mm, the inner diameter (φD1) of each opening 10 of the plurality of partition walls 8 is set.
Is 15.5 mm. The material of the pipe 9 is nylon resin (trade name) [E = 2.0 kg / mm ² ] and the wall thickness is 1.
The thing of 5 mm was used.

When the number of the tube portions 6 is 20, the number of the supply holes 13 of the pipe 9 is set to 20, and the opening diameter (φ
Assuming that d) is 0.3 mm, when the gas-liquid mixed refrigerant passes through the supply hole 13 of the pipe 9 during the cooling operation, a differential pressure of ² kg / cm ² or more between the internal pressure and the external pressure of the pipe 9 is generated. Occur.

Therefore, the distortion of the diameter of the pipe 9 can be expressed by the following equation. (ΔD2 / D2) = ε = (σ0 / E) = {(P · D2) / 2t} / E where P is the differential pressure, t is the wall thickness of the pipe 9, and E is the Young's modulus of the pipe 9.

That is, the degree of expansion of the pipe 9 can be expressed by the following equation. .DELTA.D2 = D2.times. {(P.D2) / 2t} / E By substituting a numerical value into the above equation, it becomes 0.75 mm, and it can be seen that the pipe 9 expands in the radial direction of 0.75 mm.

Therefore, the set dimension of 0.5 mm, that is,
The gaps between the openings 10 of the plurality of partition walls 8 and the outer periphery of the pipe 9 can be reliably sealed. In this way, when a pipe 9 of another material and thickness is adopted,
By designing the degree of expansion of the pipe 9 in consideration of the set dimensions, each opening 10 of the plurality of partition walls 8 and the outer periphery of the pipe 9 can be similarly sealed.

(Modification) In the present embodiment, the present invention is applied to a laminated refrigerant evaporator. However, the present invention may be applied to a refrigerant evaporator other than a laminated heat exchanger. Further, the present invention may be used for a refrigerant condenser, a heater core, a radiator, an oil cooler, or the like.

In this embodiment, a cylindrical pipe is used. However, an elliptical pipe or a multi-hole cross-sectional pipe may be used.
Further, not only elastic expansion due to a pressure difference between the inside and outside generated in the pipe during operation but also plastic deformation of the pipe by pressurization at the time of manufacturing may seal each opening of the plurality of partition walls and the outer periphery of the pipe.

[0030]

According to the present invention, a pipe is formed by a tubular member having a diameter smaller than a set dimension from each opening of a plurality of partition walls inserted into the tank, so that the pipe is attached to the tank when the pipe is assembled. Since the outer periphery is inserted into the tank without being caught by the plurality of partition walls, the pipe can be smoothly assembled to the tank.

Further, by forming the pipe with a tubular member whose diameter increases by a predetermined dimension or more due to the differential pressure between the internal pressure and the external pressure, after the pipe is assembled into the tank and the heat medium or the like flows into the pipe, the pipe is formed. Since it expands radially outward, the outer periphery of the pipe and the plurality of partition walls of the tank can be reliably sealed.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a state before a cooling operation of a laminated refrigerant evaporator of the present invention.

FIG. 2 is a cross-sectional view showing a state in which a cooling operation of the laminated refrigerant evaporator of the present invention is performed.

FIG. 3 is a front view showing a laminated refrigerant evaporator of the present invention.

FIG. 4 is a cross-sectional view illustrating a method of assembling a conventional laminated refrigerant evaporator.

FIG. 5 is a sectional view showing a method of assembling a conventional laminated refrigerant evaporator.

[Explanation of symbols]

 Reference Signs List 1 laminated refrigerant evaporator (heat exchanger) 5 inlet tank (tank) 6 tube 7 inlet tank (tank) 8 partition wall 9 pipe 10 opening 13 supply hole

──────────────────────────────────────────────────続 き Continuation of front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F28F 9/02 301

Claims (1)

(57) [Claims] 1. A plurality of tube portions which are arranged in parallel and exchange heat with a heat medium flowing therethrough, are connected to ends of these tube portions, and communicate with each of the plurality of tube portions. A plurality of partition walls partitioned into a plurality of tank portions, and a tank having openings in these partition walls, and a supply hole on the outer periphery for uniformly distributing the heat medium for each of the plurality of tube portions. A pipe inserted through the opening of each of the plurality of partition walls into the tank, wherein the pipe has a diameter smaller than each of the openings of the plurality of partition walls by a set dimension, and an internal pressure. A heat exchanger characterized by being formed of a tubular member whose diameter increases by more than the set dimension due to a pressure difference from an external pressure.