JPH064227Y2 - Stacked heat exchanger - Google Patents

Description

[Detailed Description of the Invention] [Industrial field of application] The present invention relates to a laminated heat exchanger with a tank on one side, and in particular, heat exchange in the heat exchanger used in a vehicle refrigeration system or the like. The present invention relates to a laminated heat exchanger configured to reduce passage resistance of a medium.

[Prior Art] Among the laminated heat exchangers of this type, those having tanks on both sides of the passage of the heat exchange medium have a problem of increasing in size, and therefore, recently, there is a tank on one side in which a tank is provided only on one side of the passage. The laminated heat exchanger of is also developed. For example,
60-154774 and JP-A-62-119373.

Thus, as a specific example of such a laminated heat exchanger, for example, in an evaporator of a vehicle cooler, a refrigerant as a heat exchange medium such as freon is brought into a mist-like liquid phase state by an expansion valve at a preceding stage in the refrigeration cycle. Then, the heat of vaporization from the introduced air passing through the evaporator is vaporized to become a vapor phase state and is supplied to the compressor of the next stage.

However, as the volume of the refrigerant increases due to the change from the liquid state to the gas state, the passage resistance in the passage increases and the load on the compressor that circulates the refrigerant also increases. There is a problem that it needs to be converted. In order to solve these problems,
As in 61-93387, there is one in which the passage cross-sectional area of the heat exchange medium is increased stepwise in the flow direction unit from the inlet side to the outlet side.

However, even in such a heat exchanger, since it is intended to increase the passage cross-sectional area of the heat exchange medium step by step in each unit of the flow direction of the heat exchange medium, The problem has not been solved yet.

In particular, in a laminated heat exchanger with a tank on one side, the tank portion having a relatively large volume is on only one side, so the above-mentioned increase in passage resistance is a problem that cannot be ignored.

[Problems to be Solved by the Invention] The present invention has been made in consideration of the above-mentioned problems. When the heat exchange action is performed, the heat exchange medium changes from its liquid state to its gas state. The volume of the heat exchange medium passage is gradually increased according to the volume change, and the passage resistance of the heat exchange medium in the laminated heat exchanger is reduced in all passages of the heat exchanger to reduce the load on the compressor and reduce the size. It is an object of the present invention to provide a laminated heat exchanger that can be made into a material.

[Means for Solving the Problems] That is, according to the present invention, in a laminated heat exchanger configured by alternately stacking heat exchange elements and fins, the passages in the heat exchange elements are divided into a predetermined number of passage areas. In addition, by appropriately selecting the combination of the width of the heat exchange element passages and the number of stacked sheets in each passage area, the volume ratio of the passages in each passage area is changed from the inlet side to the outlet side of the heat exchange medium. The heat exchanger is configured so that its cross-sectional area or volume gradually increases from the inlet side to the outlet side of the heat exchange medium over all the passages.

[Operation] In the present invention, at the inlet side of the heat exchanger, the heat exchange medium in a liquid state in the form of mist passes through the heat exchanger, and the heat of vaporization from other fluids such as introduced air is absorbed by the heat absorption action. Even if it is vaporized when it is spilled and its volume is increased, the passage volume is made larger toward the outlet side, so it is possible to reduce the passage resistance and reduce the load on the compressor etc. And, it can be miniaturized.

[Embodiment] Next, one embodiment of the present invention will be described with reference to the drawings by taking as an example the case of being applied to an evaporator for a vehicle.

FIG. 1 is a front view of a laminated evaporator 1 with a tank on one side as a laminated heat exchanger according to an embodiment of the present invention. The laminated evaporator 1 is entirely housed in an air conditioning case 2. Air from outside or inside the vehicle, which is taken in by a blower (not shown), is blown, for example, from the front side to the back side of the paper.

The laminated evaporator 1 is configured by alternately stacking a plurality of heat exchange elements 3 and corrugated fins 4 in multiple stages, and a refrigerant inlet pipe 5 and an outlet pipe 6 are connected to the lower left and right ends thereof, respectively. The inlet block 7 and the outlet block 8 are attached. In addition, the cross-sectional areas of the refrigerant inlet hole and the refrigerant outlet hole to which the inlet pipe 5 and the outlet pipe 6 are attached are larger in the latter than in the former. Also, the inlet pipe 5
The outlet pipe 6 is connected to an expansion valve and a compressor (both not shown) of the refrigeration cycle.

In addition, at the left and right ends of the heat exchange element 3 in the stacking direction,
A reinforcing end plate 9 is attached. Further, a water receiving chamber 10 is formed in the lower portion of the air conditioning case 2.

Next, regarding the structure of the heat exchange element 3,
A more detailed description will be given with reference to FIGS.

2 is a front view of a molding plate 11 for forming the heat exchange element 3, FIG. 3 is a rear view of the molding plate 11, FIG. 4 is a partially enlarged partial sectional view of FIG. 1, and FIG. FIG. 4 is an exploded perspective view of a heat exchange element 3 portion.

First, as shown in FIG. 2, the molding plate 11 is manufactured by punching and pressing an aluminum plate, has an oblong rectangular plate shape, and has an outer peripheral wall 12 of a predetermined height at the outer edge thereof. By forming it, a shallow passage recess 13 is formed inside, and this passage recess 13 is used as the coolant passage 14.

Further, a pair of tank portion recesses 15 deeper than the shallow passage recesses 13 are formed in the lower portion of the molding plate 11 so as to communicate with the shallow passage recesses 13 to form a tank portion 16. The through hole 17 is formed in the hole.

Further, a partition wall 18 extending in the lengthwise direction of the molding plate 11 is formed between the tank portions 16, and the partition wall 18 is formed at the same height as the outer peripheral wall 12 to divide the passage 14 into left and right parts. However, the partition wall 18 is formed by the molding plate 1.
It is assumed that the outer peripheral wall 12 located at the upper part of 1 is not formed, and that the passage 14 divided into right and left can communicate with each other.

In FIG. 3, reference numeral 19 indicates the molding plate 1 described above.
2 shows a back wall on the opposite side of 1.

As shown in FIG. 4, the molding plate 11 thus formed is brazed by facing each other on the surface sides of the molding plate 11, that is, the surface sides on which the passage recess 13 and the tank recess 15 are formed. The passage 14 and the tank portion 16 are formed inside the molding plate 11 to form the heat exchange element 3 as a basic unit.

Further, the corrugated fins 4 are disposed on the back wall 19 of the molding plate 11, and the heat exchange element 3 and the fins 4 for improving heat exchange efficiency are alternately stacked in a plurality of stages to form the laminated type. Configure the evaporation 1.

In the present embodiment, the partition wall 18 is not formed in the central portion of each molding plate 11, but is formed by bending it to the left and right as shown in FIG. There shall be a difference in volume.

Therefore, in order to prevent an irregular change in the passage cross-sectional area of the refrigerant passing through the inside of the laminated evaporator 1, the width of the tank portion 16 is formed so as to match the width of the refrigerant passage 14. Generally, however, it may be formed to have the same width in all passages irrespective of the width of the passage 14 for the refrigerant in order to meet the requirements of work forming and balance between the left and right sides.

Of course, the communication hole 17 of the tank portion 16 is for communicating between the adjacent heat exchange elements 3, but a part of the communication hole 17 of the tank portion 16 is not formed as described later. By setting the closed state, it is possible to change the refrigerant flow path. When the width of the tank portion 16 is formed to be the same width in all the passages regardless of the width of the passage 14 for the refrigerant as described above, the communication holes 17 are arranged in a straight line in each heat exchange element 3. The formation position can be standardized so that it can be formed.

Next, the change of the refrigerant flow path and the accompanying passage 14
The change in volume will be described with reference to FIGS. 6 and 7.

FIG. 6 is a plan view of the laminated evaporator 1, and FIG. 7 is a schematic diagram of the laminated evaporator 1, in which the passages 14 in the laminated evaporator 1 are four passage areas A in this embodiment. It is divided into B, C, and D (see boundary lines AB, BC, CD, and DA by phantom lines in FIG. 6). The sixth
In the figure, the fins 4 are not shown for the sake of clarity.

That is, as shown in FIG. 6, the passage area A is connected to the inlet block 7, the passage area B is constituted by the same molding plate 11 as the passage area A, and the passage area C is adjacent to the passage area B. Further, the passage section D is constituted by the same molding plate 11 as the passage section C and is connected to the outlet block 8.

More specifically, the boundary between the passage area A and the passage area B is a partition wall of each of a total of 16 forming plates 11 (8 units as the heat exchange element 3) that constitute both passage areas A and B. It is formed by 18. The boundary between the passage area A and the passage area D does not form the communication holes 17 (see FIG. 4 and FIG. 5) of the tank portion 16A of the passage area A and the tank portion 16D of the passage area D, and keeps them closed. It is formed by doing so.

Further, the passage area B and the passage area C communicate with each other through the communication holes 17 formed in the tank portions 16B and 16C.

Further, the boundary between the passage area C and the passage area D is formed by the respective partition walls 18 of a total of 20 forming plates (10 units as the heat exchange element 3) forming the passage areas C and D.

Then, as shown in FIG. 7, the atomized liquid phase refrigerant introduced into the laminated evaporator 1 through the inlet pipe 5 and the inlet block 7 first enters the tank portion 16 in the passage area A. Then, it vaporizes while rising in the passage 14, transitions from above the partition wall 18 to the passage 14 in the passage area B, descends in the passage area B, and enters the tank portion 16 in the passage area B. Then, it enters the tank portion 16 in the passage area C through the communication hole 17, rises up the passage 14 in the passage area C, and the partition wall 1
Enter the passage 14 in the passage area D separated by 8. Next, it is introduced into the next stage compressor from the outlet block 8 and the outlet pipe 6 through the passage 14 and the tank portion 16 in the passage area D.

The refrigerant passes through each of the passages 14 through such a passage, but the passage area A, the passage area B, the passage area C,
It is a feature of the present invention that the volume of the passage is gradually increased from the inlet side to the outlet side of the refrigerant in each inside of the passage area D.

That is, as shown in the table of FIG. 8, each passage area A,
The width of the passage 14 formed by the B, C, and D molding plates 11 is
For example, "5: 6" is set in the passage areas A and B, and "5: 6" is also set in the passage areas C and D. Further, the number of 3 units of heat exchange elements is set to, for example, "4: 5".

More specifically, the partition wall 18 shown in FIG. 2 and FIG.
By shifting the formation position of the passages to the right of the forming plate 11 in the drawing, the passage widths of the passages 14 adjacent to each other are set to the above "5: 6"
Set to. Further, as shown in FIG. 6, the passage area A,
By setting the units of the heat exchange elements 3 constituting B and the passage areas C and D to 8 units and 10 units, the number ratio of the molding plates 11 or the unit ratio of the heat exchange elements 3 is set to the above "4: 5". Set.

Under such setting conditions, each passage area A, B, C, D
The volume ratio of is the product of the width and the number of sheets, and is "20: 24: 25: 30" as shown in the table of FIG. 8, and each passage area A, B, C, D is from the passage area A. The volume gradually increases as the refrigerant moves from the inlet side toward the outlet side toward the passage section D.

On the other hand, as described above, with the passage of the refrigerant in the passage 14, the refrigerant in the liquid phase changes to the gas phase by absorbing heat and increases its volume.

Therefore, since the volume of the passage 14 gradually increases corresponding to the increase in the volume of the refrigerant, the passage resistance of the refrigerant in the passage 14 does not increase.

As a result, the load on the compressor that allows the refrigerant to pass through the passage 14 of the laminated evaporator 1 is reduced, and the laminated evaporator 1 can be provided according to the state of the refrigerant in the laminated evaporator 1.

In the present invention, the communication hole 17 in the above embodiment
Also, the way of dividing the passage area by the site where the partition wall 18 is formed is arbitrary, and the number thereof can be appropriately designed,
The volume ratio may be selected depending on the application and scale of the laminated evaporator and other heat exchangers.

In dividing the passage areas, the sixth embodiment of the above embodiment
The positions of the boundary lines AB, BC, CD, DA in the figure are divided so that the boundary line AB and the boundary line CD are aligned with each other, and the width of the passage section D is accordingly illustrated in FIG. It is also possible to make it project further downward in the drawing.

Further, the laminated heat exchanger with the one-side tank has been described as an example, but the present invention can be applied to the heat exchanger with the two-side tank.

[Advantages of the Invention] As described above, according to the present invention, the passage area is gradually increased so that the volume of the passage is gradually increased according to the volume change accompanying the change of the phase state of the heat exchange medium passing through the inside of the laminated heat exchanger. Since it is configured by partitioning, it is possible to pass the heat exchange medium without increasing the passage resistance in the passage, downsizing the heat exchanger such as a laminated evaporator and reducing the load on the compressor and It is possible to realize miniaturization.

[Brief description of drawings]

1 is a front view of an embodiment of the present invention, FIG. 2 is a front view of the molding plate 11, and FIG. 3 is a molding plate 11 thereof.
4 is a partial enlarged partial sectional view of the laminated evaporator 1, FIG. 5 is an exploded perspective view of the heat exchange element 3 portion, and FIG. 6 is a plan view of the laminated evaporator 1.
FIG. 7 is a schematic diagram of the laminated evaporator 1,
FIG. 8 is a table of the volume ratio of the passage areas A, B, C, D in the same manner. DESCRIPTION OF SYMBOLS 1 ... Laminated evaporator 2 ... Air conditioning case 3 ... Heat exchange element 4 ... Corrugated fin 5 ... Inlet pipe 6 ... Outlet pipe 7 ... Inlet block 8 ... Outlet block 9 ... Reinforcing end plate 10 ... Water receiving chamber 11 Molding plate 12 Outer peripheral wall 13 Passage recess 14 Refrigerant passage 15 Tank portion recess 16 Tank portion 17 Communication hole 18 Partition wall 19 Back wall A, B, C, D ... Passage area AB, BC, CD, DA ... Borderline of passage area

Claims (3)

[Scope of utility model registration request] 1. A heat exchange element having a passage for a heat exchange medium and a plurality of molding plates each having a depression for a tank portion on one side thereof laminated to form a passage for a heat exchange medium and a tank portion capable of communicating with each other. And a fin are alternately stacked in a plurality of stages, and the heat exchange medium is formed by a partition wall formed in the concave portion for passage of the molding plate so as to extend in the lengthwise direction and leave a part thereof. Passages are formed and the partition walls are formed so as to be offset from the center in the width direction of the forming plate, and the passages in the heat exchange element are divided into a predetermined number of passage areas, and the heat in each passage area is divided. By appropriately selecting the combination of the width of the passages of the exchange element and the number of stacked sheets, the volume ratio of the passages in each passage area is changed from the inlet side to the outlet side of the heat exchange medium. Layered heat exchanger being characterized in that so as to incrementally Te. 2. The laminated heat exchanger according to claim 1, wherein the width of the tank portion is matched with the width of the passage of the heat exchange medium. 3. The laminated heat exchanger according to claim 1, wherein the tank portion has the same width as a whole regardless of the width of the passage of the heat exchange medium. .