JPH07332890A - Double type heat exchanger - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a double-integrated heat exchanger that can significantly improve manufacturing efficiency, reduce manufacturing cost, and further reduce size and weight. The purpose is to [Structure] As a basic structure, a so-called laminated heat exchanger in which a plurality of strip-shaped tube elements 1 are laminated in the thickness direction with fins 2 interposed therebetween is adopted. As each tube element 1, one having a plurality of heat exchange medium flow passages 3 and 4 composed of flat tubes 3a and 4a and bulging headers 3b and 4b communicating with both ends thereof in a mutually independent manner is used. . Then, the adjacent tube elements 1 are communicatively connected at the headers 3b and 4b to integrally configure the plurality of heat exchangers X and Y.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a radiator,
The present invention relates to a multi-layer laminated heat exchanger in which two or more heat exchangers such as a condenser, an evaporator, an intercooler, and an engine oil cooler are integrally configured.

[0002]

2. Description of the Related Art Conventionally, for example, a radiator for cooling an engine and a condenser for a car air conditioner are manufactured separately, and are placed in a front position in an engine room of an automobile, in a front-rear proximity state where the condenser is located on a windward side of the radiator. It is installed side by side.

However, if both of them are manufactured separately and installed in a limited space in the engine room in a front-rear proximity state, both manufacturing and installation work will be costly and troublesome. . Such inconvenience is not limited to the relationship between the condenser and the radiator, but may occur with other heat exchangers.

On the other hand, for example, Japanese Patent Laid-Open No. 1-2479.
As shown in Japanese Patent Publication No. 90, a double type integrated heat exchanger in which two heat exchangers such as a condenser and a radiator are integrated has been proposed.

In this double-integrated heat exchanger, a plurality of flat tubes having fins interposed between them are arranged between a pair of headers arranged in parallel with each other at a predetermined interval. The first heat exchanger and the second heat exchanger having both ends connected to the corresponding headers are connected side by side, and a common fin extending over both heat exchangers is used as a fin for each heat exchanger. As a result, both heat exchangers are connected and integrated.

[0006]

Such a conventional double-integrated heat exchanger is integrated as compared with a plurality of heat exchangers which are separated and independent, so that it is easy to install the heat exchanger in an automobile or the like. There is an advantage that simplification can be achieved.

[0007] However, the conventional double integrated heat exchanger of this type is basically only the independent heat exchangers connected by the common fins, so that the manufacturing efficiency is notably improved. Therefore, it was not possible to significantly reduce the manufacturing cost. Also, a pair of header pipes arranged in parallel,
Since a plurality of heat exchangers having the conventional structure having a plurality of tubes for connecting them in communication are simply arranged by connecting them in front and back, they are particularly strongly required to be small in size in recent years. It has not always been possible to sufficiently satisfy the need for weight reduction.

The present invention has been made in view of the above circumstances, and it is possible to significantly improve the manufacturing efficiency, thereby reducing the manufacturing cost, and further reducing the size and weight. An object is to provide a double-integrated heat exchanger.

[0009]

The present invention has, as a basic structure, a so-called laminated type in which a plurality of strip plate tube elements are laminated in the thickness direction with fins interposed therebetween. By adopting the heat exchanger of No. 2 and providing each tube element with a plurality of heat exchange medium flow passages composed of a flat tube and bulging headers communicating with both ends of the tube in a mutually independent manner, The heat exchanger is configured integrally. That is, the present invention is provided with a plurality of strip plate tube elements, and each tube element has a flat tube and a bulging shape communicating with both ends thereof by stacking two core plates facing each other. A plurality of heat exchange medium flow passages, which are composed of headers and are independent of each other, are formed, and these tube elements have fins interposed between the flat tubes and the headers are joined to each other. In this state, the heat exchange medium flow passages at corresponding positions in the adjacent tube elements, which are stacked in the thickness direction, are communicatively connected at the header, so that a plurality of heat exchangers independent from each other are formed. The gist of the present invention is a multi-layer heat exchanger of the type described above.

Examples of the combination of a plurality of heat exchangers independent of each other in the above-mentioned multi-layer type heat exchanger include, for example, a condenser and a radiator, an intercooler and a radiator,
Engine oil coolers and radiators can be mentioned as preferred embodiments. However, the present invention is not limited to the combination of two heat exchangers of different types as described above, and is also applicable to the combination of three or more heat exchangers of different types, or further two or more heat exchanges of the same type. The same applies to a combination of vessels.

The multi-layer type heat exchanger may be a so-called horizontal type in which tube elements are vertically stacked in a horizontal state, and a so-called horizontal type in which tube elements are vertically stacked in a vertical state. It may be a vertical type.

It is desirable to form one or a plurality of notches between the flat tubes of both heat exchange medium flow passages for the purpose of reducing the heat influence between the heat exchange medium flow passages in each tube element. .

Further, as the fins, for the purpose of reducing the number of parts and facilitating the setting of the fins, one common fin arranged so as to straddle both flat tubes of each tube element is used. It is preferable that one or a plurality of notches are formed in the middle portion in the width direction of the flat tube to block heat conduction between the flat tubes.

When any one of the heat exchangers is configured as a condenser, a corrugated tube is formed inside the flat tube in the heat exchange medium flow passage functioning as a condenser for the purpose of improving the pressure resistance and the heat exchange efficiency. It is preferable that the inner fins of the above are loaded, the flow passage portion is divided by the fins into a plurality of passages, and a pair of core plates constituting the tube element are joined and integrated.

[0015]

A plurality of heat exchangers are constructed by connecting the heat exchange medium flow passages of the adjacent tube elements through communication in the bulging header.

A heat exchange medium flows into each heat exchange medium flow passage of the tube element from one header, flows through the flat tube and flows into the other header.

As described above, while the heat exchange mediums are separately circulated in the respective heat exchangers independently of each other, the air circulation gap including the fins formed between the tube elements constituting these heat exchangers. Air flows through. Thus, heat exchange is performed between each heat exchange medium and air.

[0018]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below based on an embodiment applied to a heat exchanger integrally having a radiator and a condenser.

In this specification, the term aluminum is used to include an aluminum alloy.

(First Embodiment) FIGS. 1 to 21 show a first embodiment of the present invention. In a multi-layer stack type heat exchanger according to this embodiment, the inside of each tube element is It is a so-called vertical type in which the heat exchange medium flows vertically.

This heat exchanger comprises a plurality of vertically elongated aluminum strip plate tube elements (1) which are vertically stacked and arranged in the left-right direction, and between adjacent tube elements (1) (1). And a corrugated fin (2) made of aluminum, which is also interposed and integrally joined.

As shown in FIGS. 1 and 17, the tube element (1) has flat tubes (3a) (4a) on both sides in the width direction and bulging headers (3b) (which communicate with both ends thereof). 4b) and the heat exchange medium flow passages (3) and (4) are integrally provided in a mutually independent manner. The heat exchange medium flow passage (3) located on one of the windward sides serves as a condenser (X), and the heat exchange medium flow passage (4) located on the other leeward side is a radiator (Y).
Respectively function as.

Then, the both flat tubes (3a)
An elongated notch (5) along the longitudinal direction is formed between (4a) to block heat conduction between both tubes. Due to the presence of the notch portion (5), heat of one flat tube (3a) is suppressed from being conducted to the other flat tube (4a).

Then, each tube element (1) is
As shown in FIGS. 10 to 13, adjacent ones are brazed to each other in abutment state at the headers (3b) and (4b), and the heat exchange medium distribution provided in each header (3b) and (4b). Adjacent headers are connected to each other through the holes (6) and (7).

Each of the tube elements (1) is formed by superposing two strip-shaped core plates (P) each having an elongated dish shape so as to face each other and integrally brazing.

The core plate (P) is formed by press working. By forming by press working in this way, the manufacturing efficiency can be greatly improved. As the material of the core plate (P), a brazing sheet in which a brazing material layer is clad on both surfaces of an aluminum core material is preferably used. By using such a brazing sheet, the two core plates (P) and (P) that are arranged to face each other and that constitute the tube element (1), the adjacent tube elements (1), and the tube element (1) The brazing work such as the brazing of the 1) and the fins (2) can be easily and surely performed.

As shown in FIG. 6, for example, the core plate (P) has a vertically long shape as a whole, and both end portions thereof are edged in an arc shape, and one end portion in the width direction of the arc shape end portions is formed. The side portions each have a stepped notch shape from the tip end side.

Further, both ends of the core plate (P) are respectively located on one side in the width direction thereof, that is, on the side having the stepped notch near the base end of the notch step. Thus, circular outward bulges (15) and (15) are formed. Circular flow holes (16) and (16) are formed in the top walls of these bulges (15) and (15), respectively.
An outwardly projecting flange (16a) extends around the entire circumference of the one circulation hole (16).

On the other hand, at both ends of the core plate (P),
Relatively large outward bulges (17) (17) each having a vertically long curved shape are formed so as to occupy the entire remaining portion excluding the circular outward bulges (15) (15).
Both bulging portions (17) (17) exhibiting these longitudinally curved shapes
On the top wall of each of the through holes, there are formed through holes (18) (18) each having a shape corresponding to the shape of the bulging portion, and among these through holes, a circular outside having the flange (16a) is formed. An outwardly projecting flange (18a) extends over the entire circumference of the flow hole (18) located at the end opposite to the lateral bulge (15). These flanges (1
6a) and (18a) are tube elements (1) and (1)
Adjacent to each other and their corresponding headers (3b)
(4b) When connecting each other, the flange (16a)
The (18a) is fitted into the corresponding flow holes (16) and (18), so that the tube elements (1) and (1) are prevented from being displaced from each other. Therefore, the corresponding headers (3b) and (4b) can be securely connected in a liquid-tight state, and the heat exchanger main body (A) can be easily assembled and brazed. Since the tube elements (1) do not move relative to each other by this time, defective joints can be eliminated.

In the middle portion of the core plate (P) in the lengthwise direction excluding the above-mentioned both ends, a slit-like cutout portion (5) along the lengthwise direction is formed in the widthwise middle portion. Has been formed. The intermediate strip plate portions (19) (20) located on both sides of the cutout portion (5) sandwich the cutout portion (5) from the circular outward bulging portion (15) on the one end side to the circular outer side on the other end side. Three parallel groove grooves (19a) extending straight toward the bulging portion (15) are formed in an outward bulging shape, and a longitudinally curved outward bulging portion (17) on one end side is formed. ), Two parallel groove grooves (20a) extending straight from the other end toward the vertically curved outward bulging portion (17) are formed in the outward bulging shape. Thus, both of the intermediate strips (19)
The (20) has straight ribs (19b) (20b) protruding inwardly between the concave groove portions (19a) (20a).

One side portion in the width direction of the core plate (P), that is, the side where the stepped notch is formed is a portion which functions as the heat exchange medium flow passage (3) for the condenser (X). The other side is the side that functions as the heat exchange medium flow passage (4) for the radiator (Y).

Then, the above-mentioned two core plates (P) and (P) are superposed and joined by facing each other with the outward bulging portions (15) and (17) located outside. A piece of tube element (1) is formed. At this time, the ribs (19b) on both sides of the core plates (P) (P) that function as capacitors are provided with corrugated aluminum between their tips as shown by the solid and broken lines in FIG. The inner fins (21) made of metal are brazed and integrated in a state in which they are interposed in a plane parallel to the core plates (P) (P).

The inner fins (21) are set to have a length from the outer bulging portion (15) on one end side of the heat exchange medium flow passage (3) to the outer bulging portion (15) on the other end side. Has been done. Both end edge portions are formed in corresponding arc shapes along the inner peripheral edges of the outer bulging portions (15) and (15) as shown in FIGS. 5 and 14. On the other hand, the arcuate edge portions of the inner fins (21) are locked to the inner fin-side inner peripheral edge portions of the outer bulging portions (15) (15) of the core plates (P) (P), respectively. A pair of inwardly projecting locking bulges (15a) (15a) for restricting the movement of the fins in the longitudinal direction are formed. Therefore,
The inner fin (21) is provided in the flat tube (3a) of the heat exchange medium flow passage (3) for the condenser, and both ends of the arcuate end portions thereof are respectively engaged with the locking bulges (15a) (15a). In the stopped state, the flat tubes (3a) are disposed over the entire length and the entire area of the flat tubes (3a), and the core plates (P) and (P) which are opposed to each other are joined and integrated. Therefore, the inner fins (21) intervening inside the pair of core plates (P) (P) are prevented from being displaced in the temporarily assembled state in which they are opposed to each other, and they are integrated by brazing. After that, the flat tube (3a) of the heat exchange medium flow passage (3) for the condenser is reinforced by the inner fins (21) over the entire length and the entire area thereof to have excellent pressure resistance.

The bulging portion (15a) for locking is not limited to this embodiment in the formation position, the number or the specific shape thereof. In short, the inner portion of the flat tube (3a) is not limited to this. As long as the fin (21) can be positioned, any other design change is allowed.

The ribs (20b) of the core plates (P) (P) on the side functioning as radiators are integrated by direct brazing joints at their tips as shown by the solid and broken lines in FIG. Has been done.

Of course, two types of core plates (P) (P) in which the formation position of the rib (19b) is shifted in the width direction particularly in the portion functioning as the heat exchange medium flow passage (3) for the condenser (X). The ribs (19b) of one core plate (P) facing each other may be joined to the plane wall portion between the ribs (19b) of the other core plate (P) by using. In this case, it is possible to eliminate the risk of defective joint due to the displacement of the plate, as in the case of joining the tip portions of the ribs (19b). Therefore,
The assembling work can be roughly performed, yet the core plates (P) and (P) can be reliably joined to each other, and the strength and pressure resistance can be excellent. Also,
By adopting such a structure, the fluid diameter of the flat tube can be reduced and the heat exchange performance can be improved.

Thus, each tube element (1) is
A header (4b) for a radiator (Y) and a header (3b) for a capacitor (X) are formed at both upper and lower ends thereof, respectively, and the upper header (4b) for the radiator (Y) to the lower header (4b) are formed. 4b) a straight heat exchange medium flow passage (4) is formed in the flat tube (4a), while going from the upper header (3b) for the condenser (X) to the lower header (3b), A straight heat exchange medium flow passage (3) having inner fins (21) inside is formed in the flat tube (3a).

Thus, each tube element (1) is
As shown in FIGS. 10 to 13, the corrugated fins (2) are provided between the adjacent flat tubes (3a) (4a).
And the flat tubes (3a) and (4a) are brazed in contact with each other and the headers (3b) and (4b) adjacent to each other and the fins (2) and the flat tubes (3a) and (4a) are laminated in the thickness direction with the intervening Jointed and integrated, each header (3b)
Adjacent headers are in communication connection with each other through the flow holes (6) and (7) provided in (4b). Therefore,
A multi-layered heat exchanger body (A) in which a first heat exchanger (X) as a condenser and a second heat exchanger (Y) as a radiator are formed on both sides in the width direction of the tube element (1). ) Has been formed.

The outermost core plates (P) forming the tube elements (1) (1) on the left and right ends of the heat exchanger body (A) are, as shown in FIG. It is formed in a flat plate shape having an outer peripheral shape corresponding to (P). However, instead of such a flat plate-shaped outermost core plate (P), a bulged header or the like may be press-molded like other core plates (P).

The right outermost tube element (1)
As shown in FIGS. 1 to 4, the side surfaces of the upper headers (3b) and (4b) of the first heat exchanger (X) as a condenser and the second heat exchanger (Y) as a radiator in FIG. Inlet tubes (8) (9) for introducing refrigerant and cooling water respectively, and also a first heat exchanger (X) as a condenser and a second heat exchange as a radiator in the left outermost tube element (1). Outlet pipes (10) and (11) for discharging the heat-exchanged refrigerant and cooling water are connected to the side surfaces of the lower headers (3b) and (4b) of the container (Y), respectively.

As shown in FIG. 15, the cooling water and the refrigerant as the heat exchange medium, which have flowed in through the inlet pipes (8) and (9) provided separately from each other, flow through the inside of each tube element. In a state of being divided into one side portion side and the other side portion side, the respective widths flow from the upper side to the lower side and flow out from the outlet pipes (10) and (11) provided separately.

The refrigerant may be made to meander and flow through the tube element group in the first heat exchanger (X) that functions as a condenser. In this case, as the tube element (1) at an appropriate position, one in which the circulation hole (16) is not formed in the top wall of the circular outward bulging portion (15) of one of the core plates (P) constituting the tube element (1). It can be carried out by using or by fitting a separately formed cap to the flow hole (16).

As shown in FIGS. 1, 3, 4 and 14, an L-shaped attachment portion (25) is provided at one side edge of the upper and lower ends of the outermost core plate (P). It is extended integrally. A fan mounting stay (26) is attached to the left and right mounting parts (25) (25) at both ends by bolts (2).
It is attached in the state of being fastened and fixed in 7). The middle portion of the stay (26) is fastened and fixed with bolts (29) to the mounting members (28) fitted to the upper and lower ends of the left and right intermediate portion of the heat exchanger body (A). There is. Thus, a cooling device including a fan (C)
Are attached using the stays (26) (26).

Further, the radiator header (4b) of the heat exchanger body (A) is provided at the upper, lower, left and right ends thereof with a mounting member (3) made of a press-molded product having a corresponding cross-sectional shape.
0), (30), (30) and (30) are fitted and fixed.
Each of the mounting members (30), (30), (30), (30) has a pin (30a) protruding upward or downward, and the pin (30a) is formed on the mounting side of a vehicle body or the like. By inserting into the pin insertion hole,
The heat exchanger body (A) can be fixed to the mounting side.

In the figure, (D) is a radiator header (4
The drain part attached to b), and (F) are filler parts.

On the other hand, the corrugated fins (2), as shown in FIGS. 14, 16 and 17, both heat exchange medium flow passages (3) of the tube elements (1).
It is composed of one shared fin arranged in a manner straddling (4). And, in the widthwise intermediate portion of the fin (2), a rectangular shape that blocks heat conduction between the flat tubes (3a) (4a) of the both heat exchange medium flow passages (3) (4). A notch (2a) is formed. Therefore,
Heat conduction between the heat exchange medium flow passage (3) functioning as the condenser (X) and the heat exchange medium flow passage (4) functioning as the radiator (Y) is cut off, and one of the heat is transferred to the fin (2). It is possible to avoid the inconvenience that the heat is transferred to the other side via the and the heat exchange performance is deteriorated.

18 to 21 show a modified example of the fin. The fins (3
In 1), a long cutout portion (31a) along the length direction is formed by cutting out all the intermediate portions in the width direction, leaving only one pitch at both end portions in the length direction. The fin (41) shown in FIG. 19 has notches (41a) formed alternately in the vertical direction in the middle portion in the width direction. The fin (51) shown in FIG. 20 has a plurality of small circular holes (notches) (51a) formed in the middle portion in the width direction. The fin (61) shown in FIG. 21 has a plurality of vertically extending slits (notches) in the widthwise middle portion.
(61a) is formed.

In each of the fins (31) (41) (51) (61) shown in FIGS. 18 to 21, notches (31a) (41a) formed in the widthwise intermediate portion.
(51a) and (61a) act so as to block heat conduction between the flat tubes (3a) and (4a) of the heat exchange medium flow passages (3) and (4), respectively.

Any of the above fins (2) (31)
Even in (41), (51) and (61), one shared fin is arranged so as to straddle both heat exchange medium flow passages (3) and (4) of each tube element (1). Therefore, as compared with the case where two independent fins are used, adjacent tube elements (1) (1)
This has the effect of facilitating the work of setting the fins (2) between each other.

(Second Embodiment) FIGS. 22 to 27 show a second embodiment of the present invention.

As in the first embodiment, the multi-layer heat exchanger of this embodiment also has a radiator and a condenser integrally.

In the heat exchanger according to this embodiment,
A so-called horizontal type in which a heat exchange medium flows in the left and right directions in each tube element (1), and a plurality of horizontally elongated aluminum strip plate tube elements (1) are in a horizontal state and in a vertical direction. Are arranged in layers.

The uppermost tube element (1) constituting the above heat exchanger has an inlet pipe for introducing a refrigerant into the upper surface of the left header (3b) of the first heat exchanger (X) which functions as a condenser thereof. (8) but also the left header (4b) of the second heat exchanger (Y) which also functions as a radiator
Inlet pipes (9) for introducing cooling water are communicatively connected to the upper surface of each. Further, the tube element (1) at the lowermost stage is provided with an outlet pipe (10) for letting out the refrigerant to the lower surface of the right header (3b) of the first heat exchanger (X) which functions as a condenser, and also as a radiator. An outlet pipe (11) for drawing out cooling water is connected to the lower surface of the right header (4b) of the functioning second heat exchanger (Y).

Thus, as shown in FIG. 23, the cooling water and the refrigerant as the heat exchange medium flowing from the inlet pipes (8) and (9), which are respectively provided separately, flow in the respective tube elements. In a state of being separated into one side portion side and the other side portion side in the width direction, they respectively circulate in the left-right direction and flow out from the outlet pipes (10) and (11) provided separately.

In the first heat exchanger (X) functioning as a condenser, as shown in the same figure, the refrigerant meanders and circulates in the flat tubes (3a) of the tube element group. . In order to cause the refrigerant to meander in this way, as the tube element (1) at an appropriate position,
One of the core plates (P) which constitutes this has a circular outer bulging portion (15) without a through hole (16) formed in the top wall, or is formed separately in the above through hole (16). This can be done by fitting the caps together. When the refrigerant is meandered in this way, it is desirable to set the passage cross-sectional area to gradually decrease from the heat exchange medium passage group on the upper stage side toward the same passage group on the lower stage side.

The uppermost tube element (1) has a second heat exchanger (Y) functioning as a radiator thereof.
A filler portion (F) for injecting cooling water is provided on the upper surface of the right header (4b) of the. As shown in FIGS. 24 and 25, the filler portion (F) is placed on the upper surface of the upper bulging narrowed portion (F1) formed on the upper core plate (P) of the tube element (1). Cup-shaped filler neck (F2) integrated and joined
And are connected to each other through the openings (F1a) and (F2a) formed in the joint surface of the both.
By forming the narrowed portion (F1) in this manner, the filler neck (F2) can be easily attached.

On the other hand, the lowermost tube element (1)
Is provided with a drain portion (D) for discharging the refrigerant on the lower surface of the left header (3b) of the first heat exchanger (X) that functions as the condenser. As shown in FIGS. 26 and 27, the drain portion (D) has a downward bulging narrowed portion (D1) formed on the lower core plate (P) of the tube element (1) and a side surface thereof. And a drain cock (D2) connected in communication. Also in this case, the drain cock (D2) can be easily attached by forming the narrowed portion (D1).

Since the other construction is the same as that of the first embodiment, the corresponding portions are designated by the same reference numerals and the detailed description thereof will be omitted.

As in this embodiment, a so-called horizontal type is used,
By providing the filler portion (F) on the upper surface of the uppermost tube element (1) and the drain portion (D) on the lower surface of the lowermost tube element (1), heat is generated as in the case of a so-called vertical type. It is possible to avoid the inconvenience that air is not accumulated in the upper part of each tube element (1) at the time of injecting the exchange medium and sufficient air can not be removed, and heat is exchanged to the lower part of each tube element (1) when discharging the heat exchange medium. At the same time, it is possible to avoid the inconvenience that the medium stays. By adopting the horizontal type as described above, it is possible to increase the number of passes while preventing an increase in pressure loss and the accumulation of liquid, and it is possible to improve the performance of the heat exchanger.

In each of the above-described embodiments, the corrugated fins are used as the fins (2), but the plate fins and other various fins can be used.

Further, in any of the above-mentioned embodiments, the two heat exchangers (X) and (Y) are integrally formed in such a manner that the heat exchanger main body (A) is divided into a front surface side and a rear surface side. However, the heat exchanger main body (A) may be integrally formed so as to be divided into an upper side and a lower side.

The heat exchanger body (A) according to the present invention is not limited to the combination of the condenser and the radiator as shown in the above-mentioned embodiment, but may be, for example, an intercooler, a radiator, an engine oil cooler. It is also applicable to various combinations of a plurality of heat exchangers.

[0063]

As described above, the heat exchanger according to the present invention is provided with a plurality of strip plate tube elements, and each tube element is formed by stacking two core plates facing each other. A flat tube and a bulged header communicating with both ends of the flat tube, and a plurality of mutually independent heat exchange medium flow passages are formed,
These tube elements are stacked in the thickness direction with fins interposed between the flat tubes and the headers are joined to each other, and the heat exchange medium at a corresponding position in the adjacent tube elements. The flow passages are communicatively connected at the header so that a plurality of heat exchangers independent of each other are integrally formed. Therefore, compared to the conventional double type integrated heat exchanger in which separate and independent heat exchangers are connected by fins, the number of parts is significantly smaller, and the manufacturing efficiency can be greatly improved, thus reducing the manufacturing cost. In addition to downsizing, further downsizing and weight reduction can be achieved.

Further, by making the so-called horizontal type in which the tube elements are vertically stacked in a horizontal state, air is accumulated in the upper part of each tube element at the time of injecting the heat exchange medium as in the case of so-called vertical type. It is possible to avoid the inconvenience that sufficient air cannot be removed, and at the same time, avoid the inconvenience that the same medium stays in the lower part of each tube element when the heat exchange medium is discharged. Further, by adopting the horizontal type as described above, even when the heat exchange medium is circulated in a zigzag manner in the heat exchanger main body, it is possible to prevent an increase in pressure loss and a liquid pool, and thus, to prevent the heat exchanger from flowing. Higher performance can be achieved.

Also, by making the so-called vertical type in which the tube elements are vertically stacked in the left-right direction, the heat exchange medium can be circulated in either one of the upper and lower directions to reduce the pressure loss. it can.

As the tube element, heat exchange medium flow passages are provided on both sides in the width direction of the tube element in a mutually independent state, and one or a plurality of flat heat exchange medium flow passages are provided between the flat tubes. If a notch is used, the heat of the tubes of one heat exchanger will be conducted to the tubes of the other heat exchanger, and the heat exchange performance of one of the heat exchangers will be reduced. Avoided.

Further, the fin is composed of one shared fin arranged so as to straddle both flat tubes of each tube element, and one or a plurality of notches are provided in the widthwise intermediate portion thereof. By adopting the one formed, the heat of the tube of one heat exchanger is conducted to the tube of the other heat exchanger in the same manner as described above, and the heat exchange performance in one of the heat exchangers is reduced. The inconvenience of inviting is avoided.

[Brief description of drawings]

FIG. 1 is an overall perspective view of a heat exchanger according to a first embodiment of the present invention.

FIG. 2 is a front view of the above heat exchanger.

FIG. 3 is a plan view of the above heat exchanger.

FIG. 4 is a right side view of the above heat exchanger.

FIG. 5 is a perspective view showing a tube element of an intermediate portion which constitutes the heat exchanger main body in a separated state.

FIG. 6 is a partially omitted plan view of a core plate forming the tube element.

7 is an enlarged cross-sectional view taken along line VII-VII of FIG.

8 is an enlarged cross-sectional view taken along the line VIII-VIII of FIG.

9 is an enlarged sectional view taken along line IX-IX in FIG.

10 is an enlarged sectional view taken along line XX of FIG.

11 is an enlarged sectional view taken along line XI-XI of FIG.

12 is an enlarged sectional view taken along line XII-XII in FIG.

13 is an enlarged sectional view taken along line XIII-XIII in FIG.

FIG. 14 is a perspective view showing the outermost tube element that constitutes the heat exchanger main body, the tube element adjacent to the outermost tube element, and the corrugated fins interposed between them in a separated state.

FIG. 15 is an illustration showing a flow of a heat exchange medium.

FIG. 16 is a perspective view of a corrugated fin.

FIG. 17 is a partially enlarged vertical sectional view of the heat exchanger body.

FIG. 18 is a perspective view showing a modified example of the fin.

FIG. 19 is a perspective view showing another modification of the fin.

FIG. 20 is a perspective view showing still another modification of the fin.

FIG. 21 is a perspective view showing still another modification of the fin.

FIG. 22 is an overall perspective view of a heat exchanger according to a second embodiment of the present invention.

FIG. 23 is an illustration showing a flow of a heat exchange medium in the heat exchanger of the above.

FIG. 24 is an enlarged front view of the vicinity of a filler portion provided at the upper right end of the heat exchanger of the above.

FIG. 25 is an enlarged right side view of the vicinity of the filler portion of the above.

FIG. 26 is an enlarged front view of the vicinity of the drain portion provided at the lower left end of the heat exchanger of the above.

FIG. 27 is an enlarged left side view in the vicinity of the drain part of the same.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 tube element 2 fin 2a notch 3 heat exchange medium flow passage 3a flat tube 3b bulging header 4 heat exchange medium flow passage 4a flat tube 4b bulging header 5 notch P core plate X heat exchanger (Capacitor) Y heat exchanger (radiator)

Claims (5)

[Claims] 1. A flat plate-shaped tube element (1) comprising a plurality of strip-shaped tube elements (1), wherein each of these tube elements (1) is made flat by stacking two core plates (P) (P) facing each other. -Shaped tubes (3a) (4a) and bulging headers (3b) (3b) (4b) (4b) communicating with both ends thereof
And a plurality of heat exchange medium flow passages (3) (4) independent of each other are formed, and these tube elements (1) are provided between the flat tubes (3a) (4a). The fins (2) are interposed and the headers (3b) and (4b) are joined to each other, and the fins (2) are laminated in the thickness direction, and the corresponding positions of the adjacent tube elements (1) and (1) are The heat exchange medium flow passages (3) and (4) are connected to each other at the headers (3b) and (4b) so that a plurality of heat exchangers (X) independent from each other are provided.
(Y) is integrally configured, and is a multi-layer heat exchanger. 2. The double stack heat exchanger according to claim 1, wherein the tube elements (1) are vertically stacked in a horizontal state. 3. The double stack heat exchanger according to claim 1, wherein the tube elements (1) are vertically stacked in a lateral direction. 4. The tube element (1) has heat exchange medium flow passages (3) (4) independent from each other on both sides in the width direction, and both heat exchange medium flow passages (3) (4). 4)
4. The multi-layer laminate type according to claim 1, wherein the flat tubes (3a) (4a) are provided with one or a plurality of notches (5). Heat exchanger. 5. The fin (2) comprises one shared fin arranged so as to extend over both flat tubes (3a) (4a) of each tube element (1), and has an intermediate widthwise direction. The multi-layer heat exchanger according to any one of claims 1 to 3, wherein one or more notches (2a) are formed in the section.