Plate-shaped heat exchanger for a cooling device comprising at least one heart exchanger package

Abstract

The invention relates to a plate-shaped heat exchanger for a cooling device comprising at least one heat exchanger package, in particular for a motor vehicle, consisting of a plurality of openings for accommodating a pipe conducting a coolant, wherein each opening is surrounded by an passage and a plurality of projections are distributed between the passages for the heat exchange with the medium to be cooled. In order to allow a high performance increase of a cooling device, yet a low increase in pressure loss of the charge air, a plurality of projections are arranged around an passage, wherein the projections have a shape that assures deliberate heat conduction from the projections to the passage.

Claims

1. A plate-shaped heat exchanger for a cooling device comprising at least one heat exchanger package, wherein the heat exchanger package comprises a plurality of openings for accommodating a tube conducting a coolant, wherein each opening is surrounded by a rim hole and a plurality of projections are distributed between the rim holes for heat exchange with the medium to be cooled, wherein a plurality of projections are arranged around a rim hole, wherein the projections have a shape which ensures a targeted heat conduction from the projection to the rim hole, wherein the ends of the projections are arranged approximately circularly around the rim hole and extend orthogonally away from the rim hole, wherein a turbulator or spacer is arranged between adjacent rim holes, wherein the turbulator or spacer supports a heat exchanger package situated above, wherein a bead is arranged between adjacent rim holes in an edge region of the plate-shaped heat exchanger, wherein the edge region comprises a corrugation.

2. The heat exchanger as claimed in claim 1, wherein the projection is of circular segment-like design.

3. The heat exchanger as claimed in claim 2, wherein the width and/or the length and/or the height of the circular segment-like projection and/or the spacing between two adjacent circular segment-like projections and/or the spacing of the circular segment-like projection to a rim hole depends on the heat conduction to be achieved from the circular segment-like projection to the rim hole.

4. The heat exchanger as claimed in claim 2, wherein the circular segment-like projections are arranged in two or more rows around the rim hole.

5. The heat exchanger as claimed in claim 1, wherein there extends along the longitudinal extent of at least one projection a first material overhang which enables air exchange in the direction of the rim hole and in particular the width of the projection and/or the height of the projection and/or the depth of the projection depends on the heat conduction to be achieved from the projection to the rim hole.

6. The heat exchanger as claimed in claim 1, wherein the projections are subdivided into at least two groups which are arranged around the rim hole in such a way that each group is positioned at a spacing from a line which runs approximately centrally through the rim hole and extends perpendicularly to an edge of the heat exchanger.

7. The heat exchanger as claimed in claim 1, wherein the rim hole has, at a spacing from the surface of the heat exchanger, a crown tulip for receiving a heat exchanger situated above it.

Description

(1) The invention permits numerous embodiments. Some of them will be explained in more detail with reference to the figures illustrated in the drawing, in which:

(2) FIG. 1 shows a charge-air cooler according to the prior art,

(3) FIG. 2 shows a first plate-shaped heat exchanger according to the prior art,

(4) FIG. 3 shows a second plate-shaped heat exchanger according to the prior art,

(5) FIG. 4 shows a third plate-shaped heat exchanger according to the prior art,

(6) FIG. 5 shows a plate-shaped heat exchanger with circular segment-like projections,

(7) FIG. 6 shows a plate-shaped heat exchanger with ray-like projections,

(8) FIG. 7 shows a cross section through a projection configured as a gill,

(9) FIG. 8 shows a plate-shaped heat exchanger with projections configured as gills,

(10) FIG. 9 shows a plan view of a plate-shaped heat exchanger with ray-like projections configured as gills,

(11) FIG. 10 shows a second plate-shaped heat exchanger with ray-like projections configured as gills, and

(12) FIG. 11 shows an edge region of the plate-shaped heat exchanger.

(13) Identical features are denoted by identical reference signs.

(14) FIG. 5 shows a detail of a plate-shaped heat exchanger 2 having circular segment-like projections 10 which enclose the opening 7. The circular segment-like projections 10 here form a circle around the opening 7. As can be seen from the various FIGS. 5a, 5b and 5c, the dimensions of the circular segment-like projections 10 here can be chosen to be very different. FIG. 5a discloses circular segment-like projections 10, where each circular segment-like projection 10 covers approximately an angle of 90. FIG. 5c here shows circular segment-like projections which are substantially shorter than the circular segment-like projections according to FIGS. 5a and 5b. As illustrated in FIG. 5b, the circular segment-like projections 10 can also be arranged in multiple rows around the opening 7. Each circular segment-like projection 10 here represents a stamped-out portion which is arranged around the opening 7, wherein each opening 7 is surrounded by a circular rim hole 4.

(15) By virtue of the charge air 6 which originates from a combustion engine and is conducted through the plate-shaped heat exchangers 2 which are stacked above one another and form a package, the heat contained in the charge air 6 is passed to the circular segment-like projections 10. The circular segment-like projections 10 here serve not only as heat exchangers but also simultaneously as turbulence generators, the laminar air flow of the charge air 6 being converted into a turbulent air flow. This conversion has the advantage that a good heat supply to all circular segment-like projections 10 takes place. As a result of the circular arrangement of the circular segment-like projections 10 around the rim hole 4 and thus the opening 7, a new incoming flow of the charge air 6 takes place to generate the turbulences at each circular segment-like projection 10, thereby improving the heat exchange from the circular segment-like projection 10 to the opening 7. The shape of the circular segment-like projections 10 produces an increase in their area, which is accompanied by an increased heat absorption from the charge air 6. Since the circular segment-like projections 10 also have openings (not shown further), for example in the form of slots, a transverse exchange of the charge air 6 between the different plate-shaped heat exchangers 2 which are arranged above one another is ensured. Consequently, in spite of an inhomogeneous flow against the plate-shaped heat exchangers in the cooling device, an improved heat exchange is achieved between charge air and coolant which flows through round tubes (not shown further) which are inserted into the openings 7.

(16) Instead of the circular segment-like projections 10, other stamped-out portions, for example in the form of ellipses, are also possible around the rim holes 4.

(17) FIG. 6 illustrates a plate-shaped heat exchanger 2 which has ray-like projections 11. As can be seen from FIGS. 6a to 6c, these ray-like projections 11 are also arranged circularly around the rim hole 4 and thus around the opening 7. The ray-like projections 11 have an elongate design, with the narrow ends 12 of the ray-like projection 11 being arranged opposite the rim hole 4 and being guided directly up to the rim hole 4. The ray-like projections 11 here have slots in their longitudinal direction, with material overhangs 13 protruding out of the ray-like projections 11. In FIG. 5b, the ray-like projections are formed as so-called gills 15. The number of the projections 11 in FIG. 5a and of the gills 15 in FIG. 5b is in this case different depending on the size of the ray-like projections 11 or the gills 15.

(18) In FIG. 6c, the ray-like projections 16 are not, as in FIG. 6a, formed rectilinearly, but have a slight curvature. The ray-like projections 11, 15 or 16 serve as heat exchangers in that they absorb the heat supplied from the charge air 6 and transport it in the direction of the rim hole 4, the round tube (not shown further) flowing with the coolant through the rim hole 4. These projections 11, 15 and 16 arranged in a ray-like manner here have the particular advantage that the heat conduction is directed directly to the opening 7 and thus to the round tube, with no interruptions in the heat conduction being present as a result of structural components situated in between.

(19) FIG. 7 illustrates a cross section through a gill 15 as is worked out from the plate-shaped heat exchanger 2. Here, the gill 15 protrudes with its first material overhang 13 above the upper side of the plate-shaped heat exchanger 2, whereas the second material overhang 14 of the gill 15 is directed in the direction below the plate-shaped heat exchanger 2. Owing to this simple design, a very good transverse exchange of the charge air between the different plate-shaped heat exchangers 2 is possible.

(20) As can be seen from FIG. 8, these ray-like projections in the form of gills 15 can vary in a structurally simple manner in their design. This concerns the width (arrow A in FIG. 8a) and equally the depth (arrow B in FIG. 8b) and also the height, which is identified by the arrow C in FIG. 8c. As a result of these variations, the flow conditions at the ray-like projections 11, 15 and 16 improve, thereby leading to a better heat conduction and thus to an improved performance capability of the cooling device. The angle of the gills 15 also contributes to better heat transfer. The heat conduction here is ensured all the better the larger the number of the projections 11, 16 or gills 15 for each rim hole 4.

(21) FIG. 9a illustrates a detail of a plan view of a plate-shaped heat exchanger 2 which has openings 7 arranged in rows, wherein each opening 7 is surrounded by a rim hole 4. Whereas the centrally arranged rim holes 4 are completely surrounded by ray-like projections 11, the rim holes 4 in the edge region 17 are only approximately half-surrounded by the ray-like projections 11. Spacers 8 are situated in the edge region 17 between the rim holes 4 on the side opposite to the ray-like projections 11. These spacers 8 have the task of stabilizing the edge region 17 against mechanical stresses. FIG. 9b once again illustrates a detail around an opening 7 with a rim hole 4 which are surrounded by the ray-like projections 11. Here, the ray-like projections 11 are all arranged with the same spacing in a circle around the opening 7.

(22) FIG. 10 shows a second illustration of a plate-shaped heat exchanger 2 in which, as can be seen from FIG. 10b, the ray-like projections 11 are subdivided into two groups 18a, 18b. In each group 18a, 18b, the ray-like projections 11 here have an identical spacing from one another, wherein the spacing AB of the two groups 18a, 18b from one another is greater than the spacing of the ray-like projections 11 within a group 18a, 18b. As can be seen from FIG. 10a, a gap 19 thus extends between the groups 18a, 18b and is used to cut to size the plate-shaped heat exchangers 2 from a strip, the structure of the plate-shaped heat exchangers 2 remaining uninfluenced during the cutting-to-size process.

(23) In the case of the variants explained in connection with FIGS. 9 and 10, a performance increase of the heat transfer of approximately 10% is ensured with a pressure drop increase of approximately <50% of the charge air 6. Consequently, the growing performance requirements in cooling devices are ensured.

(24) FIGS. 11a to 11d illustrate different measures for increasing the strength of the edge region 17 of the plate-shaped heat exchangers 2. Owing to the heat supplied with the charge air 6, vibrations result in the edge region of the plate-shaped heat exchangers 2, these vibrations possibly leading to cracks and consequently to instabilities of the edge region 17. Such instabilities can be prevented if, as illustrated in FIG. 11a, the edge region is reduced up to the first row of the rim holes 4 (arrow F).

(25) A second measure for improving the stability of the edge region 17 comprises incorporating a bead 20 close to the edge region 17 between two adjacent rim holes 4 (FIG. 11b).

(26) Another improvement in the stability of the edge region 17 is achieved if the entire edge region 17 has a corrugation, thereby ensuring a stability against cracks, this being illustrated in FIG. 11c.

(27) A turbulator or a spacer 8 which is arranged between two adjacent rim holes 4 (as illustrated in FIG. 11d) also contributes to improving the strength of the edge region 17.

(28) For all the variants explained, it holds that the material used for the plate-shaped heat exchangers 2 is aluminum, stainless steel, copper or the like. The density of the plate-shaped heat exchangers 2 described in a package can here be made variable, and equally the longitudinally and transversely dividing arrangement of the rim holes 4 of the plate-shaped heat exchangers 2 is variable. A use of the plate-shaped heat exchangers 2 described is in this case not only possible in a charge-air cooler, but is also conceivable in exhaust-gas coolers, in evaporators or radiators.

(29) By means of the device described, a high performance increase in the heat exchange of the cooling device is possible. Here, a reduced pressure drop increase of the charge air is ensured and a mechanical stability of the edge region against vibrations is provided.