Turbulence metal plate and lamination disc type heat exchanger

Abstract

To provide a turbulence metal plate 1 for a lamination disc type heat exchanger.SOLUTION: A turbulence metal plate 1 has a plurality of parallel rows 3 each having wave crests 5 and wave troughs 6 that are alternately connected to one another in a row longitudinal direction 4, where three directly adjacent rows 3 are arranged offset from one another in the row longitudinal direction 4 such that the wave crests 5 and the wave troughs 6 of the three adjacent rows 3 are arranged on straight lines 7 that extend obliquely with respect to the row longitudinal direction 4 and to which they belong.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a turbulator metal thin plate for a stacked disk type heat exchanger in the form described in the preamble of claim 1. Further, the present invention relates to a stacked disk type heat exchanger provided with at least one such turbulator metal thin plate.

[0002] Turbulator metal thin plates are already well known and serve to increase the heat transfer area between two stacked disks of a stacked disk type heat exchanger and to swirl the cooling fluid or the fluid to be cooled. Such turbulator metal thin plates provide on the one hand an enlarged surface that can be utilized for heat transfer, but in particular the improved mixing of the coolant also increases the pressure loss, which in turn often requires, for example, a pump to be made stronger and thus more expensive, which also requires more electrical energy, which is desirably kept as low as possible, especially if possible in an electric vehicle.

[0003] Therefore, in the turbulator metal thin plate of the type described at the beginning, there is always a target conflict between on the one hand the expansion of the heat transfer surface and the mixing of the coolant and on the other hand the pressure loss.

[0004] Therefore, the present invention addresses the problem of providing at least one improved or alternative embodiment that contributes to better handling the target conflict existing between the cooling output and the pressure loss, in particular for turbulator metal thin plates of the type described at the beginning.

[0005] According to the present invention, this problem is solved by the subject matter of independent claim 1. Advantageous embodiments are the subject matter of the dependent claims.

[0006] The present invention is based on the general idea of forming a turbulator metal thin plate for transferring heat from a coolant to oil, for example, in a laminated disk type heat exchanger of an electric vehicle, with wave peaks and wave valleys that are formed differently from each other and arranged differently from each other. In this case, the wave peaks and wave valleys of the turbulator metal thin plate according to the present invention are formed and arranged relative to each other so as to achieve not only high heat transfer and good mixing of the oil or coolant, but also a relatively low pressure loss. For this purpose, the turbulator metal thin plate according to the present invention has a plurality of parallel rows each having wave peaks and wave valleys connected to each other in the row longitudinal direction. At least three directly adjacent rows are arranged offset from each other in the row longitudinal direction such that the wave peaks and wave valleys of these three adjacent rows extend inclined with respect to the row longitudinal direction of these rows and are arranged on their respective straight lines. This represents a complete departure from the conventional arrangement of wave peaks and wave valleys in turbulator metal thin plates known from the prior art, and for the first time enables improved heat transfer, improved mixing of the fluid flowing through the turbulator metal thin plate, and a smaller pressure loss. This is achieved according to the present invention by the fact that the open cross section present for the flow-through is relatively large and the vortices and thus the heat transfer can be maintained high at least unchanged.

[0007] In an advantageous refinement of the turbulator sheet according to the invention, the crests and troughs of all rows are arranged on the respective zigzag lines extending transversely to the row longitudinal direction. The zigzag lines extend parallel to the flow direction of the fluid flowing through the turbulator sheet, whereby a relatively large open flow cross-section can be utilized and the pressure loss can be kept low. In this case, in experiments, it has been shown that particularly high heat transfer and thus particularly high cooling output as well as relatively low pressure loss can be achieved by the three crests or troughs arranged on each side of the zigzag line of the crests and troughs arranged on the zigzag line. Furthermore, the improved heat transfer with enhanced heat transfer enables the stacked disk heat exchanger to be configured smaller and thus more compact as a whole, which is a great advantage especially in the particularly narrow installation space situation in recent automobiles, especially recent electric vehicles.

[0008] In another advantageous embodiment of the turbulator sheet according to the invention, the turbulator sheet is manufactured by deep drawing. By means of such a deep drawing process, which has been trusted for many years in the sheet metal processing industry, especially in the automotive industry, a large number of troughs and crests can be processed into the turbulator sheet to be deformed in a single punching and deep drawing step, so that the turbulator sheet can be manufactured more quickly and thus more inexpensively.

[0009] In another advantageous embodiment of the turbulator sheet according to the invention, the turbulator sheet has a height H of 0.9 to 1.3 mm, preferably a height H of about 1.1 mm. Thereby, a significantly smaller component height is obtained compared to the turbulator sheets known hitherto on the basis of the prior art, and this component height advantageously affects the component height of the stacked disk heat exchanger configured with such a turbulator sheet.

[0010] Additionally or alternatively, the turbulator sheet metal may have a material thickness of about 0.1 mm. Due to a significantly smaller material thickness compared to turbulator sheet metals known from the prior art heretofore, the turbulator sheet metal according to the invention can not only be produced relatively easily in a forming tool in a resource-saving manner, but is also less expensive and optimized in terms of weight, which is a great advantage especially in electric vehicles.

[0011] Furthermore, the present invention is based on the general idea of providing a stacked disk type heat exchanger comprising a plurality of stacked disks each having a bottom and a circumferentially extending edge. A turbulator sheet metal corresponding to the above paragraph is arranged between at least two adjacent stacked disks. This means that, for example, in the stacked disk type heat exchanger according to the present invention, the turbulator sheet metal according to the invention and a conventional, i.e., another turbulator sheet metal, can be alternately arranged in a hollow chamber disposed between the turbulator sheet metals according to the invention. Due to the turbulator sheet metal according to the invention, the advantages described with respect to this turbulator sheet metal can be transferred to the stacked disk type heat exchanger according to the invention, and these advantages are specifically a higher cooling output based on improved vortices and a small pressure loss. Another great advantage is that, based on the increased heat transfer rate of the turbulator sheet metal according to the invention and the low pressure loss of the turbulator sheet metal according to the invention, the stacked disk type heat exchanger according to the invention for providing the same cooling output can be configured to be smaller and thus more compact, similar to another component such as a coolant pump.

[0012] In a particularly preferred embodiment of the stacked disk type heat exchanger according to the present invention, the stacked disks of the stacked disk type heat exchanger each have one inflow opening and one outflow opening, and the inflow opening and the outflow opening are formed in a parallelogram shape and each have two long sides and two short sides. The transition portion from one long side to an adjacent short side and the transition portion from one short side to an adjacent long side are rounded, that is, formed differently from the original shape of the parallelogram. Further, the two long sides may be inclined and position-adjusted with respect to each other. Further, the stacked disks may further have protrusions protruding inward or outward from the bottom of each stacked disk. Due to the inflow opening and the outflow opening formed according to the present invention, the inflow opening and the outflow opening are placed in the vicinity of the edge of the short side, whereby a relatively large distance for heat transfer is provided between the inflow opening and the outflow opening located diagonally opposite each other. In this case, the inflow opening and the outflow opening are formed so as to follow the contour with respect to the edge regarding the shape facing the edge, whereby a relatively dense arrangement of the inflow opening or the outflow opening at the belonging edge is enabled. Through the edge, the individual stacked disks are brazed to each other. Through the protrusions protruding inward or outward from the bottom, the area that can be utilized for heat transfer can be further enlarged, and such protrusions can be further arranged so as to act to reduce the pressure loss. Similarly, by the cooperation of these protrusions with the turbulator sheet in a shape-coupled manner, such protrusions can be used to position-fix the turbulator sheet arranged between two adjacent stacked disks.

[0013] In a particularly preferred embodiment of the stacked disk type heat exchanger according to the present invention, each of the stacked disks has one inflow opening and one outflow opening, each formed in an elliptical shape. The stacked disks further have projections protruding inward or outward from the bottom of each stacked disk. Regarding these projections arranged on the stacked disks, the same advantages as those of the stacked disks provided with parallelogram-shaped inflow and outflow openings can be obtained. Specifically, therefore, these advantages lie in the possible positioning of the turbulent flow metal thin plates by such projections, the expansion of the area that can be utilized for heat transfer, and the possibility of reducing the pressure loss.

[0014] For the purpose, the stacked disk type heat exchanger is configured as an oil-coolant heat exchanger having a coolant side and an oil side, and a turbulent flow metal thin plate is arranged on the coolant side, and another turbulent flow metal thin plate, which may be formed corresponding to the prior art, is arranged on the oil side. Such a stacked disk type heat exchanger formed as an oil-coolant heat exchanger can be a great advantage particularly in an electric vehicle. Therefore, this stacked disk type heat exchanger can be formed in a more compact overall configuration based on the increased cooling output, and thus not only optimizes the structural space but also is lightweight in terms of weight, which advantageously affects the cruising range of the electric vehicle. Regarding the stacked disk type heat exchanger formed as an oil-coolant heat exchanger according to the present invention, another component, for example, a coolant pump, can be manufactured smaller and with lower output, and thus not only optimizes the configuration space but also can be manufactured at a lower cost.

[0015] In another advantageous embodiment of the stacked disk type heat exchanger according to the present invention, another turbulator thin metal plate surrounds the inlet opening and the outlet opening. In particular, in the stacked disk having elliptical inlet and outlet openings, the inlet and outlet openings can be arranged at intervals with respect to the edges of the respective stacked disks, thereby creating a shorter distance between the belonging inlet and outlet openings, resulting in less pressure loss. At this time, in order to ensure high heat transfer despite this, it may be stipulated that another turbulator thin metal plate completely surrounds the inlet and outlet openings, which not only enables reliable positioning of the other turbulator thin metal plate, but also the area available for heat exchange can be significantly improved.

[0016] For the purpose, the other turbulator thin metal plate has a height H of 2.9 mm to 3.1 mm, preferably about 3.0 mm. The other turbulator thin metal plate, which is usually arranged on the oil side, may be formed corresponding to the prior art.

[0017] In a particularly preferred embodiment, the turbulator thin metal plate and / or another turbulator thin metal plate according to the present invention has a notch, and a protrusion for fixing the respective turbulator thin metal plate or another turbulator thin metal plate according to the present invention relative to the stacked disk engages within the notch. Therefore, the following advantages are obtained by the notch or protrusion according to the present invention. That is, a larger area available for heat transfer, fixing the position of the turbulator thin metal plate or another turbulator thin metal plate according to the present invention, and reduction of possible pressure loss.

[0018] Another important feature and advantage of the present invention is apparent from the dependent claims, the drawings, and the corresponding description of the drawings based on the drawings.

[0019] Of course, the features described above and the features described below can be used not only in the described combinations but also in other combinations or individually without departing from the scope of the present invention. For example, the components described above and the components described below of a higher-level unit such as a machine, device, or assembly shown individually can form separate components or elements of this unit or can be an integrated area or section of this unit even if they are illustrated differently in the drawings.

[0020] Preferred embodiments of the present invention are shown in the drawings and will be described in detail in the following description. The same reference numerals indicate the same or similar components or components that are functionally the same.

Brief Description of the Drawings

[0021]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11

[0022] Corresponding to Figs. 1 to 5 and Fig. 9, the turbulent flow metal thin plate 1 according to the present invention for the stacked disk type heat exchanger 2 according to the present invention (see particularly Figs. 5 and 9) has a plurality of parallel rows 3 having ridges 5 and valleys 6 connected to each other in the row longitudinal direction 4. Three directly adjacent rows 3 are displaced from each other in the row longitudinal direction 4 such that the ridges 5 and valleys 6 are arranged on their respective straight lines 7 extending obliquely with respect to the row longitudinal direction 4. In the case of a total of five adjacent rows 3, the middle row 3 belongs to the straight line 7 of the row 3 arranged on the right adjacent side as well as to the straight line 7 of the row 3 arranged on the left side, for example, extending orthogonally to this straight line 7.

[0023] As can be seen from Figs. 1 and 3, the ridges 5 and valleys 6 of all the rows 3 are arranged on their respective zigzag lines 8 extending in the lateral direction with respect to the row longitudinal direction 4. The flow direction 9 of the turbulent flow metal thin plate 1 according to the present invention also extends in the lateral direction with respect to the row longitudinal direction 4. In Fig. 2, the row longitudinal direction 4 extends in the plane of the drawing, while the flow direction 9 extends in a direction perpendicular to the plane of the drawing.

[0024] With the turbulent flow metal thin plate 1 according to the present invention, it is possible to achieve particularly high heat transfer and particularly effective vortices of, for example, a coolant flowing through the turbulent flow metal thin plate 1. At the same time, based on a cross section that is relatively large and open in the flow direction 9, the pressure loss can be reduced. Such a reduction in pressure loss makes it possible, in particular, to use a smaller coolant pump. This smaller coolant pump is not only simply more compactly configured, but can be manufactured at a lower cost, and at the same time requires less electrical energy for operation. Due to the heat transfer enhanced by the ridges 5 or valleys 6 arranged along the zigzag line 8 in the flow direction 9, the entire stacked disk type heat exchanger 2 can also be manufactured compactly, so that the overall structural space is optimized.

[0025] The turbulent metal thin plate 1 can be manufactured by a deep drawing process in a single common deep drawing and punching process, enabling low-cost production.

[0026] Generally, since the term "turbulent metal thin plate" represents a turbulent insert, the turbulent metal thin plate 1 described in the present application or another turbulent metal thin plate 10 (see FIGS. 5, 6, and 9) can also be manufactured from materials other than metal thin plates, particularly aluminum, plastic, etc.

[0027] The turbulent metal thin plate 1 may have a height H of 0.9 to 1.3 mm, preferably a height H of about 1.1 mm (see FIG. 2). The material thickness of the turbulent metal thin plate 1 is about 0.1 to 0.3 mm. Due to the improved heat transfer performance of the turbulent metal thin plate 1 according to the present invention, the height H of the turbulent metal thin plate 1 according to the present invention can also be reduced, thereby reducing the overall structural height of the laminated disk type heat exchanger 2 according to the present invention as well. The web 11 (see FIG. 2) connecting the peak portion 5 to the valley portion 6 may be bent at an angle of up to 78° with respect to each peak portion 5 or each valley portion 6. As a result, an almost sinusoidal path occurs from the peak portion 5 to the valley portion 6 via the web 11. The width of each row 3, that is, for example, the width B of the peak portion 5, may be 0.8 mm.

[0028] Corresponding to FIGS. 5 and 9, the laminated disk type heat exchanger 2 according to the present invention has laminated disks 12 (see FIGS. 5, 7, and 8) or laminated disks 12' (see FIGS. 9 to 11), and these laminated disks 12 or laminated disks 12' each have a bottom portion 13 and an annular edge portion 14. Through these edge portions 14, the laminated disks 12, 12' are tightly bonded to each other, for example, brazed to each other. Between two adjacent laminated disks 12, 12', the turbulent metal thin plate 1 according to the present invention and another turbulent metal thin plate 10 are alternately arranged, or only the turbulent metal thin plate 1 is arranged.

[0029] When observing the stacked disks 12 corresponding to FIGS. 5, 7, and 8, it can be seen that each of the stacked disks 12 has one inflow opening 15, one outflow opening 16, and two through openings 24. It is obvious that only one inflow opening 15 and one corresponding outflow opening 16 per stacked disk plane are used to flow through the space located between two adjacent stacked disks 12. The fluid does not flow into or out of this space through the through openings 24, but into or out of the space located above or below it. When observing the inflow opening 15 and the outflow opening 16 of the stacked disk 12 corresponding to FIGS. 5, 7, and 8, these inflow opening 15 and outflow opening 16 are formed in a parallelogram shape and have two long sides 17 and two short sides 18. It can be seen that the transition part 19 from the long side 17 to the corresponding short side 18 connected to this long side 17, and the transition part 19 from this short side 18 to the long side 17 connected to this short side 18 are rounded / formed in a round shape. Additionally, both long sides 17 extend inclined with respect to each other and are thus not parallel. Furthermore, protrusions 20 may be provided that protrude inward from the bottom 13 (see FIG. 7), that is, upward, or outward (see FIG. 8), that is, downward in the incorporated state. The protrusions 20 also serve to increase the area that can be utilized for heat transfer and to reduce the pressure loss when flowing through the space located between two adjacent stacked disks 12.

[0030] Unlike the stacked disk 12 corresponding to FIGS. 5, 7, and 8, the stacked disks 12' corresponding to FIGS. 9, 10, and 11 each have similarly an inflow opening 15' and an outflow opening 16', but the inflow opening 15' and the outflow opening 16' are formed in an elliptical shape. Here too, for each (flow) space defined by two adjacent stacked disks 12', one inflow opening 15' and a diagonally opposed outflow opening 16' are provided respectively. The through-opening 24' is used for the supply or discharge of fluid to adjacent spaces. As can be seen from FIGS. 9 to 11, the stacked disk 12' shown here also has a protrusion 20' that protrudes inward from the bottom 13, that is, upward in the incorporated state (see FIG. 11) or downward in the incorporated state, that is, outward (see FIG. 10). Each protrusion 20, 20' may have a height of about 1.4 mm.

[0031] In two adjacent stacked disks 12, 12', it is conceivable that the two protrusions 20, 20' of the two adjacent stacked disks 12, 12' are in contact with each other, or rather, are brazed to each other.

[0032] The stacked disk type heat exchanger 2 according to the present invention may be configured as an oil-coolant heat exchanger having a coolant side 21 and an oil side 22. Preferably, the turbulent flow metal thin plate 1 according to the present invention is disposed on the coolant side 21, and another turbulent flow metal thin plate 10 is disposed on the oil side 22.

[0033] When observing another turbulent flow metal thin plate 10 corresponding to FIG. 9, it can be seen that this turbulent flow metal thin plate 10 surrounds the inflow opening 15', the outflow opening 16', and the through-opening 24' of the laminated disk 12' to which it belongs. The inflow opening 15', the outflow opening 16', and the through-opening 24' are not directly arranged at the edge 14 in the laminated disk 12', but are spaced apart from the edge 14. As a result, a relatively short distance contributing to pressure loss reduction occurs between each inflow opening 15' and the outflow opening 16'. Nevertheless, in order to be able to enhance heat transfer, another turbulent flow metal thin plate 10 surrounds the inflow opening 15', the outflow opening 16', and the through-opening 24'.

[0034] The turbulent flow metal thin plate 1 according to the present invention may also have a notch 23 similar to another turbulent flow metal thin plate 10. In the notch 23, the protrusions 20, 20' of the laminated disks 12, 12' to which it belongs are engaged, thereby fixing the position of the turbulent flow metal thin plate 1 or another turbulent flow metal thin plate 10 according to the present invention. The turbulent flow metal thin plate 1 according to the present invention may be adapted in terms of its size such that this turbulent flow metal thin plate 1 is arranged between the protrusions 20 or 20' on the edge side and is held via the protrusions 20, 20'.

[0035] Another turbulent flow metal thin plate 10 may have a height H of 2.9 mm to 3.1 mm, preferably a height H of about 3 mm. Additionally or alternatively, it is conceivable that another turbulent flow metal thin plate 10 has a material thickness of about 0.2 mm. Another turbulent flow metal thin plate 10 has webs 11 oriented orthogonally to the respective crests 5 and troughs 6 as shown in FIG. 6. Naturally, the arrangement of the turbulent flow metal thin plate 1 according to the present invention on the oil side 22 is also conceivable.

[0036] The laminated disks 12, 12' themselves have a wall thickness of about 0.4 mm. As a result, they can not only be manufactured inexpensively, resource-savingly, and simply, but also have a relatively small weight.

[0037] In particular, the laminated disk type heat exchanger 2 according to the present invention and the turbulent flow metal thin plate 1 according to the present invention inserted into the laminated disk type heat exchanger 2 can achieve high heat transfer, small pressure loss, and a particularly compact structural form. This is a great advantage especially for use in electric vehicles.

Claims

1. A turbulent metal sheet (1) for a stacked disc heat exchanger (2), comprising: The turbulent metal sheet (1) has a number of parallel rows (3) each having wave crests (5) and wave troughs (6) alternately connected to each other in the row longitudinal direction (4), A turbulent metal sheet (1), characterized in that three immediately adjacent rows (3) are arranged offset from one another in the row longitudinal direction (4) such that the wave crest portions (5) and the wave trough portions (6) of the three adjacent rows (3) are arranged on respective straight lines (7) that extend obliquely relative to the row longitudinal direction (4).

2. 2. The turbulent sheet metal according to claim 1, characterized in that the wave crests (5) and the wave troughs (6) of all rows (3) are arranged on the respective zigzag lines (8) which extend transversely to the longitudinal direction (4) of the rows.

3. 3. The turbulent sheet metal according to claim 1 or 2, characterized in that the turbulent sheet metal (1) is produced by deep drawing.

4. the turbulent metal sheet (1) has a height H of between 0.9 mm and 1.3 mm, preferably about 1.1 mm; and / or 4. The turbulent sheet metal according to claim 1, wherein the sheet metal has a material thickness of about 0.1 mm.

5. A stacked disk heat exchanger (2) comprising stacked disks (12, 12') each having a bottom (13) and an annularly extending edge (14), 5. A stacked disk heat exchanger (2), in which a turbulent metal sheet (1) according to any one of claims 1 to 4 is arranged.

6. The laminated disk (12) has an inlet opening (15) and an outlet opening (16) in each case at the bottom (13), the inlet opening (15) and the outlet opening (16) being formed as a parallelogram, each having two long sides (17) and two short sides (18), the transitions (19) from one long side (17) to an adjacent short side (18) and from one short side (18) to an adjacent long side (17) being formed as rounded edges, Both of said long sides (17) are aligned at an angle relative to each other, The laminated disk (12) has a protrusion (20) protruding inwardly or outwardly from the bottom (13).

6. The stacked disk type heat exchanger according to claim 5.

7. the lamination disks (12') each have an inlet opening (15') and an associated outlet opening (16'), the inlet opening (15') and the outlet opening (16') being oval in shape, 6. The stacked disk type heat exchanger according to claim 5, wherein the stacked disk (12') has a protrusion (20') protruding inwardly or outwardly from the bottom (13).

8. 8. The stacked disk heat exchanger according to claim 5, wherein the stacked disk heat exchanger (2) is configured as an oil-coolant heat exchanger with a coolant side (21) and an oil side (22), the turbulent metal sheet (1) being arranged on the coolant side (21) and a further turbulent metal sheet (10) being arranged on the oil side (22).

9. 9. A stacked disc heat exchanger according to claims 7 and 8, characterized in that said further turbulent metal sheet (10) incorporates said inlet openings (15') and said outlet openings (16').

10. said another turbulent metal sheet (10) has a height (H) of between 2.9 mm and 3.1 mm, preferably a height H of about 3.0 mm; and / or 10. A stacked disc heat exchanger according to claim 8 or 9, characterized in that the further turbulent metal sheet (10) has a material thickness of about 0.2 mm.

11. 11. The stacked disk heat exchanger according to claim 8, wherein the turbulent metal sheet (1) and / or the further turbulent metal sheet (10) have notches (22, 23') into which the protrusions (20, 20') engage for positional fixing.

12. 12. A stacked disc heat exchanger according to claim 5, wherein the stacked discs (12, 12') have a wall thickness of about 0.4 mm.

Images