Heat exchanger plate for high-pressure refrigerant

Abstract

Heat exchanger plate (1, 20, 30) for high-pressure refrigerant in a plate-fin heat exchanger divided into adjacently arranged inlet tank and outlet tank, comprising at least one channel support plate (2) with parallel open channels (14, 15) present in at least one of the surface areas (3, 4) and at least one cover plate (5) that can be soldered thereto and / or a further channel support plate, wherein the channel support plate (2) has on one exchanger insertion end face (6) an insertion area (9) divided into inlet area (7) and outlet area (8) for insertion into the adjacently arranged inlet tank and outlet tank divided heat exchanger and on the other end face (10) has a free area (11), wherein in at least one of the two surface areas (3, 4) two flat, parallel channel parallel fields (12, 13) each with parallel directed, surface-side open channels (14, 15) are arranged next to each other, which are connected to each other in the free area (11) via a third flat channel arc field (16) with curved, likewise surface-side open channels (17), wherein in each case a parallel channel (14, 15) from the parallel channel parallel fields (12, 13) a curved channel (17) of the channel arc field (16) is assigned for continuous channel guidance, wherein the channels (14, 15) closed by the cover plate (5) or another channel support plate (21, 22) are connected to one another in the respective surface area of ​​a channel support plate (2, 21, 22, 23) by introduced transverse barriers (28) across several channels within the channel parallel fields (12, 13) in such a way that the high-pressure refrigerant can partially flow alternately between the closed channels, whereby heat transfer and pressure equalization in the high-pressure refrigerant over the cross section of the channel support plate(s) (2, 21, 22, 23) takes place, wherein the transverse barriers (28) are arranged so that they span several channels (14, 15).

Description

[0001] The invention relates to a heat exchanger plate for high-pressure refrigerant in a plate-fin heat exchanger divided into adjacently arranged inlet tank and outlet tank.

[0002] The R774 refrigerant in heat exchangers in vehicle air conditioning systems is under very high pressure. To overcome the limitations caused by the extreme wall thickness required for single-channel refrigerant tubes, extruded multi-channel tubesheet technology is traditionally used. This involves extruding thin aluminum plates with parallel, small-diameter channels for the refrigerant flow. This technology allows the production of tubes with the required strength and walls that are not too thick.

[0003] One problem, however, is that the extrusion process limits the channel arrangement to parallelism, which is not necessarily the best possible arrangement in terms of improved heat transfer and flow control. Furthermore, extruded multi-channel tube sheets are expensive.

[0004] In particular, these two problems are also present in the three plate-based heat exchangers described below.

[0005] A device for heat transfer is described in the document DE 101 10 828 A1, in which the heat transfer from a first fluid to a second fluid separated from the first fluid is carried out with a stack-shaped or shell-shaped structure comprising at least two layers, in particular plates, wherein each layer comprises a heat transfer region which has numerous channels, an inlet region arranged upstream of the heat transfer region in the flow direction and an outlet region arranged downstream of the heat transfer region in the flow direction, wherein the inlet region and / or outlet region comprises at least one support element.

[0006] One problem is that the channels of a plate are aligned parallel to each other, and the corresponding inlet and outlet areas of the channels on each plate are largely diagonally opposite each other. The supply from the inlet to the channels and the outlet from the channels in the layers are reinforced with support elements to prevent possible material distortion and material changes within the plate, which, however, is detrimental to the refrigerant flow rate.

[0007] A similar heat exchanger for a carbon dioxide vehicle air conditioning system is described in the document DE 100 35 939 A1. It is provided with a channel through which a high-pressure refrigerant flow flows, and a second channel through which a low-pressure refrigerant flow is separated from the first channel. The first and second channels each have a plurality of small channels formed in or on individual heat transfer plates, and several layers of heat transfer plates are connected to one another. The heat transfer plates, with their parallel channels, are placed on top of one another and soldered such that the channels of one plate are closed by the flat surface of the adjacent plate placed on top. The channels of the adjacent plates, each with carbon dioxide flowing through them at different pressures, can be offset from one another or have different channel cross-section dimensions.

[0008] One problem is that soldering the adjacent heat transfer plates is complicated.

[0009] Furthermore, a hand-brazed plate heat exchanger and a transcritical cooling system are described in the document DE 11 2004 002 637 T5, in which heat is transferred between a first fluid and a second fluid, wherein the first fluid is pressurized and wherein the hand-brazed plate heat exchanger comprises the following: - a plurality of plate pairs, each plate pair enclosing a plurality of parallel flow channels extending from a first inlet opening to a first outlet opening, each of the flow channels having a hydraulic diameter of less than one millimeter, the plate pairs being arranged as a stack, the first inlet openings being aligned with each other to define a first inlet manifold for distributing the first fluid to the flow channels, and the second openings being aligned with each other to define a first outlet manifold for collecting the first fluid from the flow channels, - a plurality of turbulator plates interlocked between the plate pairs for defining flow paths for the second fluid, each of the turbulator plates being sandwiched between the plate pairs to provide structural support thereto, and - Reinforcements extending between each of the plate pairs, aligned with the first inlet and outlet openings, and defining the first inlet and outlet manifold between the plate pairs.

[0010] One problem is that additional air ribs are arranged between the plates, which requires more material.

[0011] In summary, all three plate-containing devices also have the problem that the channel-guiding plates are designed in such a way that they have openings - inlet openings and / or outlet openings - through which they are connected to each other and through which the refrigerant flows in the microports on the plates are formed.

[0012] US 2003 / 0 037 908 A1 describes a cooling device for cooling a refrigerant.

[0013] DE 195 28 116 A1 describes a heat exchanger with a sandwich structure made of several plates stacked on top of each other, at least one of which is provided with openings forming flow channels.

[0014] WO 02 / 066 918 A1 describes a heat exchanger for use in motor vehicles or for industrial applications, e.g. a heat exchanger for use as an evaporator, condenser, oil cooler, charge air cooler, heater cores, etc.

[0015] The invention is therefore based on the object of providing a heat exchanger plate for high-pressure refrigerants which is designed in such a way that an improvement in heat transfer and flow guidance can be achieved.

[0016] The problem is solved by the features of patent claim 1.

[0017] The heat exchanger plate for high-pressure refrigerant in a plate-fin heat exchanger divided into adjacently arranged inlet tank and outlet tank has, according to patent claim 1 at least one channel support plate with parallel open channels in at least one of the surface areas and at least one cover plate that can be soldered thereto and / or a further channel support plate, wherein the channel support plate has an insertion area divided into an inlet area and an outlet area on one exchanger insertion end face for insertion into the heat exchanger divided into adjacently arranged inlet tanks and outlet tanks and a free area on the other end face, and that in at least one of the two surface areas, two flat, parallel channel parallel fields, each with parallel channels open on the surface side, are arranged next to one another, which are connected to one another in the free area via a third flat channel arc field with curved channels that are also open on the surface side,wherein a curved channel of the channel arc field is assigned to each parallel channel from the parallel channel parallel fields for continuous channel guidance, wherein the channels closed by the cover plate or another channel support plate in the respective surface area of ​​a channel support plate are connected to one another by introduced transverse barriers across several channels within the channel parallel fields such that the high-pressure refrigerant can partially flow alternately between the closed channels, whereby heat transfer and pressure equalization in the high-pressure refrigerant takes place across the cross section of the channel support plate(s), wherein the transverse barriers are arranged such that they span several channels.

[0018] The channel support plate can preferably have a thickness d B which, compared to the thickness d A of the cover plate is larger.

[0019] The open channels can be installed in a channel support plate of 0.7 mm to 1.2 mm thickness. B be incorporated and the cover plate has a thickness d A from 0.25 mm to 0.45 mm.

[0020] A plug-in recess is provided between the inlet area and the outlet area, which separates the channel parallel fields when the multi-channel tube plate is inserted into an inlet tank and outlet tank of the heat exchanger, whereby the inlet area and the outlet area transition from an initial constriction into an expansion up to the channel parallel fields.

[0021] The heat exchanger plate can consist of two channel support plates which are mirror-symmetrical and are soldered together in contact with the open corresponding channels on the surface areas, whereby the thicknesses d B the channel support plates are the same or different.

[0022] The heat exchanger plate can have a channel support plate with open channels on both surface areas, wherein the two surface areas are each closed with a soldered cover plate.

[0023] The channels closed by the cover plate or another channel support plate can be connected to one another in the respective surface area of ​​a channel support plate by means of introduced transverse barriers across several channels within the channel parallel fields in such a way that the high-pressure refrigerant can partially flow alternately between the closed channels, whereby heat transfer and pressure equalization in the high-pressure refrigerant occurs over the cross section of the channel support plate(s).

[0024] The open channels can be embossed, rolled or milled in the surface area of ​​a channel support plate.

[0025] The invention will be explained in more detail using several embodiments and several drawings.

[0026] They show: Fig. 1 an exploded and perspective view of a first heat exchanger plate according to the invention for high-pressure refrigerant comprising a channel support plate and a cover plate spaced therefrom, Fig. 2 an enlarged section of the channel support plate of the heat transfer plate according to the invention in plan view according to Fig. 1, Fig. 3 a longitudinal section of a channel support plate with guided channels with a spaced cover plate according to Fig. 1, Fig. 4 a longitudinal section through a second heat exchanger plate according to the invention comprising two opposing, corresponding open channels and Fig. 5 a longitudinal section through a third heat exchanger plate according to the invention with a centrally arranged channel support plate with open channels on both surfaces and solderable cover plates that can be attached on both sides.

[0027] The following are the Fig. 1 to 3 considered together.

[0028] In Fig. 1 shows a schematic representation of a heat exchanger plate 1 for high-pressure refrigerant for insertion into a plate-fin heat exchanger (not shown) divided into an inlet tank and an outlet tank, wherein the heat exchanger plate 1 has at least one channel support plate 2 with parallel open channels 14, 15 present in a surface region 3 and a cover plate 5 that can be soldered thereto, wherein the rear surface region 4 is optionally designed without channels.

[0029] The channel support plate 2 has, on one exchanger insertion end face 6, an insertion area 9 divided into an inlet area 7 and an outlet area 8 for insertion into the heat exchanger divided into adjacently arranged inlet tank and outlet tank, and a free area 11 on the other free end face 10, wherein in the surface area 3 two flat, parallel channel parallel fields 12, 13, each with parallel channels 14, 15 that are open on the surface side, are arranged next to one another, which are connected to one another in the free area 11 via a third flat channel arc field 16 with curved channels 17 that are also open on the surface side, wherein a curved channel 17 of the channel arc field 16 is assigned to each parallel channel 14, 15 from the parallel channel parallel fields 12, 13 to form a continuous channel guide.

[0030] The cover plate 5 is intended to cover the channel support plate 2 and close the open channels 14, 15.

[0031] The open channels 14, 15 are in a channel support plate 2 of preferably 0.7 mm to 1.2 mm thickness d B incorporated and the cover plate 5 can have a thickness d A from 0.25 mm to 0.45 mm.

[0032] Between the inlet area 7 and the outlet area 8, a plug-in recess 29 is provided in order to be able to plug the channel support plate 2 into a heat exchanger consisting of an inlet tank and an outlet tank, which are adjacent, wherein the inlet area 7 and the outlet area 8 of the channel support plate 2 pass from a frontal constriction 31 into an extension 32 up to the channel parallel fields 12, 13, which is also shown in an enlarged section in plan view in Fig. 2 after Fig. 1 is shown.

[0033] The channel support plate 2 has a thickness d Bwhich, compared to the thickness d A of the cover plate 5 may be larger, as in Fig. 3 is shown in a longitudinal section before soldering the channel support plate 2 to the cover plate 5.

[0034] A second heat exchanger plate 20 according to the invention can also, as in Fig. 4, consist of two channel support plates 21, 22, which are mirror-symmetrical and have open corresponding channels on the mutually associated surface areas 26, 27 and are soldered to each other in a contacting manner, wherein the thicknesses d B21 , d B22 the channel support plates 21, 22 equal to d S21 =d B22 or differently with d B21 ≠d B22 can be.

[0035] A third heat exchanger plate 30 according to the invention can furthermore, as in Fig. 5, alternatively have a channel support plate 23 with open channels present on both surface areas 24, 25, wherein the two surface areas 24, 25 can each be closed with a soldered cover plate 51, 52.

[0036] In the case of a heat exchanger plate 1 according to the invention modified with respect to the channel parallel fields 12, 13, as for example additionally in Fig. 2, in a special embodiment, the channels 14, 15 closed by the cover plate 5 or another channel support plate can be connected to one another in the respective surface area of ​​a channel support plate 2 by means of transverse barriers 28 such that the high-pressure refrigerant can partially flow alternately between the channels closed by the transverse barriers 28, whereby heat transfer and pressure equalization in the high-pressure refrigerant takes place over the cross section of the channel support plate(s) 2.

[0037] This is also useful for reducing the adverse effects of mechanical blockage of channels or similar cases.

[0038] In the case of the channel support plates belonging to the respective heat exchanger plate 1, 20, 30 according to the invention, the open channels 14, 15 in the surface area(s) 3, 24, 25, 26, 27 of a channel support plate(s) 2, 21, 22, 23 can be optionally embossed, rolled or milled.

[0039] The advantage of the heat exchanger plate 1, 20, 30 according to the invention is that the channels 14, 15 closed by soldering can be designed for maximum mechanical strength as well as maximum heat transfer and maximum flow efficiency. List of reference symbols 1 heat exchanger plate 2 first channel support plate 3 first surface area 4 second surface area 5 first cover plate 6 Transformer insertion face 7 Entrance area 8 Outlet area 9 Insertion area 10 free front side 11 free area 12 first channel parallel field 13 second channel parallel field 14 parallel channels 15 parallel channels 16 Canal arch field 17 curved channel 20 second heat exchanger plate 21 second channel support plate 22 third channel support plate 23 fourth channel support plate 24 Surface area 25 Surface area 26 Surface area 27 Surface area 28 Transverse lock 29 Plug-in recess 30 third heat exchanger plate 31 Constriction 32 Extension 51 second cover plate 52 third cover plate d B Thickness of a duct support plate d AThickness of a cover plate

Claims

[1] Heat exchanger plate (1, 20, 30) for high-pressure refrigerant in a plate-fin heat exchanger divided into adjacently arranged inlet tank and outlet tank, comprising at least one channel support plate (2) with parallel open channels (14, 15) present in at least one of the surface areas (3, 4) and at least one cover plate (5) that can be soldered thereto and / or a further channel support plate, wherein the channel support plate (2) has on one exchanger insertion end face (6) an insertion area (9) divided into inlet area (7) and outlet area (8) for insertion into the adjacently arranged inlet tank and outlet tank divided heat exchanger and on the other end face (10) has a free area (11), wherein in at least one of the two surface areas (3, 4) two flat, parallel channel parallel fields (12, 13) each with parallel directed, surface-side open channels (14, 15) are arranged next to each other, which are connected to each other in the free area (11) via a third flat channel arc field (16) with curved, likewise surface-side open channels (17), wherein in each case a parallel channel (14, 15) from the parallel channel parallel fields (12, 13) a curved channel (17) of the channel arc field (16) is assigned for continuous channel guidance, wherein the channels (14, 15) closed by the cover plate (5) or another channel support plate (21, 22) are connected to one another in the respective surface area of ​​a channel support plate (2, 21, 22, 23) by introduced transverse barriers (28) across several channels within the channel parallel fields (12, 13) in such a way that the high-pressure refrigerant can partially flow alternately between the closed channels, whereby heat transfer and pressure equalization in the high-pressure refrigerant over the cross section of the channel support plate(s) (2, 21, 22, 23) takes place, wherein the transverse barriers (28) are arranged so that they span several channels (14, 15). [2] Heat exchanger plate according to claim 1, characterized by that the channel support plate (2) has a thickness (d B) which, compared to the thickness (d A ) of the cover plate is larger. [3] Heat exchanger plate according to claim 2, characterized by that the open channels (14, 15) are formed in a channel support plate (2) of 0.7 mm to 1.2 mm thickness (d B ) are incorporated and the cover plate (5) has a thickness (d A ) from 0.25 mm to 0.45 mm. [4] Heat exchanger plate according to claims 1 to 3, characterized by that a plug-in recess (29) is provided between the inlet region (7) and the outlet region (8), which plug-in recess separates the channel parallel fields (12, 13) when the channel support plate (2) is inserted into an inlet tank and outlet tank of a heat exchanger, wherein the inlet region (7) and the outlet region (8) transition from an initial constriction (31) into an expansion (32) up to the channel parallel fields (12, 13). [5] Heat exchanger plate according to claim 1, characterized bythat it consists of two channel support sheets (21, 22) which are mirror-symmetrical and are soldered together in contact with the open corresponding channels on the surface areas (26, 27), wherein the thicknesses (d B ) of the channel support plates (21, 22) are the same or different. [6] Heat exchanger plate according to claim 1, characterized by in that it has a channel support plate (23) with open channels present on both surface areas (24, 25), wherein the two surface areas (24, 25) are each closed with a soldered-on cover plate (51, 52). [7] Heat exchanger plate according to claims 1 to 6, characterized by that the open channels (14, 15) in the surface area (3, 24, 25, 26, 27) of a channel support plate (2, 21, 22, 23) are embossed, rolled or milled.

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