ITMI940396A1 - HEAT EXCHANGER, IN PARTICULAR SUPPLY AIR COOLER OF AN INTERNAL COMBUSTION ENGINE - Google Patents

Description

openings in the shaped parts form the distributor tube; moreover spacer rings must have openings and must enclose an annular space in common in each chamber, which at the two ends borders with elastically deformable sealing means, which intercept the distributor pipe, during the tightening of the plates, axial with respect to the tube, on the coupling surfaces located outside the chambers, with respect to the second channels.

Description of the finding

The invention relates to a heat exchanger according to the introductory definition of claim 1. In such a heat exchanger, known from US-A 4.592.414, each time at the two end sides of the plates arranged overlapping must be executed next to each other respectively in pairs of inflow pipes and / or outflow pipes, respectively distributor pipes. In relation to this, the spacing of the plates takes place - in the longitudinal direction of the inflow pipes, respectively outflow pipes, to be produced - by means of locally shaped plate parts in such a way that - for a pair of complementarily assembled plates - they come to creating grooves, which, in an overlapping arrangement of the pairs of plates, communicate fluidly through mutual openings of the tubes; in connection therewith, local pipe connections can be provided by alternative engagement of flanges in associated pipe openings; For the local separation, respectively, in an inlet pipe and in an outlet pipe, recesses, respectively entirely separable from each other, can be provided for a pair of plates of molded plate parts in the form of a nib.

In the known case, each pair of plates encloses one or two channels (single-current conduction or two-current conduction) for the heat absorbing fluid, where these channels in their ends are respectively connected in the recesses of an inflow pipe or an outflow pipe; in relation to this, each pair of plates along common external marginal areas has the plates supported, respectively supported, one against the other in the form of a flange, respectively of a strip.

The known case requires an expenditure of deformation, respectively molding, which is expensive, complicated and strongly incident in relation to the costs, for the plates in combination with relatively large wall thicknesses of the plates, in order to achieve a mechanically stable and self-supporting construction. The large wall thicknesses of the plates present, among other things, the following disadvantages: a non-optimal heat exchange (temporally reduced thermal passage); relatively large material requirement; relatively high weight. Since in the known case all the plates must be welded or brazed together, a "modular exchange" or a "modular" completion, independent of the supplier, or manufacturer of heat exchangers, of the heat exchanger in accordance with variable cycles of power and work of internal combustion engines; in relation thereto a "module" refers to a pair of plates.

In the known case, locally targeted sealing arrangements are also not implemented in order to seal sections of an inflow pipe or outflow pipe, crossed by a heat-absorbing fluid, in an optimal way with respect to duct sections crossed by heat-releasing fluid, of the matrix or with respect to the external environment. It is possible to slightly improve the aforementioned requirements with regard to airtightness only by means of molding contours (flange engagement in openings) which are reciprocally extremely precise and strongly incident in relation to costs.

Furthermore, the complete welding of the plates of the known case leads to a pack of plates which is relatively rigid in itself, so that mechanical stresses, for example resulting from impact stresses of the vehicle or from temperature stresses, respectively alternating temperature stresses and differences in temperature. Local expansion of the thermally conditioned materials can only be insufficiently controlled (risk of material cracks, respectively of the weld seams, as well as danger of settling, i.e. failure; of the resulting airtight plates).

The object of the invention is to indicate a heat exchanger according to the definition of claim 1, which, in the presence of a comparatively small manufacturing and material expenditure (small molding / thin plate expenditure) is relatively light in in terms of weight and in relation to this, it allows inflow and outflow distributor pipes to be produced in a very simple way, which, with mastering of temperature and mechanical stresses, which arise, are optimally sealed.

The set task is solved according to the invention by means of the peculiarities in the characterizing part of claim 1.

The two spacer rings each spaced apart in the chamber, respectively in the annular chamber, of a pair of plates, create, in the presence of relatively small plate wall thicknesses, a plate construction which is stable in terms of strength and supported each other. against the other, where a comparably large surface support, and broad in terms of contour, is possible through the chambers in the longitudinal direction of the pipe, between the mutual coupling surfaces, respectively support.

In conjunction with the use and arrangement of the elastically deformable sealing means, or a respective sealing ring, for example of rubber, in combination with an axial clamping of the plates with respect to the tubes, settling phenomena can be compensated in a sealing manner of thermally and / or mechanically conditioned plates, without having to take on the largest losses of clamping force. Therefore, in the case of the invention there is an "elastically tightened" gasket, where a pure metallic spacing is ensured through the rings in correspondence with the coupling, respectively supporting, respectively corresponding surfaces of the plate parts, with a constant clamping force.

The design and arrangement of the annular space in the respective chamber, relative to the complementarily surrounded arrangement, on the side of the plates, of the elastically deformable sealing ring, respectively, between two ring ends, enables optimum cooling of the gasket ; this is advantageous, in particular in relation to the design of the inflow-side distributor pipes, in relation to the relatively marked differential temperatures between the heat-absorbing cooling fluid (cooling water) and the heat-releasing fluid (very hot charge air).

As a result of the slots, respectively openings, contained in the two spacer rings, a uniform distribution, taking into account the requirement, of the heat absorbing fluid for example (on the inflow side) from the inner ring into the annular space can be made possible and, from there , on the first channels of the matrix.

With regard to the reduced manufacturing and construction costs, it is also advantageous that the prepared chamber and the first channels connected thereto of the matrix can be produced respectively at the same time from an assembled pair of plates.

The single pairs of plates can be construction units connected each time by themselves externally welded, or brazed together on the marginal side, which, if necessary, can be exchanged or completed; alternatively, the pairs of plates themselves can be connected in each case on the marginal side in a removable and hermetic way, so that a replacement or subsequent equipping of modular construction units of single plates is possible relatively simply and quickly.

Advantageous conformations of the invention according to claim 1 result moreover from the characteristics of claims 2 to 13. The invention is further explained by way of example based on the drawings, in which they show:

1 a heat exchanger illustrated in perspective, as well as schematically, as a plate charge air cooler in correlation with a clamping of the plates between external closing covers and a casing contour, outflow side, for the fluid (air tablet) cooled, effluent from the matrix,

Figure 2 a partial half, illustrated as a longitudinal section, of the plate matrix with the first and second channels, as well as in the execution of a distributor tube of respectively two spacer rings incorporated in a chamber of a pair of plates,

figure 3 a partial section according to III of figure 2, and

figure 4 an internal structure, seen according to section IV-IV of figure 2, of a plate of the matrix with schematic illustration of first channels, which can be complementarily executed between a pair of plates and pipes in reverse current, for a counter-current heat exchanger cross, where the first channels are connected, on the inflow side or on the outflow side, to chambers with the respective two rings.

According to Figure 1, the plates 1, 2 of the heat exchanger, arranged one on top of the other in the manner of a stack, can be mutually clamped between an upper and a lower closing lid D, respectively D ', by interposition of support strips L, preferably along the anterior and posterior corner areas. The tightening can take place with bolts, the relative screw heads of which are indicated with S. D. Heat-absorbing fluid, for example cooling water, conveyed through the opening 5 'according to the arrow K reaches, through the distributor pipe 7, in the first channels 4, which are respectively incorporated in a pair of plates 1, 2 On the outflow side, the first channels 4 are connected to the other distributor pipe 7 ', from which the cooling water is heated, as a consequence of the heat exchange with the heat transferring fluid, in particular very hot supercharging air V, respectively of the compressor (see also Figure 4), flows from the opening 5 "according to the arrow K '. Following the external contour lines R in Figure 1, the pairs 1, 2 of plates can be welded together in a hermetic manner on opposing flanged supporting parts 11, 12 (see also Figure 2); preferably, a radius / crease roller welding can be used, but a heat-resistant hard brazing or a locking gasket 8 can also be used - as shown in Figure 2 -.

The plates 1, 2 can be made of steel, steel and copper or aluminum. They form interspaces Z, in which second channels 3 are produced by means of corrugated sheet metal inserts W, extending transversely with respect to the first channels 4, respectively 4 '(Figures 2 and 3), into which second channels the heat transferring fluid is conducted, in particular, very hot charge air V, which flows from the matrix according to V '(see also figure 4) at a clearly reduced temperature, to be fed, through an opening in the casing G, as charge air to the respective combustion engine internal.

According to figures 2 and 3, pairs of plates 1, 2 arranged respectively one above the other, form - starting from reciprocal supporting parts 9, 10 figure 3, respectively 11, 12 - chambers 13, in which two metal spacer rings 14, 15 and one after the other in the axis direction of the pipe. The chambers 13 are formed here between parts, respectively approximately half cup-shaped, of the respective pairs of plates 1, 2. In correspondence with plate parts, extending transversely with respect to the axis of the distributor tube 7, of on the inflow side, of the chambers 13 an elastic sealing of the distributor tube 7 takes place with respect to the external environment (here: left side of the plate matrix) and with respect to the second channels 3. For example by means of a rubber ring 16 takes place this sealing between mutual mating surfaces, approximately annular in shape, of the plate parts mentioned above; in relation to this the rubber ring 16 is covered by annular sections 17, 18, complementarily shaped approximately half of these plate parts. Respectively at the height of these annular sections 17, 18 ends an annular space 19 enclosed by two spacer rings 14, 15 in the chamber 13. The two spacer rings 14, 15 have slots 20, 21 extending in a common transverse plane. As can also be seen from Figure 2, the plate parts mentioned above, and containing the annular sections 17, 18 with gasket ring 16, of axial flanges 22, 23 arranged overlapping and angularly bent to each other, each time on one side engage in an internal spacer ring 14. The axially traversed portion of the distributor pipe 7 is then prepared by the respectively internal spacer rings 14 and by the tubular connections originating through the axial flanges 22, 23. Cooling fluid (Figure 1) conducted according to K can thus be distributed, according to the arrow directions indicated (Figure 2) through the slots 20 of the inner ring 14 on the annular space 19, and from there, through the slots 21 of the outer ring 15, from the respective chamber 13 it can be conveyed to the first channels 4, respectively 4 '.

The respective "first channels" are constituted, on the one hand, by cylindrical and axially short distributing channels 4, which are respectively half formed by 'profiled parts 24, 24' (Figure 3) complementarily shaped with respect to the supporting parts 9, 10 reciprocal, as well as from time to time parts of the circumferential wall axial with respect to the tubes for half of the cup chamber 13; the distributor channels 4 lead into further channel structures 4 ', which are here performed on the side, opposite to the chamber 13, of the supporting parts 9, 10 between parts 25, 25', expanded in the shape of a shell, of a pair of plates 1, 2.

As can also be seen from Figure 2, the plate parts, extending transversely with respect to the axis of the tube, form, for the centering support of the spacer rings 14, 15, annular cavities with axial annular coupling surfaces between the annular sections 17 , 18 complementarily shaped and the axial flanges 22, 23 on one side and parts of the circumferential wall axial with respect to the tubes of a chamber 13 on the other side.

Along the protective parts 11, 12 tangent to each other on the external marginal side, a sealing and removable locking connection 8 can be provided; in relation to this, parts of widened ends, rounded outwardly in the form of a tongue, of the supporting parts 11, 12 approximately half surround a sealing cord 26, for example of rubber, whereas a tubular locking strip 27 compresses the support parts 11, 12 in the manner of a pincer and in relation thereto surrounds with a clamping action the sealing cord 26 and the end parts in the form of a tab reciprocally.

Figure 4 represents an alternative use of the invention, seen according to IV-IV of Figure 2, for a plate heat exchanger, in particular a charge air cooler, in the crossed counter-current construction mode. In relation to this there is a tube field, with the first channels 4, in the shape of a u, incorporated respectively between pairs of plates 1, 2 and projecting transversely with respect to the axes of the inflow-side and outflow-side distributor pipe 7 , 7 '. Under the inversion of the current direction (arrow St) the field of the first channels 4 is crossed, in the area with straight wings, with mutually opposite directions and, on the inflow side (arrow F) it is connected to a distributor pipe 7 and , on the outflow side (arrow F '), is connected to the other distributor pipe 7', through the respective chambers 13. For the execution of the air spaces Z for the second channels 3 (Figures 1 and 2) the plates 1, 2 in figure 4 on the right side can be mutually supported on moldings in the manner of blocking the plates. Substantially transversely with respect to the corresponding field of channels 4, in the air spaces Z the channels 3 are traversed by the heat transferring fluid, for example very hot supercharging air, respectively air from the compressor, according to the arrow V; through an outflow part of the body G the charge air lowered in temperature following the heat exchange can thus flow through an opening in the body, according to the arrow V ', and be fed to the internal combustion engine.

The invention can also be used, for example, in a plate exchanger in triple cross countercurrent construction mode, with substantially diagonally opposite arrangement of the supply distributor pipes and of the outflow distributor pipes 7, respectively 7 ', to be shaped between and above the plates 1, 2. In relation to this there is a matrix of channels that can be decomposed into three sections of fields of channels crossed reciprocally in countercurrent, which matrix is connected, on the inlet side, through corresponding rings, with the inflow distributor 7 and, on the outlet side, through corresponding rings, with the outflow distributor tube 7 '. Contrary to the arrangement according to Figures 1 to 4, the inlet into the inflow distributor pipe 7 can be arranged at the top and the discharge of the discharge distributor pipe 7 'can be arranged at the bottom. The invention can also be used, for example, in a plate heat exchanger, in which preferably in the two end regions of the plate matrix inflow distributor pipes and / or discharge distributor pipes arranged parallel at a distance from the close to each other; in relation to this, for example, channels 4 separated from each other locally in respective tube fields between pairs of plates can be traversed with mutually opposite directions and can be connected respectively on the inlet side to an inflow distributor pipe and, on the outlet side, on an outflow distributor tube.

The characteristics described above and / or illustrated graphically are, if not already expressly claimed, also an integral part of the invention.

Claims (12)

Claims 1. Heat exchanger, in particular the charge air cooler of an internal combustion engine, with a matrix of plates (1, 2) arranged one above the other like a stack, which form channels (3 , 4, 4 '), separated from each other, for two fluids participating in the heat exchange, as well as at least one distributor pipe (7), which on the inflow or outflow side is connected with the first channels (4, 4 ') and is intercepted with respect to the second channels (3), characterized by the fact that plates (1, 2) respectively connected to each other in a hermetic way, in pairs, in the external marginal area enclose, between shaped parts complementarily, chambers 13 connected with the first channels (4, 4 '), in which respectively two spacer rings (14, 15) form, between reciprocal coupling surfaces and openings of the shaped parts, the distributor tube (7), and from the fact that the two spacer rings (14, 15) have slots ure (20, 21) and together enclose in each chamber (13) an annular space (19), which in the two ends borders with elastically deformable sealing means (16), which interdict the distributor channel (7), in the course of the clamping of the plates, axial with respect to the tubes, in correspondence with the coupling surfaces, located outside the chambers (13), with respect to the second channels (3). 2. Heat exchanger according to claim 1, characterized in that the pairs (1, 2) of plates are hermetically connected to each other in planes, respectively extending transversely with respect to the axes of the pipe, on supporting parts (11, 12 ) external reciprocal, and enclose the first channels (4, 4 ') between profiled parts (24, 24'; 25, 25 ') and complementarily shaped plates, on whose input side, respectively output side, the plates (1, 2) are shaped approximately half enlarged respectively in the chamber (13). 3. Heat exchanger according to claim 1 or 2, characterized in that the other channels (3) are arranged, in a transversal direction with respect to the first channels (4, 4 '), in cavities (Z), which are respectively left in the stack of plates between those parts of the plates (1, 2), which run in pairs, and surround, the first channels (4, 4 '). Heat exchanger according to one or more of claims 1 to 3, characterized in that at least one sealing ring made of rubber is provided as the respective sealing means (16), which is sheathed in each case for half by complementarily shaped annular sections (17, 18), which are contained in plate parts, superimposed on each other transversely to the axis of the tube, for the chambers (13). 5. Heat exchanger according to one or more of claims 1 to 4, characterized in that openings respectively arranged overlapping the complementarily shaped plate parts in the chambers (13), in the execution of tubular flanges each time (22 , 23) axial, bent angularly with opposite reciprocal direction, engage in the internal spacer rings (14). 6. Heat exchanger according to one or more of claims 1 to 5, characterized in that the respective pairs of plates (1, 2) are shaped, starting from mutual coupling and support surfaces, complementarily in the form of a cup or muffler, in the execution of the chambers (13). 7. Heat exchanger according to one or more of claims 1 to 6, characterized in that the spacer rings (14, 15) with their front side ends are arranged in plate parts, shaped lowered in the manner of ring on both sides of a common sealing ring (16), of a chamber (13). 8. Heat exchanger according to one or more of claims 1 to 7, characterized in that the slots (20, 21), respectively openings, in the two spacer rings (14, 15) are arranged approximately at the height of the first channels (4, 4 ') of the matrix. 9. Heat exchanger according to one or more of claims 1 to 8, characterized in that the pairs of plates (1, 2) enclosing the chambers (13) and the spacer rings (14, 15) are brazed or welded on the marginal side . 10. Heat exchanger according to one or more of claims 1 to 8, characterized in that the pairs of plates (1, 2) enclosing the chambers (13) and the spacer rings (14, 15) are removably connected to each other on the marginal side by means of a sealing connection (8). 11. Heat exchanger according to one or more of claims 1 to 10, characterized in that the respectively outer spacer ring (15) is arranged, at least for a part of its circumference, in the chamber (13) in the direction transversal with distance from the opposite wall of the chamber, through which the first channels (4) are fluidically connected to the chamber (13). 12. Heat exchanger according to claims 4, 5 and 7, characterized in that the plate parts respectively extending transversely with respect to the axis of the tube and supported on reciprocal annular coupling surfaces, for the centering support of the spacer rings (14, 15) inside the chambers (13) form lowered ring-shaped cavities with annular coupling surfaces between the complementarily shaped annular sections (17, 18) and the axial flanges (22, 23) on one side, and wall parts circumferential axial to the tubes of a chamber (13) on the other side.