ITMI940397A1 - HEAT EXCHANGER, IN PARTICULAR SUPPLY AIR COOLER OF AN INTERNAL COMBUSTION ENGINE - Google Patents

Description

than the other, that is, seconds, channels.

Description of the finding

The invention relates, in accordance with the introductory definition of claim 1, to a heat exchanger known from US-A 4592 414. In the case known each time at the two end sides of the plates lying one above the other must be performed close to each other, respectively in pairs, inflow pipes and / or outflow pipes, respectively distributor pipes. In relation to this the distance between the plates - in the longitudinal direction of the inflow or outflow pipes to be produced - takes place mainly by means of locally hollowed plate parts, which each time - per pair of associated plates in complementary way - enclose cavities; these cavities, in the overlapping arrangement of the pairs of plates, form structures of inlet pipes, respectively outflow pipes, and communicate through openings in the portions of recessed plates, wherein local tubular connections are provided by alternative engagement of flanges in associated openings in correspondence parts of plates arranged one above the other; For the respective local separation in an inlet pipe and in an outlet pipe, recesses can be provided, each completely separable from each other, of parts of plates molded 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-receiving fluid, where these channels at their ends are respectively connected in the spatially enlarged recesses of an inflow pipe or of a outflow pipe; in relation to this, each pair of plates along common external marginal areas is 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 expensive, complicated and highly cost-impacting molding, for the plates in combination with relatively large plate wall thicknesses, in order to achieve a mechanically stable and self-supporting construction. The large wall thicknesses of the plates have, among other things, the following disadvantages: a non-optimal heat exchange (temporally reduced passage of heat); relatively large material requirement; relatively high weight. Since in the known case all the plates must be welded or brazed together, it is practically not possible a "modular exchange" or a "modular" completion, independent from the supplier, or from the manufacturer of the heat exchangers, of the heat exchanger in accordance with variable power and duty cycles of internal combustion engines; in relation thereto a "module" refers to a pair of plates.

The aim of the invention is to indicate a heat exchanger according to the introductory 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 terms of weight and in relation to this it allows inflow channels and outflow channels that can be produced in a very simple way, which are optimally sealed, with control of the thermal as well as mechanical stresses originating.

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

The invention creates a mechanically stable plate construction, in particular in the area of the inflow or outflow pipes to be produced, where the rings used are basically support means, spacer means and sealing means between the plates clamped to each other in the direction longitudinal of the inlet pipes or outflow pipes by suitable clamping means. In relation to this there is the possibility of producing single rings entirely or partially, or at least in correspondence with the front ends preparing the contact formation of the plates, of an elastic material such as rubber; such rings would preferably be arranged between those complementarily hollowed plate parts, in which the heat absorbing fluid, for example cooling water, would be to be hermetically shielded with respect to the conal structures of the matrix, which conduct the heat transferring fluid, for example very hot compressed air, and which would possibly need to be additionally sealed with respect to the external environment of the plate heat exchanger (corner zone of the plate matrix).

Within the scope of the invention, an external sealing, on the marginal and sealing side, of those pairs of shell-like and complementary plates, which form, respectively, respectively enclose channel structures for the heat absorbing refrigerant, can be provided, and which enclose the rings, respectively ring-side distributor structures, to conduct the heat-absorbing fluid like a tube, and distribute it uniformly in a targeted manner.

Said pairs of plates represent exchangeable modules, respectively, if necessary, that can be completed, of the heat exchanger. Such plate modules can be arranged on reciprocal plate parts, which are flattened with respect to the recessed parts for the rings, mutually clamped and additionally with supporting action. In correspondence with the locally flattened contact points, centering means of the plates can be provided in the form of grooves and corresponding with geometric constraint; however, it is also possible to provide a spot welding connection or a hard soldering connection at these locally flattened contact formation points.

The aforementioned construction method allows an overlapping stacking of finely welded modules, where for the production of the tubes they would only be inserted between two such modules, corresponding gasket rings and / or spacer rings. The rings, to be anchored respectively between the plates, for the inflow or outflow pipes of the matrix can be supported in a very simple way centered in position, for example by means of cavities or protrusions in the form of a groove, or rib, arranged on the parts of the plates, or bosses, respectively annular grooves or annular flanges, where the flanges can be engaged in the form of a collar in a ring.

Advantageous embodiments of the invention according to claim 1 result moreover from the characteristics of claims 2 to 18. The invention is further explained by way of example on the basis of the drawings, in which they show:

figure 1 a heat exchanger, illustrated in perspective, as well as schematically, as a plate-type charge air cooler in correlation with a clamping of the plates between external closing covers and an outline of the flow-side casing for the fluid (compressed air ) cooled outflowing from the matrix, figure 2 a shell-like structure, seen according to section II-II of figure 3, of a matrix plate with schematic representation of a tubular inversion current matrix, executable complementarily, between a pair of plates and which is connected, through openings, on the ring side, to corresponding openings of the inlet pipe, respectively of the outflow pipe,

Figure 2a is a variant seen according to II-II of Figure 3, but modified with respect to Figure 2, with respect to the arrangement of the supply pipe and the arrangement of the discharge pipe and of the matrix, here in "triple crossed counter-current construction mode" ,

Figure 3 is a partial half, shown as a longitudinal section, of the plate matrix in the construction of an inlet pipe in the combination of rings formed of metallic spacer material and a sealing material, for example rubber,

Figure 4 is a projection view, developed according to A-A of Figure 3 in the drawing plane, with an illustration respectively of an execution of openings for the supply of the heat-absorbing fluid (cooling water), carried out between a spacer ring and a plate,

figure 5 is a view corresponding contextually to figure 4 and which can be differentiated according to A-A from figure 3, however with an illustration of a second embodiment of openings, which can be respectively unilaterally conformable between the spacer rings and a plate bordering them,

Figure 6 is a variant of the plate matrix and of the execution of inflow pipes, modified with respect to Figure 3 in the sense that the metal spacer rings have, in execution of the corresponding openings, a U-shaped cross section, open unilaterally with respect to a plate,

figure 7 a variant of the plate matrix and of the design of the inflow pipes, modified in particular with respect to figure 3 in the sense that rings tightened each time between two plates of adjacent pairs of plates are made in the combination of metal spacer rings profiles with circular section ring seals,

figure 8 is a variant seen according to figures 3, 6 and 7 and modified with respect to these exemplary embodiments, in particular in the sense that all the rings have spacing and sealing qualities and from time to time between surfaces, opposite each other in the direction of 'axis of the tube, have cavities for housing integrated channels in pairs, on the side of the plates, for the heat-absorbing fluid (cooling water), figure 9 a projection view, developed according to B-B of figure 8 in the plane of the drawing, for cylindrical channels integrated in the form of pairs of plates, which can be fixed between reciprocal cavities of approximately semicircular shape of adjacent front surfaces of rings,

Figure 10 is an alternative, view according to B-B of Figure 8, of Figure 9 for channel cross sections, here for example hexagonal, integrated as a pair of plates, which can be enclosed between reciprocal cavities of approximately trapezoidal shape of adjacent front surfaces of rings,

Figure 11 is a partial detail of the matrix, shown longitudinally sectioned, of the heat exchanger, according to which, for example, the respective spacer ring is located in an annular cavity, respectively annular pocket, which are respectively formed between parts of complementarily shaped plates and with openings, and

12 is a longitudinal section, enclosing channel structures, of a pair of plates illustrated with a removable, outer marginal side, rubber locking gasket as a means of connecting the plates.

According to figure 1, the plates 1, 2, arranged one on top of the other like a stack, of the heat exchanger can be mutually clamped between an upper and a lower closing cover D, respectively D ', with interposition of strips support L, preferably along the front and rear corner zones. The tightening can take place with bolts, of which the relative bolt heads are indicated with S. in the upper closing cover D. Through the opening 5 'the heat absorbing fluid, for example cooling water, fed according to the arrow K, reaches through the inflow pipe 7 into the first channels 4, which are enclosed, or incorporated, respectively in a pair of plates 1, 2. On the outflow side the first channels 4 are connected to the outflow pipe 7 ', from which the cooling water is heated as a consequence of the heat exchange with the fluid giving off heat added, in particular air V very hot of the supercharging compressor (see also figure 2), flows out of 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 hermetically welded to each other on complementary flanged edges U, respectively U '(see also Figures 3, 6, 7, 8); Preferably, a radius / crease roll welding can be used, but a high temperature resistant hard baring can also be used.

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

Figure 2 is to be understood according to section II-II of Figure 3, where the respective first channels 4 are conducted with an inversion of the current direction (arrow ST), so that together with the indicated current direction V, V 'of the heat transferring fluid , which as very hot charge air flows through the respective second channels 3, there is a heat exchanger crossed in countercurrent; consequently in this case through the field Fd (figure 2) of first channels 4 originating between a pair of plates 1, 2 from complementary cavities respectively, a matrix of U-shaped plate tubes is formed, projecting transversely with respect to the inlet pipe and to the outflow pipe 7, 7 'respectively; it is connected on the inlet side (arrow F) with the inlet pipe 7 (figure 2) and on the outlet side (arrow F ') with the outlet pipe 7'.

Figure 2a illustrates a concept of use, possible in the field of the invention, of the plate heat exchanger in triple cross-countercurrent construction mode with substantially diagonally opposite arrangement of the inflow pipes and outflow pipes 7, respectively 7 ' , to be carried out between and on the plates 1, 2. In relation to this there is a matrix with channels articulated in three sections of tube fields Fdl, Fd2, Fd3 mutually crossed in the opposite direction, which matrix is connected on the input side (F ) through corresponding rings 9 with the inlet pipe 7 and, on the outlet side (F ') through corresponding rings 9, with the outflow pipe 7'. Contrary to the arrangement according to Figures 1 and 2, according to Figure 2a, for example, the inlet into the inlet pipe 7 is intended to be arranged at the top and the discharge of the outlet pipe 7 'is to be understood as arranged at the bottom. Moreover, the functions and operating modes of Figure 2a correspond to the nomenclature of the reference marks already used in Figure 2.

With simultaneous design, for example of the inlet pipe 7 - practically identical with the respective design of the outlet pipe - the plates 1, 2 are basically supported against each other on rings and are clamped in the longitudinal direction of the pipes, whereas in the figures 3, 4 and 5 there is a combination of rings 8 made of an elastic material such as rubber and metal spacer rings 9. A respective pair of weldable plates 1, 2 - as mentioned - on the side of the edges (U, U ') contains the spacer ring 9, which through openings 10 is in connection with the first channels 4 of the matrix; starting from supporting parts 11, 12 on the marginal side and mutually flattened, the pairs of plates 1, 2 form, between parts 13, 14 shaped in an enlarged and complementary way (axially in relation to the axis of the tube), the air spaces Z, in which the rings 8 provide a sealing, tightened on the plate side, with respect to the other channels 3 and also with respect to the external environment. The expandedly shaped plate parts 13, 14 contain openings 5 of the inlet pipe 7, which are respectively surrounded by rings 8, respectively 9. Along the supporting parts 11, 12, spot welding or possibly a brazing connection.

A welded pair 1, 2 of plates represents an optionally exchangeable or, if necessary, completable module. The slots 10, 10 'respectively, of the spacer rings 9 (Figures 4 and 5) are formed by cavities, open towards a front surface of ring and counter surfaces, bordering on their respective open sides, of the respectively shaped part 13; the slots 10 thus made have in Figure 4 a transversal section partially - on the internal side - approximately semicircular in shape and continuing from there towards the outside approximately in a square shape; in figure 5 the slots 10 'have a quadrangular cross section; the ring strips left between the openings 10, 10 'end with an obtuse joint angle relative to the extension of the part 13.

In the case of relatively small sheet thicknesses for the plates 1, 2 approximately <0.5 mm, and with relatively small required clamping forces, a mechanically stable plate construction can thus be created, which at the necessary points is optimally sealed (cooling water / very hot air). Any offset of the plates, as a cause of thermal stresses or temperature changes or mechanical stresses, can be corrected in a very simple way by means of an easy subsequent tightening; this also applies in conjunction with the remaining examples (Figures 6 to II).

As illustrated in particular in conjunction with Figures 3, 4 and 5, in the further configuration the respective height H of a cutout 10, 10 'respectively, must be made <2/3 of the maximum radial wall thickness D of the spacer ring 9 and the width B of the cutout 10 must be made <5 mm; in conjunction with this, the current flow surface respectively determining for a cavity can preferably be dimensioned in an order of magnitude of at most 1/20 of the narrowest current flow cross section of an opening 5 of an inlet pipe or of an outflow pipe 7, respectively 7 '.

Figure 6 differs from Figures 3, 4 and 5 in the sense that the respective spacer rings 15, which are arranged inside a pair of plates 1, 2 which can be welded on the edge side, have a U-shaped cross section here opened unilaterally in the longitudinal direction of the inflow channel 7; in relation to this, the spacer rings 15 have transversal slots 16 extending up to a free support wing thereof, through which the inflow pipe 7 is connected, in correspondence with the respective spacer ring 15, with the first channels 4 of the matrix . The aforementioned "free" ends of the support wings rest in each case firmly on the first part of the shaped plate 13. In the case of relatively high form stability, such spacer rings 15 lead to a not insignificant weight reduction.

Figure 7 differs from Figures 3 to 5 due to the fact that instead of the rings 8 (Figure 3) made of rubber or an elastic material such as rubber, rings 16 are provided in the combination of a spacer ring and a seal, which contain, in circumferential grooves on the front side, gasket rings 16 "made of rubber or Teflon, which, with local crushing, rest hermetically on the corresponding counter surfaces of the shaped plate parts 13, 14. during a profiling P of the surface enlarging the passage of heat in correspondence with the contour of the ring, it is possible to achieve at the same time a highly effective cooling of this annular combination 16 ', 16 ", and more precisely through the heat exchange of the water of cooling, conveyed through the inlet pipe 7, with the very hot compressor air supplied by the supercharger (channels 3 in Z).

Figures 8, 9 and 10 show a heat exchanger embodiment, in which all the rings 17 between the plates 1, 2 are produced as elements simultaneously transmitting and sealing forces, for example of a hard rubber ; in relation to this, a pair of plates 1, 2 conforming respectively to first channels 4, respectively 4 'is fixed between front surfaces of the ring opposite each other in the axis direction of a pipe to be produced, for example inlet pipe 7; in relation to this, the complementarily shaped parts 13, 14 starting from the mutually flattened supporting parts 11, 12 are located one above the other partially and, with the openings 5, directly; partially the rings 17 enclose, in complementary cavities 18 (figure 9), respectively 19 (figure 10), contained between opposite front surfaces, the channels 4 (figure 9), respectively 4 '(figure 10) contained between shapes of plates surrounded in correspondingly, which in Figure 9 have a circular cross section, respectively cylindrically, and in Figure 10 they have a polygonal cross section, for example, in this case, hexagonal.

In all the types of embodiments discussed up to now it is advantageously possible that the parts of a pair of plates 1, 2, starting from the support parts 11, 12 locally flattened, ending after one end side, respectively on the corner side, in direction on connecting flanges Q, U 'in the form of a strip, likewise enclose channel structures 20 of the matrix; these can also be connected for example to the inlet pipe 7 through openings in the rings, respectively in correspondence with the rings.

In the embodiment example according to Figure 11, respective pairs of plates 1, 2 enclose - in relation to the overlapping arrangement of the corresponding openings 5, for example of an inlet pipe 7 - annular-shaped pockets T, in which rings 20 are respectively arranged spacers; these are connected, in correspondence with mutually opposite circumferential areas, through openings 21, with the first channels 4, integrated on the plate side, of the matrix. In the locally spacing execution of the interspace Z for the second channels 3 of the matrix, further rings 22 are provided - comparable with the rings 16 'of figure 7 - which, with the inclusion of further sealing rings 16 "or sealing cords, are supported on ring surfaces, which are formed by parts 13, 14 locally shaped in the form of a ring or hollowed out of the plates 1, 2; the first openings 5 terminate respectively in annular flanges 23 which engage, with a centering action, in the rings 22. Reference 24 indicates in figure 11 means for centering the rings 20; in relation to this, they can be molded ribs, bosses or similar.

Also in the examples already mentioned and indicated in particular in Figures 3 to 9 the rings 8, respectively 16 ', respectively 17, can be incorporated in annular pockets which are shaped by the shaped plate parts 13, 14.

According to Figure 12, instead of a local sealing connection by brazing or welding along the outer edges U, U 'of the pairs 1, 2 of plates, a sealing-locking connection 25 can be provided; in relation to this, the outer edges U, U 'conforming to mutual coupling and support surfaces, have rounded protruding jaws 26, 27, which surround a partial circumference of a ring or of a cord 28 in the form of rubber; a fixing tube 29 slotted unilaterally surrounds the cord 28 and engages the jaws 26, 27 in an embracing manner with reciprocal clamping in the manner of a pincer of the outer edges U, U '.

The invention can also be used in a plate heat exchanger, in which inflow pipes and / or outflow pipes arranged one next to the other parallel at a distance are preferably formed in the two end regions of the plate matrix; in relation to this, for example, channels 4 locally separated from each other can be traversed in a mutually opposite direction in respective tubular fields and can be connected respectively, on the inlet side, to an inflow pipe and, on the outlet side, to a delivery pipe outflow.

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

Claims (18)

Claims 1. Heat exchanger, in particular the charge air cooler of an internal combustion engine, the matrix of which consists of plates (1, 2) arranged one on top of the other in the form of a stack, which enclose channels (3; 4), separated from each other, for two fluids that participate in the heat exchange, and which by means of openings (5) in complementarily shaped parts (13, 14) shape inflow and outflow pipes (7, 7 '), which are respectively in connection with the first channels (4) of the matrix, characterized by the fact that the inflow tubes and the outflow tubes (7, 7') consist of rings (8, 9) tightened in a hermetic way between the shaped parts (13, 14), which, in different planes of distance, perform a fluidic connection with the first channels (4) or a fluidic interception with respect to the second channels (3) of the matrix. 2. Heat exchanger according to claim 1, characterized in that respectively a pair of plates (1, 2) in the form of a shell, preparing the first channels (4) of the matrix between complementary shapes, has plates, which along edges ( U, U ') reciprocal are brazed, or welded to each other hermetically. 3. Heat exchanger according to claim 1 or 2, characterized in that rings (8, 17) are made, at least partially, of rubber or an elastic material such as rubber and intercept the fluidic connection between an inlet pipe or an outflow pipe (7, 7 ') and the other channels (3) contained in cavities (Z) between the shaped parts (13, 14) of the plates. 4. Heat exchanger according to one or several of claims 1 to 3, characterized in that the rings (8, 9) are arranged in the respective shell lining of the openings (5) contained in the shaped parts (13, 14) plates, an inlet pipe or outflow pipe (7, 7 ') between the plates (1, 2). 5. Heat exchanger according to one or more of claims 1 to 4, characterized in that metal rings (9, 15) are incorporated in a pair of plates (1, 2) respectively enclosing the first channels (4) of the matrix , which through openings or slots (10, 10 ', 16) are in connection with the first channels (4). 6. Heat exchanger according to claim 5, characterized in that the openings or slots (10,10 ', 16) are made between open cavities along a front surface of a ring (9, 15) and flat counter surfaces of a shaped part (13) of the plate, where the remaining strips between the cavities rest, enclosing an obtuse joint angle, on the part (13) of the plate. 7. Heat exchanger according to claim 5 or 6, characterized in that the respective height (H) of a cutout (10, 10 ') is selected <2/3 of the maximum radial wall thickness (D) of the respective ring ( 9) and the cutout width (B) is chosen <5 mm, where the current crossing surface prepared respectively by a cutout (10, 10 ') or by a channel (4-Figure 9) is dimensioned to a maximum of 1 / 20 of the current crossing cross section, respectively narrower than the inlet pipe or outflow pipe (7, 7 '). 8. Heat exchanger according to claim 5, characterized in that the metal rings (15) have a U-shaped cross section, one-sided open in the longitudinal direction of an inlet or outlet pipe (7, 7 '), with transverse openings (16) terminating in correspondence with the free support wings and which are connected to the first channels (4). 9. Heat exchanger according to claim 3, characterized in that the ring produced, at least partially, of rubber is a rubber ring surrounded on the outer circumference by a metal ring. 10. Heat exchanger according to claim 1, characterized in that the inlet pipe (7) is traversed by a current of heat-receiving cooling fluid, wherein respectively a metal ring (16 '), intercepts the inlet pipe ( 7) compared to very hot fluid in the second channels (3), on the internal circumference it is equipped with a surface profiling (P) which increases the thermal passage and rests, by means of gasket rings (16 ") or gasket cords, inserted in circumferential grooves, on counter surfaces of adjacent plates (2, 1). 11. Heat exchanger according to claim 1, characterized in that in each case two rings (17), mutually following each other in the direction of the pipe axis and formed as supporting force-transmitting and sealing elements, of an inflow pipe or outflow pipe (7, 7 ') surround shapes, correspondingly contoured in complementary cavities (18, 19) contained between reciprocal front surfaces, of a pair (1, 2) of plates and which together perform the first channels (4, 4 '). 12. Heat exchanger according to one or several of claims 1 to 11, characterized in that the pairs of plates (1, 2) at the end regions of the matrix starting from supporting parts (11, 12), executing reciprocal contact surfaces, execute the plate parts (13, 14), respectively complementarily shaped, for the rings, where the pairs (1, 2) of plates between the supporting parts (11, 12) enclose channel structures ( 20) on the marginal side respectively complementarily shaped and which can be fluidically stressed through the rings (9, 15. 13. Heat exchanger according to claim 12, characterized in that the pairs (1, 2) of plates are spot-welded or brazed on the supporting parts (11, 12). 14. Heat exchanger according to claim 12, characterized in that the pairs (1, 2) of plates mutually engage each other in a sealing and centering way at the supporting parts (11, 12). 15. Heat exchanger according to one or several of claims 1 to 14, characterized in that the spacer rings and / or the sealing rings are centered, by means of cross-members, bosses, grooves, projections or the like in correspondence with the respective mating surfaces of the shaped parts (13, 14) of the plates. 16. Heat exchanger according to one or several of claims 1 to 15, characterized in that the first rings (20) are respectively incorporated in ring-shaped pockets (T), which are formed between parts, complementarily recessed, of a pair of plates (1, 2). 17. Heat exchanger according to one or several of claims 1 to 16, characterized in that the openings (5) of a pair of plates (1, 2) at least on one shaped side of the plate are connected in annular flanges (23) axial, which engage respectively in a spacer and / or gasket ring (22). 18. Heat exchanger according to claim 1, characterized in that the pairs of plates (1, 2) are removably connected to each other along mutual external edges (U, U ') by means of a rubber locking gasket (25).