EP1843115B1 - Core type radiator with change of flow direction - Google Patents

Description

The invention relates to a heat exchanger according to the preamble of claim 1.

Heat exchangers of known design have a tube / rib block, which consists of pipes or flow passages through which a first fluid can flow and ribs which can be flowed over by a second fluid. Tubes and ribs are in heat-conducting connection; For example, they are soldered or mechanically connected. The tubes have over the block protruding pipe ends, which each open into a collection or distribution box, ie communicate with this on the first fluid. The first fluid, for. B. a coolant is supplied to the heat exchanger via a connecting piece (inlet nozzle) and withdrawn after flowing through the tube / rib block via a second connecting piece (outlet nozzle) again. As it flows through the tube / fin block, heat is transferred from one fluid to the other via the fins. For example, air flows through the tube / fin block, which is heated by the coolant. The tube / fin block generally has a plurality of tubes, e.g. As round tubes or flat tubes, which can be arranged in one or more rows. Depending on the intended use of the heat exchanger, the tubes can be hydraulically connected in parallel, ie all flowed through in the same direction, or individual pipe groups can be connected in series, so that they are flowed through successively and the fluid covers a longer path in the heat exchanger. The deflection of the fluid flow, which from a Pipe group exits, takes place in the collection boxes, which have divided by partitions diverting chambers. A deflection of the fluid flow can either transversely to the second fluid flow, for. B. an air flow - it is then called a deflection in the width of the heat exchanger - or in or against the flow direction of the second fluid (air flow) - one then speaks of a deflection in depth. In this case, an at least two-row or two-pipe arrangement of the tubes or flow channels is required. A double-flow design with deflection in the depth can be realized for example by a flat tube with inner partition. By deflecting the first fluid flow in the heat exchanger, different outlet temperatures for the second fluid flow can be achieved. For example, the air flow emerging from the heat exchanger, which is heated by the coolant, receives a specific temperature stratification or a desired temperature profile.

In heat exchangers for motor vehicles, eg. As radiators of a heating and air conditioning, such a temperature stratification is desired: So should the emerging from the radiator in the upper air cooler and the exiting air in the lower area to be warmer. The cooler air is supplied to the head area of the vehicle occupant and the heat air to the foot area of the vehicle occupant. Moreover, in today's vehicles a so-called right / left separation, i. H. independent heating of the driver and front passenger side usual.

By the DE 33 17 983 C1 The applicant has been known such a radiator for a motor vehicle heating system, which has a right / left separation. The radiator is divided into two blocks, which are supplied from a common flow with coolant, but each have their own return with flow control. This allows the flow in each sub-block (for right or left) to be set independently, thereby individually controlling the air temperature for the driver and front-passenger sides.

By the DE 43 13 567 C1 a radiator for a right / left control was known. The known radiator has additional means to produce a temperature stratification in the above sense (cool head - warm feet). For this purpose, transversely extending distribution pipes are provided both in the lower and in the upper collecting box of the radiator, which effect a different loading of the radiator pipes and thus a stratification of the air temperature. The known heating system is referred to as a water-regulated system, since the air temperature is adjusted via the regulation of the coolant throughput. In air-controlled systems, the coolant flow rate is not regulated, but hot and cold air streams are brought by mixing to the desired temperature.

By the DE 101 58 436 A1 a radiator with partial flow deflection and the features of the preamble of claim 1 has been known.

It is an object of the present invention to achieve a predetermined temperature profile for the exiting fluid flow (secondary flow) for a heat exchanger of the type mentioned above with simple means, wherein beyond an independent control of sub-blocks should be possible.

This object is solved by the features of claim 1. According to the invention, it is provided that the first fluid flow supplied to the heat exchanger can be deflected both in width and in depth, not in succession but simultaneously. This means that the incoming fluid flow is divided into a first partial flow, which is deflected in depth, and a second partial flow, which is deflected in width. Thus, the advantage is achieved that at least two different temperature zones are created for the exiting fluid flow in a relatively narrow space, namely, a first, warm zone from the fluid inlet to the division and deflection of the fluid flow, a second, approximately lukewarm zone, which adjacent to the warm zone is placed, and in a third, cold zone. For the deflection in the depth of a double-row or twin-flow design is required, which can be represented by two separate rows of tubes or a flat tube with two discrete, parallel flow channels. The tube / rib block can be soldered or mechanically be made, ie consist of flat tubes with corrugated ribs or round or oval tubes with flat ribs.

In an advantageous embodiment of the invention, the first collection box has an inlet chamber and the second collection box a deflection chamber, in which the division and deflection of the fluid flow takes place. The first collection box further has an exit chamber which is separated from the entry chamber by a longitudinal dividing wall. Furthermore, an outlet chamber section is arranged in the first collection box, into which the second partial flow diverted into the width opens. The exit chamber section is in fluid communication with the exit chamber. With this arrangement, the advantage is achieved that due to the reduced flow rate of the second partial stream a relatively strong cooling is achieved, d. H. a cold zone for the air temperature profile.

According to a further advantageous embodiment of the invention, the heat exchanger can be extended by "reflection" in a heat exchanger with separate right / left control. This is done by providing a second inlet chamber with a further connection piece, extended collection boxes with a further deflection chamber and a further outlet chamber portion, which is combined with the first outlet chamber portion. By such an extension with a mirror image arrangement of the two inlet nozzle and inlet chambers and a central outlet chamber section on the one hand, the aforementioned temperature stratification warm / lau / cold maintained and on the other hand, an independent flow control for the two inlet chambers supplied fluid streams are made possible.

Advantageously, the heat exchanger is designed as a radiator of a Kraftfahrzeugheizungs- and / or air conditioning, ie the manifolds and pipes are flowed through by a coolant of a cooling circuit of an internal combustion engine, while the ribs are overflowed by ambient air. The radiator according to the invention is advantageously part of a water-regulated heating system with RechtslLinks control. Due to the air temperature profile according to the invention are different tempered air streams, which can be taken directly behind the radiator through channels and the corresponding points in the vehicle can be supplied. For example, the cold air is supplied to the defrost and the head area of the vehicle occupant and the warm air to the foot and rear area of the vehicle. This can be dispensed with devices for mixing cold and warm air such as channels, flaps and mixing rooms.

In a further advantageous embodiment of the invention, the two flow connection stubs are each arranged on the front side of the heat exchanger, with other arrangements, for. B. side or up abragend possible. The return pipe is preferably also arranged frontally next to one of the two flow nozzles - here are arrangements on the side, top or center possible. An advantage of a central arrangement of the return nozzle is a symmetrical flow in the second row of tubes. The direction of flow of the air is preferably in the direction of the deflection in the depth (cross-DC) - the opposite direction (cross-countercurrent) is also possible.

In a further advantageous embodiment of the invention, the first partial flow can be throttled by a suitable choke element, so that the ratio of the mass flows changes in favor of the second partial stream: the coolant volume flow V ₁ is thus relatively small and the volume flow V ₂ relatively larger. An advantage of this throttling is that an asymmetrical arrangement of the return pipe is compensated. In addition, in a radiator design with two opposing inlet connection of advantage that the coolant flow on the right side is increased in throttling the first partial flow on the left side. In an advantageous embodiment, the throttle element may be formed as a baffle, which is preferably arranged in the outlet chamber section of the return pipe. The baffle is thus transverse to the flow direction of the exiting first partial flow and acts much like a baffle plate - thereby the desired throttling is achieved. The strength of the throttle effect can be adjusted by the arrangement and size of the baffle.

According to a preferred embodiment, the entire radiator can be designed as a soldered all-aluminum heat exchanger, d. H. with flat tubes and corrugated ribs.

Fig. 1

einen erfindungsgemäßen, als Heizkörper ausgebildeten Wärmeübertrager und

Fig. 2

einen Ausschnitt des Heizkörpers mit einem Leitblech.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below. Show it

Fig. 1

an inventive, designed as a radiator heat exchanger and

Fig. 2

a section of the radiator with a baffle.

Fig. 1 shows a heat exchanger 1, which is designed as a radiator of a heating and / or air conditioning, not shown, of a motor vehicle. The radiator 1 has a double-row or double-flow tube / rib block 2 with a first flat tube row 2a and a second flat tube row 2b. The flow channels 2a, 2b can be formed by separate flat tubes or a common flat tube with a partition wall. Between the flat tubes are corrugated ribs, which are not shown. Flat tubes and corrugated ribs are soldered together and form the tube / rib block 2, which of ambient air, represented by an arrow L, can be flowed through (an opposite air flow direction in the sense of a countercurrent flow is also possible). The radiator 1 also has two manifolds, a first (upper), only partially illustrated collection box 3 and a second (lower) collection box 4, in which unillustrated pipe ends of the tube / rib block 2 open. The upper header 3, which has a tube bottom 3a, is divided into a first inlet chamber 5, a second inlet chamber 6 and an outlet chamber 7, consisting of three communicating outlet chamber sections 7a, 7b, 7c. The first inlet chamber 5 has a first inlet or feed pipe 8 and the second inlet chamber 6 has a second inlet or feed nozzle 9, the outlet chamber 7 with its sections 7a, 7b, 7c has an outlet or return pipe 10, wherein all nozzles are arranged frontally. This need not necessarily be the case Rather, the outlet nozzle 10 may be arranged, for example, centrally and above the outlet chamber section 7b. The first inlet chamber 5 is bounded by the tube bottom 3a, a central longitudinal partition wall 5a and a half transverse wall 5b (longitudinal partition wall 5a and transverse partition wall 5b may also be integrally formed as a longitudinal / transverse partition wall). In an analogous manner, the symmetrically arranged and symmetrically formed second inlet chamber 6 is bounded by a centrally extending longitudinal partition wall 6a and a transverse half transverse wall 6b, wherein - as mentioned - the lid of the collecting tank 3 is not shown. The lower collection box 4 has a first deflection chamber 11 and a second deflection chamber 12, which is partitioned off from the first deflection chamber 11 by a partition wall 13.

The illustrated embodiment has two Heizungsvorläufe and a common return and is thus suitable for independent heating of the driver and passenger side in a motor vehicle. Deviating from the illustrated embodiment, however, a "halved" heat exchanger or radiator is conceivable, which ends in the plane of the partition wall 13, d. H. has only one flow and one return.

The function of the radiator 1 in a Krattfahrzeugheizungsanlage will be described below. The radiator 1 is connected via the two supply line 8, 9 connected to the coolant circuit of an internal combustion engine of the motor vehicle, both heats are independently controllable with respect to their coolant flow rate (water-side control). It is considered at first only the left half of the radiator 1 with the flow pipe 8. The coolant flow passes through the inlet chamber 5 in a tube group of the first row of tubes 2a and flows through them in the direction of the arrow V̇, where V̇ denotes the coolant mass flow (mass per unit time). The coolant thus flows into a first passage from the inlet chamber 5 in which is arranged in the lower header box 4 diversion chamber 11, where the total current V into two partial flows V _1, V ₂ divided and is deflected in depth and in width. The relationship applies: $$\dot{V}={\dot{V}}_1+{\dot{V}}_2\mathrm{,}$$

und einen Teilstrom ${{\dot{V}}_2}^{ʹ}$

aufteilt und in der Tiefe und in der Breite umgelenkt wird.The partial flow with the mass flow rate V̇ ₁ passes according to the arrow V̇ ₁ in the rear row of pipes 2b and flows through them from bottom to top. The second partial flow V ₂ is deflected according to the arrow V ₂ in the width and flow both in the front and in the rear row of tubes up into the section 7b of the exhaust chamber 7. The deflected in the depth partial flow V ₁ passes after passing through the rear Tube row 2b in the section 7a of the outlet chamber 7, where both partial flows V̇ ₁ and V̇ ₂ reunite and emerge as a total flow through the return pipe 10. The (for the drawing) left half of the radiator 1 described and shown by arrows flow applies analogously to the right half with flow nozzle 9, second inlet chamber 6, second deflection chamber 12 and the sections 7b, 7c of the outlet chamber 7. It thus results - which is not shown in the right half - a mirror image flow with a total flow V̇ ' , in the lower steering box 12 in a partial flow ${{\dot{V}}_1}^{\text{'}}$

and a partial flow ${{\dot{V}}_2}^{\text{'}}$

divided and deflected in depth and in width.

Instead of the flow path shown in the left half, temperature zones are shown as rectangles 1a, 1b, II and III in the right half. The two fields Ia and Ib indicate a zone of relatively warm air, i. H. Air with a relatively high outlet temperature. Zone II is a zone of lower air temperature and may be said to be lukewarm, while Zone III is a zone of relatively low air temperature, i. H. less heated air. By means not shown, such as channels and / or partitions, the air these fields Ia, 1b, II III isolated taken and directed to the desired locations in the passenger compartment. For example, the warm air emerging from the fields Ia, Ib would be supplied to the footwell, while the cold air leaving the region III would be sent to the defroster jets. The same temperature distribution results on the left side - however, the temperature level for the right and left sides may be different due to the independent control of both sides.

As already indicated above, the illustrated heat exchanger 1 with two feeders and a return can also be in a through the partition 13th divided plane and completed there each front side. This would result in a functioning radiator with a flow and a return, which has the flow pattern shown on the left and the temperature profile shown on the right (mirrored). The nozzles for flow and return can be implemented as desired.

Fig. 2 shows an upper section of the radiator 1 according to Fig. 1 , Wherein like reference numerals are used for the same parts. Shown is the upper header 3 with the first flow nozzle 8 and outlet nozzle 10, which is followed by the outlet chamber section 7a. The flow of the coolant corresponds to the in Fig. 1 , ie, the flow of coolant entering through the feed pipe 8 first flows downward in accordance with the arrow V̇ and is there - as in Fig. 1 shown - divided into two partial streams V̇ ₁ and V̇ ₂ , so that the first deflected in the depth partial flow V̇ ₁ flows upwards and enters the outlet chamber section 7 a . There, according to the invention, an approximately parallel and above the tube sheet 3a extending baffle 14 is arranged. The coolant flow entering from the rear row of tubes 2 a into the outlet chamber section 7 a strikes the guide plate 14 approximately perpendicularly, which thus acts like a baffle plate and increases the flow resistance of the coolant flow or throttles the partial flow V ₁ . This changes the ratio of the coolant mass flows in favor of the partial flow V̇ ₂ . In addition, by the arrangement of the guide plate 14 (in the drawing on the left side of the radiator 1) of the entering through the right, not shown second inlet nozzle coolant flow increases. Overall, the result of the arrangement of the guide plate 14 is a gleichmäßigte, ie approximately symmetrical temperature distribution, which compensates for the asymmetrical arrangement of the single outlet nozzle 10 (return pipe). In a symmetrical arrangement of the return neck 10, z. B. in the middle of the radiator, such a baffle would not be required. The baffle 14 can be modified in terms of its overlap of the partial stream V ₁ and with respect to its height above the tube plate 3a so as to achieve the desired air temperature distribution on the heater.

Claims (26)

1. Heat exchanger, substantially comprising a twin-row or double-flow tube/fin block (2), a first header (3) and a second header (4), wherein the tubes of the tube/fin block (2) communicate with the headers (3, 4) by way of a first fluid which can be supplied to the heat exchanger via at least one first port (8) and discharged therefrom via a second port (10), wherein a second fluid can flow through the tube/fin block (2) at right angles to the tubes, wherein the first fluid can be diverted in the heat exchanger both at right angles to the flow direction (L) of the second fluid, i.e. in the width direction of the heat exchanger, and in or against the flow direction (L) of the second fluid, i.e. in the depth direction of the heat exchanger, characterised in that the first header (3) comprises an inlet chamber (5) and the fluid flow (V) supplied to the inlet chamber (5) can, after a first passage through the tube/fin block (2), be divided into a first partial flow (V₁ ) and a second first partial flow (V₂ ), the first partial flow (V₁ ) being divertible in depth and the second first partial flow (V₂ ) being divertible in width.
2. Heat exchanger according to claim 1, characterised in that the first partial flow (V₁ ) and the second first partial flow (V₂ ) can be returned to the first header (3).
3. Heat exchanger according to claim 2, characterised in that the first header (3) comprises an outlet chamber (7).
4. Heat exchanger according to claim 2 or 3, characterised in that the first partial flow (V₁ ) can be combined with the second first partial flow (V₂ ) in the outlet chamber (7).
5. Heat exchanger according to claim 4, characterised in that the recombined partial flows (V₁ ) and (V₂ ) can be directed to the second port (10) as an outlet flow.
6. Heat exchanger according to any of claims 1 to 5, characterised in that the second header (4) comprises at least one diverting chamber (11) for diverting the fluid flow (V) in width and depth.
7. Heat exchanger according to any of claims 1 to 6, characterised in that the at least one inlet chamber (5) is bounded by a longitudinal partition (5a) and a transverse partition (5b) or by a one-piece longitudinal/transverse partition.
8. Heat exchanger according to any of claims 3 to 7, characterised in that the outlet chamber (7) comprises a chamber section (7a) disposed adjacent to the longitudinal partition (5a) of the inlet chamber (5).
9. Heat exchanger according to any of claims 1 to 8, characterised in that the first port (8) is disposed at the end face of the inlet chamber (5).
10. Heat exchanger according to any of claims 1 to 9, characterised in that the second port (10) is disposed at the end face of the outlet chamber (7) or the chamber section (7a) respectively.
11. Heat exchanger according to any of claims 1 to 10, characterised in that the outlet chamber (7) comprises a second chamber section (7b), to which the second first partial flow (V₂ ) can be supplied.
12. Heat exchanger according to any of claims I to 11, characterised in that the first header (3) comprises a second inlet chamber (6) with a third port (9), to which a second fluid flow can be supplied.
13. Heat exchanger according to claim 12, characterised in that the second header (4) comprises a second diverting chamber (12) arranged to be symmetrical relative to the first diverting chamber (11).
14. Heat exchanger according to claim 12 or 13, characterised in that the first header (3) comprises a third outlet chamber section (7c) arranged to be symmetrical relative to the first outlet chamber section (7a).
15. Heat exchanger according to one or more of the preceding claims, characterised in that it is designed as a heater (1) of a motor vehicle heating system.
16. Heat exchanger according to claim 15, characterised in that the coolant of a cooling circuit of an internal combustion engine of the motor vehicle can flow through the primary side of the heater (1) and ambient air (L) can flow through the secondary side.
17. Heat exchanger according to claim 15 or 16, characterised in that the first header (3) comprises two externally mounted inlet chambers (5, 6), each provided with a supply connection (8, 9).
18. Heat exchanger according to claim 17, characterised in that a common chamber section (7b) of the outlet chamber (7) is provided between the inlet chambers (5, 6).
19. Heat exchanger according to any of claims 15 to 18, characterised in that the heater (1) comprises a common outlet chamber (7) with the three chamber sections (7a, 7b, 7c) and a return connection (10).
20. Heat exchanger according to claim 19, characterised in that the return connection (10) is preferably disposed at the end face of the heater (1).
21. Heat exchanger according to any of claims 15 to 20, characterised in that the heater (1) comprises a heater block (2) made of flat tubes (2a, 2b) and corrugated fins.
22. Heat exchanger according to one or more of the preceding claims, characterised in that the partial flow (V₁ ) can be restricted by a restrictor element (14).
23. Heat exchanger according to claim 22, characterised in that the restrictor element is designed a s baffle (14) and disposed at right angles to the flow direction of the partial flow (V₁ ).
24. Heat exchanger according to claim 22 or 23, characterised in that the baffle (14) is disposed in the outlet chamber section (7a).
25. Heat exchanger according to any of the preceding claims, in particular according to claim 24, characterised in that the baffle (14) is disposed at a distance from and parallel to the tube sheet (3a) and/or follows the contour of the header.
26. Heat exchanger according to claim 23, 24 or 25, characterised in that the baffle (14) has a length corresponding to the entire width or to a part of the width of the flow path of the partial flow (V₁ ).

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