DE102014212906A1 - Intercooler with a plate heat exchanger - Google Patents

Abstract

The invention relates to a constructed in the design of a plate heat exchanger intercooler (1) with a plurality of heat exchanger plates (2). Each heat exchanger plate (2) is designed as a liquid-carrying hollow body, wherein superimposed heat exchanger plates (2) are arranged at such a distance that the charge air cooler (1) is designed to be flowed through by the charge air to be cooled (3). In order to achieve the desired heat exchange and thus a reduction of the charge air temperature, the heat exchanger plate (2) by a coolant (4) of a cooling water circuit of an internal combustion engine can be flowed through. For fluid guidance, each heat exchanger plate (2) has a coolant inlet (5) and a coolant outlet (6), through which the coolant (4) is discharged after flowing through the entire heat exchanger plate (2). In this case, the supplied coolant (4) from the coolant inlet (5) by means of a along one longitudinal side of the turbulence body (7) extending, with the coolant inlet (5) connected to the first collecting channel (9) distributed and then occurs transversely to the longitudinal extent of the collecting channel (9) through this to be collected on the other side of the turbulence body (7) in a further collecting channel (11). As a result, a flow direction of the coolant (4) within the turbulence body (7) in a counter-current direction to the supplied charge air (3) is achieved in a thermodynamically optimal manner.

Description

The invention relates to a designed as a plate heat exchanger intercooler with several, each having a liquid-carrying hollow body having heat exchanger plates, which are each connected to a coolant inlet and a coolant outlet, wherein at least individual heat exchanger plates are flowed by the charge air to be cooled on the outside and within of a coolant, in particular a Coolant, through-flowable hollow body is arranged for example as a turbulence sheet running turbulence body.

To increase the performance of internal combustion engines, turbochargers or superchargers are used to compress the air. In this case, however, there is an undesirable heating of the air also referred to as charge air as a result of compression in the supercharger to temperatures above 150 ° C.

In order to reduce such heating of the charge air, air coolers are used, which are often arranged in a cooling module and serve to cool the charge air. The charge air flows through a heat exchanger, which, for example, flows through the ambient air and is thus cooled. As a result, a cooling of the charge air is possible, which allows an increase in performance of the internal combustion engine.

In order to allow for improved cooling, motor vehicles use coolant-cooled intercoolers, which are arranged in the intake area. The intercooler consists of a plurality of sheets and profile elements, which are connected to flow channels for the coolant and protrude with their ends in collecting tanks. Between the flow channels for the coolant, the charge air to be cooled flows transversely to the flow direction of the coolant in the flow channels.

From the DE 103 28 746 A1 For example, a device with a multi-stage heat exchanger and a method for producing such a device are known.

From the EP 1 899 589 B1 a charge air cooler for a motor vehicle is known in which charge air can be cooled by a coolant flowing in flow channels, wherein the flow channels for the coolant are formed by flat tubes. Preferably, the flat tubes are arranged in at least one row. In this case, preferably, a deflection of the coolant flow in the width and / or the depth of the charge air cooler takes place.

The EP 1 170 478 A2 discloses a compressor housing having a charge air cooler. The US 2004/0118389 A1 discloses a turbocharger with intercooler. Furthermore, the refers also EP 1 491 843 A2 on a charge air cooler for motor vehicles. The EP 2 169 338 A1 further relates to a gas cooler for an internal combustion engine.

Furthermore, the concerns DE 10 2011 016 625 A1 a usable as an oil cooler plate heat exchanger with a plurality of heat exchanger plates, each forming a flow trough with a peripheral edge web. In the flow trays turbulence plates are inserted, which are formed from corrugated sheet metal and rest on both sides of each adjacent heat exchanger plates. If these turbulence sheets are flown in the direction of the longitudinal rows, the greatest flow resistance results, while the lowest flow resistance results in the transverse direction. By an appropriate inclination or inclination of the rows with respect to the resulting between the inlet and outlet main flow direction for the oil or the cooling water thus the most favorable flow resistance can be adjusted with respect to the main flow direction and an optimal ratio of the cooling capacity to the flow resistance can be achieved.

In addition, the disclosed DE 198 02 012 C2 a water-cooled fuel cooler with a plate heat exchanger. The propagation or flow direction of the media through the flow channels of the plate heat exchanger from flow channel to flow channel overlap. Each medium describes a zigzag flow path through the heat exchanger.

A disadvantage is found in practice, the considerable flow resistance, which is associated with the use of a turbulence body. Although it is already known to achieve a suitable ratio between flow resistance and achievable cooling capacity by different inflows of the turbulence body in a heat exchanger, the achievable results so far are still not optimal.

Against this background, the invention has the object to provide a much improved charge air cooler, which is in particular thermodynamically optimized and also can be produced relatively inexpensively.

This object is achieved with a charge air cooler according to the features of claim 1. The dependent claims relate to particularly expedient developments of the invention.

According to the invention, therefore, a charge air cooler is provided, in which at least one, preferably all heat exchanger plates inside arranged at the hollow body, connected to the coolant inlet first collecting channel or connected to the coolant outlet second collecting channel, wherein at least one collecting channel along a longitudinal side of the turbulence body extends such that the coolant distributed along the longitudinal side of the turbulence body enters and through this substantially passes transversely to the longitudinal direction. As a result, a significant increase in the heat transfer is achieved in a surprisingly simple manner, without this at the same time the flow resistance in the flow through the heat exchanger plates is undesirably high.

The invention is based on the finding that large turbulences and a comparatively low flow resistance can be reconciled by flowing through the plate heat exchanger transversely to its largest cross section. Although this does not reduce the flow resistance in relation to a specific cross-sectional area, it does, however, limit the flow resistance to a sensible degree due to the area enlarged according to the invention in the sum. Thus, by the heat exchanger plates are flowed through in the direction of their shorter extension, which also runs parallel to the inflow direction of the charge air, not only the flow loss is reduced within the heat exchanger plates, but also significantly improves the thermodynamic efficiency due to the changed flow direction of the coolant. The collecting channel fulfills the function of the distribution of the coolant over the entire longitudinal side of the turbulence body. It is easily understood that the relatively large area of the turbulence body on its longitudinal side results in a sufficiently high volume flow, regardless of an optionally reduced flow rate.

A particularly advantageous embodiment of the invention is achieved in that a distributor element is arranged at least in a collecting channel associated with the coolant inlet, by means of which a substantially constant volumetric flow distribution along the turbulence body can be set. By the collecting channel is designed as a distributor element or a distributor element is arranged in this, it is achieved that results in a nearly uniformly distributed flow profile over the entire cross-sectional area along the longitudinal side of the turbulence body. As a result, the efficiency is further improved and also reduces the total flow resistance by avoiding speed differences. Of course, the distributor element can also be an integral part of the collecting channel or the heat exchanger plate.

In a simple variant of the collecting channel has along its main extension different cross-sectional areas, so as to achieve a uniform loading of the turbulence body with the coolant due to the thus achievable constant flow velocity. For this purpose, at least one collecting channel is separated from the turbulence body by a separating element having a plurality of passage openings, the areal proportion of the passage openings being different in the longitudinal direction of the collecting channel, in particular increasing with increasing distance from the coolant inlet or the coolant outlet. In this way, a trouble-free adjustment of the coolant inlet is achieved in the turbulence body in a simple manner. For this purpose, in the top or bottom of the heat exchanger plates projections, such as webs are embossed, which block or cover certain inlet areas or outlet areas. By a decreasing with increasing distance from the coolant inlet or coolant outlet blocking can be achieved in a simple manner, a uniform distribution of the coolant.

The blocks each limit the passage openings. According to a particularly advantageous embodiment of the invention, at least individual passage openings on an adjustable size or distribution, so as to allow rapid adaptation to different conditions of use. Thus, for example, the intercooler be adapted to adapt to different internal combustion engines modular, with different lengths long sides can arise, so that an adaptation of the interlocks makes sense. Furthermore, a different installation location of the intercooler in the motor vehicle, for example, deviating from a horizontal orientation and the concomitant impairment of the flow of the coolant, make an adjustment of the passage openings required.

Another, also particularly promising embodiment of the invention is also achieved in that the longitudinal side has an orientation substantially transverse to the flow direction of the charge air, so that the flow direction of the cooling water is parallel to the flow direction of the charge air cooler. As a result, an optimal flow guidance is achieved and at the same time realized the largest possible inflow surface for the charge air to be cooled.

It proves to be particularly practical if the collecting channel of the coolant inlet on a side facing away from the direction of flow of the charge air side and the collecting channel of the coolant outlet at one of the flow direction of the Charge air facing side is arranged so as to realize the thermodynamic particularly effective known countercurrent principle, in which the two coolant flows of the charge air and the coolant flow in opposite directions.

The coolant inlet and the coolant outlet could be located on the same side of the charge air cooler. On the other hand, it is particularly practical if the coolant inlet is arranged in the area of a first end face of the turbulence body and the coolant outlet in the region of a second end face of the turbulence body opposite the first end face, so that the flow path traveled by the coolant is constant irrespective of the entry location into the turbulence body. In particular, the flow path which has traveled in the two flow channels on the inlet side and on the outlet side always adds to a full length of a flow channel.

One might think of arranging the coolant inlet or the coolant outlet in recesses of the turbulence body. If according to a further particularly efficient embodiment of the invention, the turbulence body along the opposite collecting channels two side surfaces of matching size, in particular congruent surfaces along the longitudinal sides, the cross section of the turbulence body between the inlet side and the outlet side changes neither in terms of the area nor the geometry, so that Flow of the coolant is further optimized.

Another, also particularly promising embodiment is also realized in that the collecting channels are arranged in mutually parallel planes, so that therefore the distance between the inlet side and the outlet side of the turbulence body is constant. In order to optimize the inflow or outflow in the collecting ducts, they may be inclined with respect to the horizontal or relative to each other, for example, with different orientations.

In another, likewise particularly practical modification, the turbulence body has a shaping designed as a positioning aid or as a centering aid so as to simplify assembly, in particular in the case of non-symmetrical turbulence bodies, and to preclude assembly errors. As a result, the turbulence body can also be designed, for example, as an insert which is enclosed in the cavity without an additional fixing means with the heat exchanger plate.

The invention allows numerous embodiments. To further clarify its basic principle, one of them is shown in the drawing and will be described below.

This shows in

1 a charge air cooler with a plurality of heat exchanger plates in a perspective view;

2 one in 1 shown heat exchanger plate with a turbulence body enclosed therein in a plan view;

3 a variant of in 2 shown heat exchanger plate with a positioning aid;

4 a section of the in 2 shown turbulence body in a perspective view;

5 a variant of in 1 shown heat exchanger plate with opposite coolant inlet and coolant outlet;

6 another variant of in 1 shown heat exchanger plate with external coolant inlet and coolant outlet;

7 a variant of in 2 shown heat exchanger plate with a distributor element.

An inventive intercooler 1 will be described below on the basis of 1 to 7 explained in more detail. The intercooler 1 is considered a plate heat exchanger with several heat exchanger plates 2 executed. Each heat exchanger plate 2 consists of a liquid-carrying hollow body, wherein superimposed heat exchanger plates 2 are arranged so spaced that the intercooler 1 from the charge air to be cooled 3 designed to flow through. In order to achieve the desired heat exchange and thus a reduction in the charge air temperature, the heat exchanger plate 2 from a direction indicated by arrows coolant 4 a cooling water circuit of an internal combustion engine, not shown, can be flowed through, as will be explained in detail below.

For fluid guidance, each heat exchanger plate 2 a coolant inlet 5 and a coolant outlet 6 through which the coolant 4 after flowing through the entire heat exchanger plate 2 is dissipated. Within the hollow body of the heat exchanger plate 2 is a turbulence body designed as a turbulence plate 7 inserted.

Essential to the invention is that the supplied coolant 4 from the coolant inlet 5 not directly into the turbulence body 7 occurs, but first by means of a along a long side 8th of the turbulence body 7 extending, with the coolant inlet 5 connected first collecting channel 9 is distributed. By the coolant 4 initially unhindered over the entire longitudinal side 8th of the turbulence body 7 flows and then transversely to the longitudinal extent of the collecting channel 9 enters this, is thermodynamically optimal way a flow direction 10 of the coolant 4 within the turbulence body 7 in the counterflow direction to the supplied charge air 3 reached. After flowing through the turbulence body 7 becomes the coolant 4 in one with the coolant outlet 6 connected second collection channel 11 collected.

In 2 is the heat exchanger plate 2 with a turbulence body enclosed therein 7 shown in a plan view. Starting from the coolant inlet 5 gets the coolant 4 first in the first collection channel 9 and is distributed there substantially uniformly over the entire longitudinal side 8th of the turbulence body 7 before getting across to the long side 8th in the counterflow direction to the inflowing charge air 3 through the turbulence body 7 flows through and through the second collection channel 11 the coolant outlet 6 is supplied. The coolant inlet 5 and the coolant outlet 6 are the front side of the turbulence body 7 through a separating element 12 from each other and separated from it, so that the turbulence body 7 has an easy to produce rectangular basic shape.

In addition is in 3 nor a largely similar variant of the heat exchanger plate 2 represented, in which the turbulence body 7 an executed as a positioning aid molding 13 has as a recess. In this shape 13 engages a corresponding projection of the heat exchanger plate 2 one, so that the turbulence body 7 can be performed in a simple manner as a depositor, without this with the heat exchanger plate 2 must be firmly connected. This results in particular manufacturing advantages.

In 4 is the turbulence body 7 to recognize in an enlarged perspective view. The turbulence body 7 consists of a large number of wave-shaped turbulence plates 14 with regular wave crests and troughs, which are offset against each other in rows. The turbulence body 7 is in operation in the flow direction 10 flows along the longitudinal rows, which results in a relation to the cooling effect optimum flow resistance. The longitudinal rows can also be made from a single turbulence sheet. Inside the heat exchanger plate 2 lies the turbulence body 7 with the troughs and the wave crests against the inner wall surface of the heat exchanger plate, not shown 2 at.

In the 5 and 6 is still a variant of in 1 shown heat exchanger plate 2 shown, wherein the coolant inlet 5 in the area of a first end face 15 of the turbulence body 7 and the coolant outlet 6 in the area of one of the first end face 15 opposite second end face 16 of the turbulence body 7 is arranged. This is the result of the coolant 4 traveled flow path regardless of the entry location of the coolant 4 into the turbulence body 7 constant. In particular, the adds in the two flow channels 9 . 11 the inlet side and the outlet side flow path always to the same length corresponding to the longitudinal side 8th , While at the in 5 shown variant of the coolant inlet 5 and the coolant outlet 6 in a respective recess 17 by a separator 18 separated turbulence body 7 are arranged in the in the 6 shown variant of the heat exchanger plate 2 the coolant inlet 5 and the coolant outlet 6 arranged externally, causing the turbulence body 7 along the opposite collecting channels 9 . 11 has two congruent, mutually offset side surfaces.

In 7 is another variant of the heat exchanger plate 2 with a distribution element realized by blocking 19 in the two collection channels 9 . 11 shown by a substantially constant volume flow along the longitudinal side 8th of the turbulence body 7 and thus also in the flow through the turbulence body 7 with a flow direction 10 in the counterflow direction to the supplied charge air 3 is adjustable. The distributor element 19 has this one between the respective collection channel 9 . 11 and the turbulence body 7 arranged separating element 20 with several openings 21 whose passage size increases with increasing distance from the coolant inlet 5 or the coolant outlet 6 increases. At the same time, the distance between adjacent passage openings decreases 21 with increasing distance from the coolant inlet 5 or the coolant outlet 6 from. Through the distributor element 19 is achieved that an almost equally distributed flow profile over the entire cross-sectional area of the turbulence body 7 results. As a result, the efficiency is further improved and also the total flow resistance within the heat exchanger plate 2 reduced.

LIST OF REFERENCE NUMBERS

1

 Intercooler

2

 heat exchanger plate

3

 charge air

4

 coolant

5

 Coolant inlet

6

 coolant outlet

7

 turbulence body

8th

 long side

9

 collecting duct

10

 flow direction

11

 collecting duct

12

 separating element

13

 formation

14

 turbulence plate

15

 front

16

 front

17

 recess

18

 separating element

19

 distributor element

20

 separating element

21

 Port

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 10328746 A1 [0005]
• EP 1899589 B1 [0006]
• EP 1170478 A2 [0007]
• US 2004/0118389 A1 [0007]
• EP 1491843 A2 [0007]
• EP 2169338 A1 [0007]
• DE 102011016625 A1 [0008]
• DE 19802012 C2 [0009]

Claims (10)

A charge air cooler designed as a plate heat exchanger ( 1 ) with a plurality, each having a liquid-carrying hollow body heat exchanger plates ( 2 ), each to a coolant inlet ( 5 ) and a coolant outlet ( 6 ) are connected, wherein at least individual heat exchanger plates ( 2 ) of the charge air to be cooled ( 3 ) can be flowed on the outside and within the hollow body through which a coolant can flow, a turbulence body ( 7 ), characterized in that at least one heat exchanger plate ( 2 ) disposed within the hollow body, with the coolant inlet ( 5 ) connected first collecting channel ( 9 ) and / or one with the coolant outlet ( 6 ) second collecting channel ( 11 ), wherein at least one collecting channel ( 9 . 11 ) along a longitudinal side ( 8th ) of the turbulence body ( 7 ) such that the coolant ( 4 ) distributed along the longitudinal side ( 8th ) of the turbulence body ( 7 ) enters this. Intercooler ( 1 ) according to claim 1, characterized in that at least in a collecting channel ( 9 . 11 ) a distributor element ( 19 ) is arranged, through which a constant volume flow distribution along the turbulence body ( 7 ) is adjustable. Intercooler ( 1 ) according to claims 1 or 2, characterized in that at least one collecting channel ( 9 . 11 ) from the turbulence body ( 7 ) through a plurality of passage openings ( 21 ) having separating element ( 20 ), wherein the areal proportion of the passage openings ( 21 ) in the longitudinal direction of the collecting channel ( 9 . 11 ) is different. Intercooler ( 1 ) according to claim 3, characterized in that at least individual passage openings ( 21 ) have an adjustable size and / or distribution. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the longitudinal side ( 8th ) an orientation transverse to the flow direction of the charge air ( 3 ) having. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the collecting channel ( 9 ) of the coolant inlet ( 5 ) at one of the direction of flow of the charge air ( 3 ) and the collecting channel ( 11 ) of the coolant outlet ( 6 ) at one of the direction of flow of the charge air ( 3 ) facing side is arranged. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the coolant inlet ( 5 ) in the region of a first end face ( 15 ) of the turbulence body ( 7 ) and the coolant outlet ( 6 ) in the region of one of the first end face ( 15 ) opposite second end face ( 16 ) of the turbulence body ( 7 ) is arranged. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the turbulence body ( 7 ) along the opposite collecting channels ( 9 . 11 ) two particularly congruent side surfaces of matching size along the longitudinal sides ( 8th ) having. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the collecting channels ( 9 . 11 ) are arranged in mutually parallel planes. Intercooler ( 1 ) according to at least one of the preceding claims, characterized in that the turbulence body ( 7 ) an executed as a positioning aid or centering molding ( 13 ) having.

Images