Assembly configuration for devices for exchanging heat

The present invention relates to an assembly configuration for devices for exchanging heat, in particular for motor vehicles.

A variety of devices for exchanging heat are used in motor vehicles such as in vehicle air conditioning systems, cooling circuits or circuits for cooling transmission oil or oil for power assisted steering systems. Application in motor vehicles regularly poses the problem that the mounting space available is confined so that the individual devices for exchanging heat must be configured to use as little space as possible. In addition the manufacturers increasingly set store by cost-effectively manufacturing each component.

The object of the present invention is therefore to provide an assembly configuration for devices for exchanging heat which both requires relatively little space and keeps manufacturing costs low.

The object of the invention is fulfilled by an assembly configuration according to claim 1. Preferred embodiments and further developments are the objects of the subclaims.

The assembly configuration of the invention comprises at least a first device for exchanging heat, having at least one inlet for a first fluid medium, a header and/or distributor tube for the first fluid medium, a plurality of first flow-through devices for the first fluid medium, a collecting means—referred to below as header—and at least one outlet for the first fluid medium.

Furthermore, adjacent the first device for exchanging heat the invention provides a second device for exchanging heat, having at least an inlet for a second fluid medium, a header and/or distributor tube for the second fluid medium, a plurality of second flow-through devices for the second fluid medium, and at least one outlet for the second fluid medium. Said header and/or distributor tube is preferably an elongated pipe. The second device for exchanging heat may project from the first device for exchanging heat in particular in longitudinal direction.

The header and/or distributor tube serves to distribute the fluid medium to a plurality of flow-through devices or to collect the fluid medium passing into the header and/or distributor tube from the flow-through devices.

For this purpose the header and/or distributor tube comprises a plurality of openings for receiving the end portions of the flow-through devices. The header and/or distributor tube has a cross-section selected from a group of cross-sections including circular, ellipsoidal, or polygon cross-sections and combinations thereof.

The flow-through devices are also elongates pipes, in particular flat pipes. Each flat pipe may comprise one or more separate flow channels for the fluid medium.

The header comprises preferably at least two openings which serve as inlet and outlet for the fluid medium. In addition a drier and/or filter means through which the fluid medium flows is preferably located in the header. Such a header is described in the German patent DE 4 238 853 C2. It can be used within the scope of the present invention in particular where the first device for exchanging heat is configured as a condenser for the air conditioner of a motor vehicle. The description of DE 4 238 853 C2 and in particular the general description in col. 1, line 1, to col. 2, line 22, and also the description of the preferred embodiments in col. 2, line 45, to col. 5, line 42, is included by reference in the disclosure of the present patent application.

The header used within the scope of the present invention can further have the configuration as described in EP 0 669 506 B2 also for the condenser of an air conditioner for motor vehicles. The general description in col. 1, line 1, to col. 1, line 48, and the particular description of the Figures in col. 2, line 4, to col. 5, line 22, is made the object of disclosure of the present patent application wherein said object is significant in particular in the case that a filter means is to be inserted into the header.

A configuration of the second device adjacent the first device is understood to mean that they are not spatially separate but positioned immediately next to each other and particularly preferably they are structured integrally or held in the same frame elements. It is preferred to position the length of the second device for exchanging heat at a long side of the first device for exchanging heat.

Thus the preferred integral manufacture results in that the second device for exchanging heat is integrated into the first device for exchanging heat. Thus both of the devices for exchanging heat can be soldered simultaneously during manufacture which leads to reduced manufacturing costs. In addition, joint assembly also results in saving space in the engine compartment.

In a preferred embodiment at least one header and/or distributor tube for the first fluid medium also serves as the header and/or distributor tube for the second fluid medium. For this purpose at least two chambers are provided in the header and/or distributor tube so as to separate the two media from one another.

This is furthermore understood to mean that both the flow-through devices containing the first fluid medium and the flow-through devices containing the second fluid medium open into said at least one header and/or distributor tube. The assembly configuration preferably comprises two header and/or distributor tubes wherein both are intended to receive substantially all of the first and the second flow-through devices. Preferably two header and/or distributor tubes are provided in which both the first fluid medium and the second fluid medium flow in specified sections separate from one another.

The flow-through devices preferably comprise two end portions each of which extend into a header and/or distributor tube. Preferably said end portions extend into two different header and/or distributor tubes. It is also feasible though that each of the end portions extends into the same header and/or distributor tube. In this case it is preferred that such header and/or distributor tube comprises at least one partition means dividing the header and/or distributor tube into a first chamber into which the first end portions of the flow-through devices extend, and a second chamber into which the second end portions of the flow-through devices extend. In this way the portions on the inlet side and the portions on the outlet side of the header and/or distributor tubes can be separated from one another.

In another preferred embodiment the plurality of first flow-through devices is configured parallel to the plurality of second flow-through devices. This means that the longitudinal directions of the flow-through devices are parallel relative one another, and preferably cooling fins or the like are provided between the individual flow-through devices so as to enhance exchange of heat with the heat exchanger medium, in particular air, passing through between the flow-through devices. It is conceivable to effect separation of the first flow-through devices from the second flow-through devices by stopping a respective header and distributor tube.

Preferably the first flow-through devices have substantially the same outer geometrical shape as the second flow-through devices. Manufacture can be simplified in this way since flow-through devices do not need to be produced in different types. However it may be advantageous to use first flow-through devices having an outer geometrical shape different from the second flow-through devices.

It is also preferred that the inner geometric shape of the first flow-through devices and the second flow-through devices are configured identical.

However, in particular if the viscosity of the first fluid medium is considerably different from that of the second fluid medium, different inner geometric shapes are selected.

The flow-through devices then comprise one or more flow pathways arranged in parallel, each of which has a round, square or triangular cross-section. The cross-sectional shapes may be configured in relative precise geometric lines but it is also within the scope of the invention in particular for square or triangular cross-sections to construct rounded, in particular concave transition regions.

The hydraulic diameters of each one flow-through cross-section are preferably in the range of 0.3 mm to 10 mm. The hydraulic diameter is determined by a formula where the tube cross-section area is multiplied by 4 and then is averaged by the wetted tube circumference.

The first fluid medium is preferably the refrigerant of an air conditioner for motor vehicles. In this case, the first heat exchanger is configured as a condenser. Furthermore the first fluid medium is preferably a coolant. In this case the first device for exchanging heat is preferably configured as a radiator for a motor vehicle which cools the cooling water flowing through the vehicle engine.

In the case of the first device for exchanging heat the hydraulic diameter is preferably between 0.4 mm and 4 mm, particularly preferred between 0.4 and 1.3 mm.

The second fluid medium is preferably a service fluid for motor vehicles preferably selected from a group including motor oil for lubricating internal combustion engines, transmission oil for lubricating automatic or manual gear transmissions, transmission oil for lubricating differentials provided to distribute the motor drive torque to the driven wheels (wherein said differential may be both a single differential in the case of one driven axle and the center differential in a four-wheel drive vehicle) and the like. The second fluid medium may further include service fluids such as power steering oil, brake fluid or hydraulic oil for operating superstructures of utility vehicles.

In the case of the second device for exchanging heat that cools the service fluids in vehicles the hydraulic diameter is preferably between 0.3 mm and 10 mm, particularly preferred between 0.4 and 8 mm. Preferably the tube wall of the oil cooler, i.e. the second device for exchanging heat has a thickness between 0.2 mm and 1.5 mm, preferably between 0.35 and 1.0 mm.

Since the transmission oil cooler and the condenser operate under different conditions, in particular different temperatures or temperature differences, thermal stresses would occur in the intermediate area between the oil cooler and the condenser. For example in winter the condenser remains cold since the air conditioner is not in operation. Still, the oil cooler is exposed to warming and cooling as the driver first drives and then parks the vehicle. The oil cooler tube expands and contracts again while the condenser tube remains unchanged. For this reason the oil cooler tube should be configured strong enough to withstand the stresses generated by said expansion and contraction. For this reason the wall is preferably thicker than the tube wall in the case of an independently operated oil-air cooler where no such heat-induced stresses occur. The thickness of the wall indicated above between 0.35 and 1.0 mm ensures both sufficient strength and reduced material consumption.

In another preferred embodiment at least one header and/or distributor tube comprises at least one partition means for separating the first fluid medium chamber from the second fluid medium chamber. This is preferably a partition wall inside the header and/or distributor tube where none of the two fluid media can pass through.

In a preferred embodiment a flow-through device is provided between the first and the second flow-through devices through which substantially no medium flows. This means that a number of first flow-through devices configured parallel relative to one another is followed by at least one flow-through device in which no medium flows, followed in turn by a number of second flow-through devices in which the second fluid medium flows. Said flow-through device, in which substantially no fluid medium flows, is intended to thermally insulate the first flow-through devices from the second flow-through devices. Thermal separation between said “blind” flow-through devices and the adjacent first and second flow-through devices may be configured both with and without cooling fins. In another preferred embodiment the end portion of a flow-through device, where substantially no fluid medium flows, extends into a portion of the header and/or distributor tube which is delimited by partition walls on both sides. Between said two partition walls substantially no fluid medium is provided.

In another preferred embodiment the header is configured substantially parallel to the header and/or distributor tube. Said header has a cross-section selected from a group of cross-sections including circular or polygon cross-sections and combinations thereof.

The header is preferably shorter than the header and/or distributor tube. It is particularly preferred that the length of the header is substantially identical with the length of the portion of the header and/or distributor tube in which the first fluid medium flows. This means that the header has substantially the same length as the first device for exchanging heat. However, the header may also be longer or shorter than the first device for exchanging heat.

In another preferred embodiment the header is positioned laterally displaced relative a plane spanned by the flow-through devices or more precisely by the flow-through devices in their entirety.

In another preferred embodiment the number of first flow-through devices is larger than the number of second flow-through devices. This also means that the first device for exchanging heat covers a larger lateral surface or more precisely a larger space than the second device for exchanging heat.

Preferably at least one header and/or distributor tube, particularly preferred both header and/or distributor tubes, comprises a plurality of partition means or partition walls. In this way the first fluid medium is directed back and forth a number of times between the header and distributor tubes in the first device for exchanging heat.

In another preferred embodiment at least one additional device for exchanging heat is attached to the first or the second device for exchanging heat. Said first device can preferably be positioned between the second device and the additional device for exchanging heat.

In another embodiment the second device for exchanging heat or an additional device for exchanging heat is positioned substantially parallel to a header and/or distributor tube. It is also feasible to configure the second device for exchanging heat such that the plane spanned by the first flow-through devices and the plane spanned by the second flow-through devices are parallel relative to one another. In this case the second device for exchanging heat is positioned in front or to the rear of the first device for exchanging heat, seen in the air flow direction.

Preferably the second device for exchanging heat is a device selected from a group of devices for exchanging heat including oil coolers for power steering, transmission oil coolers and the like.

Preferably the inlet and the outlet of the second device for exchanging heat are positioned at opposite end portions of the second device for exchanging heat. This means that in the present embodiment the second fluid medium, i.e. preferably the oil, enters into a first header and distributor tube, is distributed there substantially to all of the second flow-through devices, collects in the second header and distributor tube and flows off through the outlet.

In another embodiment the inlet and the outlet of the second device for exchanging heat are preferably positioned at the same end portion of the second device for exchanging heat. In this case the second fluid medium first passes through a specified number of flow-through devices from the first header and/or distributor tube into the second header and/or distributor tube, returns from there through another part of the flow-through device into the first header and/or distributor tube and on to the outlet. In this case the header and distributor tube to which the inlet and the outlet are attached, preferably comprises a partition means or a partition wall positioned perpendicular to the longitudinal direction of the pipe.

In another preferred embodiment the longitudinal direction at least of the inlet or the outlet of the second device for exchanging heat is positioned relative to the plane spanned between the flow-through devices in their entirety at a specified angle. Said angle is between 0 degrees and 70 degrees, preferred between 0 degrees and 40 degrees, and particularly preferred between 5 degrees and 30 degrees.

Further advantages and embodiments of the assembly configuration of the invention can be taken from the accompanying drawings.

These show in:

FIG. 1
a a schematic illustration of the assembly configuration of the invention in a first embodiment;

FIG. 1
b a schematic illustration of the assembly configuration of the invention in another embodiment;

FIG. 2
a a top view of the assembly configuration of the invention;

FIG. 2
b a side view of the assembly configuration of the invention;

FIG. 2
c a top plan view of the assembly configuration of the invention;

FIG. 2
d a view of the bottom surface of the assembly configuration of the invention;

FIG. 3 a connecting device for the inlets and outlets of the first device for exchanging heat;

FIG. 4 an enlarged view of the assembly configuration of the invention;

FIG. 5 an illustration of the header for the assembly configuration of the invention;

FIG. 6 an enlarged bottom view of the assembly configuration of the invention;

FIG. 7
a an enlarged side view of the assembly configuration of the invention;

FIG. 7
b another side view of the assembly configuration of the invention;

FIG. 8 a detailed view of another embodiment of the assembly configuration of the invention.

FIG. 1
a is a schematic illustration of the assembly configuration of the invention. Reference numeral 1 refers to a first device for exchanging heat, reference numeral 2 to a second device for exchanging heat. The length of the second device 2 for exchanging heat is placed at a long side of the first device for exchanging heat. Reference numeral 5 indicates a header that is a component of the first device 1 for exchanging heat. Reference numerals 8 and 9 indicate an outlet and an inlet for feeding refrigerant into the first device 1 for exchanging heat and discharging it. Reference numeral 22 indicates an inlet for a second fluid medium into the second device 2 for exchanging heat and reference numeral 21 an outlet for the second fluid medium. In this case there is a single flow through the second device 2 for exchanging heat which may for example be an oil cooler for power steering. Alternatively, the second device for exchanging heat may be positioned beneath the first device 1 for exchanging heat which is illustrated by the dashed illustration of the device 2. In this case the second device 2 for exchanging heat is positioned beneath the supercooling zone of the first device for exchanging heat which in the present embodiment is a condenser.

FIG. 1
b illustrates the assembly configuration of the invention in another embodiment. In contrast to the second devices 2 for exchanging heat shown in FIG. 1a, the second devices 2 for exchanging heat shown in FIG. 1b comprise both the inlet 21 and the outlet 22 at one end face of the device. In this case the oil entering into the second device 2 is deflected inside the device, i.e. it flows first from the left to the right and then back from the right to the left in FIG. 1b.

FIG. 2
a is a top view of the assembly configuration of the invention. It comprises a first header and distributor tube 4 and a second header and distributor tube 3. A plurality of first flow-through devices 12 and a plurality of second flow-through devices 24 are configured between said header and distributor tubes. Reference numeral 5 indicates a header configured parallel to the header and distributor tube 3. Reference numerals 6 refer to retaining means for attaching the assembly configuration for example to the frame of a car body. Reference numeral 9 indicates an inlet for a refrigerant at the first device for exchanging heat and reference numeral 8 an outlet for the refrigerant. Reference numeral 21 indicates an inlet for the second fluid medium into the second device 2 for exchanging heat and reference numeral 22 an outlet for the second fluid medium. Reference numeral 11 indicates a connecting device for the inlets and outlets 9 and 8 of the first device 1 for exchanging heat.

The length of the flow-through devices 12 and 24 is between 100 mm and 1000 mm, preferred between 300 mm and 800 mm, and particularly preferred between 500 mm and 620 mm. The length L of the device is between 200 mm and 1100 mm, preferred between 400 mm and 900 mm, and particularly preferred between 600 mm and 700 mm. The width B of the assembly configuration is between 100 mm and 600 mm, preferred between 200 mm and 500 mm, and particularly preferred between 350 mm and 400 mm. The length of the header is between 300 mm and 600 mm, preferred between 200 mm and 500 mm, and particularly preferred between 300 mm and 350 mm.

FIG. 2
b is a side view of the assembly configuration of the invention. Reference numeral 11 indicates the connecting device for the inlets and outlets 9 and 8. Reference numeral 22 indicates the outlet for the second device 2 for exchanging heat. It can be seen that the inlet 9 comprises a number of angled regions. Reference numerals 27 and 25 indicate retaining means for fastening the connecting device 11.

FIG. 2
c is a bottom view of the assembly configuration of the invention. Reference numeral 12 refers to the plurality of flow-through devices of the first device 1 for exchanging heat. As can be taken from FIG. 2c, the longitudinal direction of the inlets and outlets 21 and 22 of the second device 2 for exchanging heat is angled relative the longitudinal direction of the flow-through devices 24.

FIG. 2
d is another side view of the assembly configuration of the invention. In this case it can also be seen that the inlets and outlets 9 and 8 comprise angled portions. The length of the portion 9a which runs substantially parallel to the header and distributor tube 4 can be customized to fit the structural conditions in the engine compartment. The reference numerals 14a, 14b and 14c indicate partition walls placed in the header and distributor tube 4 which substantially prohibit flow of the fluid media in a horizontal direction. A flow-through device 12 is preferably positioned between the two partition means 14a and 14b through which substantially no fluid medium flows. This configuration serves as thermal insulation as specified above. In this embodiment the second device 2 for exchanging heat is positioned to the left of the partition means 14a and to the right of the partition means 14b, the first device 1 for exchanging heat. This means that the first fluid medium is located to the right of the partition means 14b, whereas the second fluid medium flows at the left of the partition means 14a. In this way the fluid media are maintained spaced apart at least by the distance between the partition means 14a and 14b.

FIG. 3 shows a detailed view of the connecting device 11. It comprises receiving areas 65 and 67 for receiving the inlet and outlet 9 and 8. The end portions of the inlets and outlets 9 and 8 preferably comprise enlarged regions for receiving additional tube portions. Reference numeral 64 indicates an opening for inserting a retaining means 25 and 27. Said retaining means 25 and 27 are preferably threaded for screwing into the openings 64 and 63 above. The connecting device 11 is preferably configured at a specified angle relative the longitudinal direction of the header and distributor tube 4. Said angle is preferably between 0 degrees and 50 degrees, preferred between 0 degrees and 30 degrees, and particularly preferred between 0 degrees and 20 degrees.

FIG. 4 is another enlarged side view of the assembly configuration of the invention. The angle at which the connecting device 11 is positioned relative the header and distributor tube 3, 4 can also clearly be seen. It can further be seen that a lid 59 is attached to the header 5 so as to open the header 5.

FIG. 5 is a detailed view of the header 5. It comprises at its inside a drier and/or filter unit that serves to filter or dry the refrigerant. Reference numeral 57 refers to a housing to receive the drier and filter means in which for example granulated drier material is provided. Reference numeral 52 indicates a sealing means for closing the header 5 to be fluid-tight against the ambience when the lid 59 is closed. Reference numeral 56 is a lower housing component where the drier and filter means are positioned.

FIG. 6 is another bottom view of the assembly configuration of the invention. One can see the curved portions of the inlets and outlets 9 and 8 and the inlet 21 for the second device 2 for exchanging heat.

FIG. 7
a is an enlarged bottom view of the assembly configuration of the invention. It can be seen that the longitudinal direction of the outlet 22 of the second device 2 for exchanging heat runs at a specified angle β relative to the longitudinal direction of the flow-through devices 12 or 24. Said angle is between 0 degrees and 40 degrees, preferred between 5 degrees and 20 degrees, and particularly preferred between 8 degrees and 12 degrees.

The inlet 21 is also preferably configured at a specified angle relative to the longitudinal direction of the flow-through device 24. Said angle gamma is preferably between 0 degrees and 50 degrees, preferred between 10 degrees and 30 degrees, and particularly preferred between 18 degrees and 24 degrees.

Reference numeral 14 indicates a frame element that serves as a stabilizer both of the first device 1 and the second device 2 for exchanging heat.

FIG. 7
b is a second side view of the assembly configuration of the invention. It can be seen that the header 5 is laterally displaced relative to the plane E spanned by the flow-through devices. Reference numeral 6 in turn indicates a retaining means for the assembly configuration of the invention.

FIG. 8 is a detailed view of another assembly configuration of the invention wherein the header is not illustrated. In this embodiment both the inlet and the outlet of the second device for exchanging heat are positioned at the same end portion of the device. The partition wall 14a serves to partition the region on the inlet side from the region on the outlet side to be substantially tight.

Two partition walls 14b and 14c are also illustrated. A flow-through device 35 through which substantially no fluid medium flows is positioned below the portion defined by the two partition means 14b and 14c. Instead of a “blind” flow-through device, both the present embodiment and the embodiments illustrated above may be provided with a separator 35 whose outer dimensions preferably correspond to the outer dimensions of the flow-through devices but particularly preferred has a full cross-section, i.e. no flow channels, compared to the flow-through devices.

Assembly configuration for devices for exchanging heat

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Priority Claims (1)