EP1068478A1

EP1068478A1 - Integrated collector-heat transfer unit

Info

Publication number: EP1068478A1
Application number: EP99966865A
Authority: EP
Inventors: Bernd Dienhart; Hans-Joachim Krauss; Hagen Mittelstrass; Karl-Heinz Staffa; Christoph Walter
Original assignee: Ford Werke GmbH
Current assignee: Ford Werke GmbH
Priority date: 1999-02-01
Filing date: 1999-12-15
Publication date: 2001-01-17
Also published as: AU2277200A; JP4107461B2; WO2000046558A1; FR2789159A1; US6298687B1; JP2000227289A; FR2789159B1; CA2326558A1; DE19903833A1

Abstract

The invention relates to an integrated collector-heat transfer unit, comprising a collector housing (1) in which a collector chamber (2) and a heat transfer unit having two separate heat transfer channels (5, 6) are located, said channels being disposed in thermal contact with one another, wherein one of the heat transfer channels (5) is part of a first flow channel extending from an inlet to an outlet in the housing of the collector and has a helical extension while the other heat transfer channel (6) is part of a second flow channel extending in-between the collector chamber and a connection of the housing. According to the invention, the second heat transfer channel (6) also has a helical extension, wherein the spirals thereof are in thermal contact with at least one adjacent spiral of the first heat transfer channel (5). Said unit can be used, for instance, in air conditioning systems for automobiles.

Description

PATENT APPLICATION

Integrated collector heat exchanger assembly

The invention relates to an integrated collector-heat exchanger assembly according to the preamble of claim 1. Such assemblies are particularly useful in air conditioning systems of motor vehicles, such as C0 ₂ air conditioning systems, in order to have one collector and one internal heat exchanger of the refrigerant circuit in one integrated there To provide arrangement.

A generic integrated collector-heat exchanger assembly is disclosed in US Pat. No. 3,955,375. The structural unit shown there is part of an air conditioning system, the collector part of the structural unit being located between the outlet side of an evaporator and the inlet side of a compressor, and its heat exchanger unit forms an internal heat exchanger between the low-pressure side refrigerant in the collecting space on the one hand and the high-pressure side refrigerant in front of the evaporator inlet side on the other. The refrigerant enters the collecting space via a side inlet in the upper area of the collecting space and is sucked out of it via an opening on the upper side of the collecting space. At the same time, oil that has settled in the lower area of the collecting space is also sucked in via an oil suction line leading upwards out of the collecting space. The integrated heat exchanger unit is formed by a pipe coil arranged in the collector housing and thus in the collecting chamber, with both pipe ends being led out of the collecting chamber on the underside of the housing and opening there into connection openings of a connection block which are introduced laterally. In the case of a collector heat exchanger assembly disclosed in published patent application DE 196 35 454 A1, the heat exchanger unit is formed by one or more flat tube spirals with spaced turns, the flat tube interior forming a first and the tube spiral space forming a second heat exchanger channel of the heat exchanger unit that is in thermal contact therewith.

From US Pat. No. 4,895,203, a two-fluid heat exchanger, which is used in particular for hot water heating by a coolant of a motor vehicle engine, is known, which has a cylindrical outer housing, a hollow cylinder arranged coaxially in the interior thereof and a pipe coil running axially between the hollow cylinder and the outer housing. Direction has spaced turns. The coiled tubing forms the heat transfer channel for one fluid, while the interspace between the coil turns acts as a helical heat transfer channel for the other fluid.

The invention is based on the technical problem of providing an integrated collector-heat exchanger assembly of the type mentioned at the outset, which has a comparatively simple structure, can be produced with relatively little effort and realizes a compact integration of the heat exchanger unit in a collector housing with good heat transfer efficiency.

The invention solves this problem by providing an integrated collector-heat exchanger assembly with the features of claim 1. In this assembly, both heat exchanger channels of the heat exchanger unit characteristically have a helical course such that the turns of one channel each have at least one adjacent turn of the other channel are in thermal contact. This separates them heat transfer media flowing from one another through the two heat exchanger channels over the entire tortuous channel length to one another in heat transfer connection. Since the flow channel length can be significantly larger than the external dimensions of the heat exchanger unit due to the spiral, the heat exchanger unit can be accommodated in a comparatively compact manner in the collector housing given the required heat transfer capacity. At the same time, the construction of the heat exchanger unit from two helical heat exchanger channels in thermal contact is relatively simple and can be manufactured with little effort. In particular, it is possible to construct the integrated collector-heat exchanger assembly as a pure welded construction without the need for additional soldered connections.

In the case of a structural unit developed according to claim 2, the collecting space is formed by a collecting space arranged inside the collector housing, and the heat exchanger unit is realized very simply by means of a coiled tube, which is introduced with axially spaced turns in a sealing manner radially between the inner wall of the collector housing and the outer wall of the collecting container. While the tube interior of this tube coil forms the one heat exchanger channel, the spiral space between the spaced turns of the tube coil acts as the other heat exchanger channel. The collector-heat exchanger assembly constructed in this way can be manufactured with a few simple components.

In a further embodiment of the invention, the collecting container is open at the top, and the associated flow channel leading from the collecting container to the outside of the housing runs from the open top collecting container area downwards through the corresponding helical heat exchanger channel to at least the lower collecting container area, where it is connected to a or several oil suction holes made in the collecting container. The term “oil suction hole” is to be understood here to mean any fine opening through which a fluid which is carried along by the actual heat transfer medium and is, on the other hand, clearly viscous is entrained, which may or may not be oil. When used in air conditioning systems, it is mostly lubricating oil for the compressor that is entrained by the refrigerant. Via the oil suction holes, this can be carried away in a controlled manner by the refrigerant sucked out of the collecting container after it has previously settled down in the collecting container.

In a further embodiment, an increase in the heat transfer capacity is provided in that the collecting container outer wall has a profile adapted to the heat exchanger tube coil, so that there is a heat transfer-increasing, flat and not only linear contact of the tube coil on the collecting container outer wall . In an embodiment that also increases heat transfer, the heat exchanger tube coil is provided with an outside, surface-enlarging profile.

In the case of a structural unit developed according to claim 6, the heat exchanger unit is formed by a coaxial tubular coil, in which a radially inner and a radially outer channel represent the two heat exchanger channels. This unit can also be manufactured easily and with few components. In particular, in this case the collector housing can simultaneously form the boundary of the collecting space in which the coaxial tube coil is then located.

In a structural unit developed according to claim 7, both housing-side connection points of the continuous, not in the collecting space are located. The first flow channel ends on a common housing side, preferably facing one end region of the helical heat exchanger channels, and the flow channel is guided with a straight pipe section in the collector housing to the opposite heat exchanger channel end region. Analogously, if necessary, the inlet and outlet on the housing side can also be provided for the heat transfer medium to be temporarily stored in the collecting space, so that all connections for the integrated collector-heat exchanger assembly are accessible from one side.

In the case of a structural unit developed according to claim 8, the coaxial tubular coil merges in one end region into a U-shaped coaxial tubular section which is located radially within the spiral region and with which the flow length effective for heat transfer can be further increased without enlarging the structural unit itself.

In a further embodiment of the invention according to claim 9, the coaxial tube coil is arranged in the collecting space and shortened at one end with its radially outer channel in such a way that its mouth end lies in the upper collecting area, while the radially inner channel continues to the outside of the housing. In a further embodiment of this measure, the coaxial tube coil is provided in a lower collecting area with one or more oil suction bores that connect its radially outer channel to the lower collecting area, in which the more viscous fluid entrained by the actual heat transfer medium settles.

In the case of a structural unit developed according to claim 11, collecting space supply means are provided which supply the heat transfer medium to be temporarily stored in the collecting space with a tangential flow component. to lead. The resulting rotating inflow flow into the collecting space facilitates the desired separation of the actual heat transfer medium and the more viscous fluid entrained by it. Advantageous embodiments of the invention are shown in the drawings and are described below. Here show:

1 is a longitudinal sectional view through an integrated collector-heat exchanger assembly with a collecting space container sitting on a flat intermediate floor and the surrounding heat exchanger tube coil,

2 is a view corresponding to FIG. 1, but for a collector-heat exchanger assembly with an arched intermediate floor,

3 is a partial sectional view through a collector

1 and 2, but with a profiled collecting tank wall,

4 shows a cross-sectional view through a profiled usable instead of the unprofiled heat exchanger tube coil of FIGS. 1 to 3

Coiled tubing,

5 is a view corresponding to FIG. 1, but for a collector-heat exchanger assembly without an intermediate floor, 6 is a longitudinal sectional view of an integrated collector-heat exchanger assembly with a coaxial tube coil and connections on both sides,

7 shows cross-sectional views of various coaxial tube coils that can be used in the structural unit from FIGS.

10 is a sectional view corresponding to FIG. 6, but for a unit with only one connection side,

11 is a schematic plan view of the connection side of the assembly of FIGS. 10 and

Fig. 12 is a sectional view corresponding to FIG. 6, but for a unit with a U-shaped coaxial tube section.

The collector-heat exchanger assembly shown in FIG. 1 contains, in the interior of a collector housing 1, a cylindrical collecting container 2 which functions as a collecting space and which is seated on an intermediate floor 3. Between the collecting container 2 and the collector housing 1, a coiled tubing 5 is introduced, the windings of which are spaced apart from one another in the axial direction and bear fluid-tight radially on the inside against the outside of the collecting container and radially on the outside against the inside wall of the collector housing. In this way, a corresponding helical space 6 is formed, which is axially delimited by two adjacent coiled tubing turns, radially inwards by the collecting container wall and radially outwards by the collector housing wall. The pipe coil 5 ends on the upper side of the housing with an outlet pipe 5a led out of the housing 1 and on the lower side of the housing with an inlet pipe 5b which passes through the intermediate floor 3 and a bottom wall 1a of the collector housing 1 is passed through. While the inlet connection 5b is guided in a fluid-tight manner through the housing base wall 1a, a passage, not shown in detail, is provided in the intermediate base 3, via which the spiral intermediate space 6 is in fluid communication with a discharge space 7 delimited by the intermediate base 3 and the housing base wall 1a. An outlet 8 leads from the collector space 1 out of the collector housing 1. An inlet port 4 is introduced via a further opening on the upper side 1b of the housing and opens into the collecting container 2 which is open at the top.

In this way, the helical tube 5 in the collecting container area on the one hand and the spiral space 6 together with the upper collecting container mouth and the discharge space 7 on the other hand form a first or second flow channel, the two flow channels along their helical sections, i.e., along the spiral tube 5 and the spiral space 6, are in thermal contact with one another and thus form a first or second heat exchanger channel of a heat exchanger unit integrated in the collector housing 1.

In operation, a first heat transfer medium M1 is passed through the pipe flow channel which runs continuously from the inlet connector 5b to the outlet connector 5a in the collector housing 1 and which consists of the tube coil 5 in the heat transfer active area. A second heat transfer medium M2 to be brought into thermal contact with the first reaches the collecting container 2 via the inlet connection 4 and is temporarily stored there. From there, it can be withdrawn from the collecting container 2 in the vapor state at the top, flowing down along the spiral space 6, then entering the discharge space 7 and being drawn off from there via the outlet connection 8. Along the space formed by the spiral space 6 The second, helical flow path means that the second heat transfer medium M2 is in countercurrent thermal contact via the wall of the tube coil 5, which is made of a good heat-conductive material, with the first heat transfer medium M1 passed through the tube coil 5.

If a more viscous fluid is entrained by the second heat transfer medium M2 introduced into the collecting container 2, this settles on the bottom of the collecting container 2. In order to be able to carry it away again from there with the stream of the second heat transfer medium M2 drawn off from the collector housing 1, one or more oil suction bores 9 are provided in the lower region of the side of the container, which are dimensioned such that the more viscous fluid depends on the suction effect in a certain, desired amount is sucked out of the collecting container 2.

The collector-heat exchanger assembly constructed in this way can be used in particular for the refrigerant circuit of a motor vehicle air conditioning system in which CO ₂ or another conventional refrigerant is used. The heat exchanger unit 5, 6 integrated in the collector functions as an internal heat exchanger between the refrigerant flowing on the high pressure side of the refrigerant circuit, which in this case represents the first heat transfer medium M1, and the refrigerant flowing on the low pressure side, which in this case is the second heat transfer medium M2 represents. On the low pressure side, the collector part of the assembly connects to an evaporator with the collecting container 2 and passes into the internal heat exchanger 5, 6, while the latter is on the high pressure side between a condenser or gas cooler and an expansion valve.

The refrigerant coming from the evaporator thus reaches the collecting container 2 via the inlet connection 4 and is carried away by the refrigerant entering Compressor lubricating oil settles on the bottom of the sump. In the storage container 2, the temporarily stored refrigerant is in the lower area above the settled oil in the liquid state and in the upper area in the gaseous state. Due to the suction effect of the compressor, gaseous refrigerant is withdrawn from the collecting container 2 from above, flows helically through the intermediate space 6 downwards into the discharge space 7, entraining a certain amount of lubricating oil again via the oil suction holes 9, and leaves the collector housing 1 via the outlet connection 8 towards the compressor. In countercurrent to this, the high-pressure refrigerant coming from the gas cooler or condenser is introduced into the coiled tubing 5 via the inlet connection 5b, flows helically in the tubular coil 5 upwards in heat transfer connection with the low-pressure-side refrigerant flowing down through the interspace 6, and then leaves it Collector housing 1 via the outlet connection 5a.

It goes without saying that, depending on the application, the first heat transfer medium M1 can also be passed through the associated first flow channel in the opposite direction from that shown, in which case it then flows downwards through the coiled tubing 5 in direct current to the second heat transfer medium M2 in the spiral space 6 , ie the integrated heat exchanger unit works in this case on the direct current principle.

Fig. 2 shows a variant of the assembly of Fig. 1, which differs from this only in the mezzanine design, wherein a planar, but a curved bottom floor 3a closes the container 2 below. Otherwise, the same reference numerals have been chosen as in FIG. 1 for the corresponding elements, so that reference can be made to the above description of FIG. 1. In the example of FIG. 2, instead of or in addition to the side oil suction hole or holes 9, an oil suction hole 9a is in the intermediate holes. introduced the 3a at its lowest point. Compressed lubricating oil, which has been temporarily stored in the lower area of the collecting container 2, can be drawn off into the discharge space 7 in the lower region of the collecting container 2 and carried there by the refrigerant M2 sucked to the compressor. The arched-down intermediate floor design allows oil to be carried along to the compressor via the oil suction hole 9a made at the deepest point when little oil has accumulated in the collecting container 2.

FIG. 3 shows a cutaway sectional view of a further variant of the structural unit according to FIG. 1 or 2, only the heat-transfer-active, modified area being shown, while the structural unit otherwise corresponds to that of FIG. 1 or 2. In the assembly of FIG. 3, a collecting container 2a is provided to form the collecting space, which has a profiled side wall conforming to the tube coil 5. As a result, the turns of the tube coil 5 lie not only linearly on their radial inside but also flat against the outer wall of the collecting container, which on the one hand facilitates the fluid tightness of this connection, which is not absolutely necessary, but is generally desirable, and on the other hand improves heat transfer between that in the collecting container 2a temporarily stored and extracted from this heat transfer medium on the one hand and the heat transfer medium passed through the coiled tubing 5 on the other hand. In addition or as an alternative to this profiling of the collecting container side wall, an outside profiling of the coiled tubing can be provided in order to increase its heat-transferring surface.

FIG. 4 shows an example of such a tubular coil 5a with an enlarged surface on the outside. The increased heat transfer surface also allows a higher flow rate of the heat transfer media without reducing the heat transfer performance. Fig. 5 shows a further collector-heat exchanger assembly, which is modified compared to those of Figs. 1 and 2 in that no intermediate floor is provided. Insofar as there are corresponding functional elements, they are provided with the same reference numerals as in FIG. 1, so that reference can be made to that of FIG. 1 for their description. The collecting container 2 sits in this example directly on a flat floor 1c of a modified collector housing V. Through a first bore in the housing base 1c, the inlet connection 5b for the coiled tubing 5 is carried out, while the outlet connection 8 for the second heat transfer medium M2 is inserted into a second bore in the base 1c and opens into the lower end region of the spiral space 6, with which the one also or several oil suction bores 9 which are introduced into the collecting container side wall.

FIG. 6 shows an integrated collector-heat exchanger assembly, in which a collector housing 10 is provided, which delimits an internal collecting space 11 when an independent collecting container is omitted. In this collecting space 11 there is a coaxial tubular coil 12 which contains a radially inner channel 12a and a radially outer channel 12b. By machining on both sides, the coaxial tube coil 12 is shortened at its two end sections, bent over into an inlet connection 12c and an outlet connection 12d, in its radially outer channel 12b in such a way that it respectively opens out inside the collector housing 10, while the radially inner channel 12a emerges on both sides from the Collector housing 10 is brought out. At the lower end, the outer coaxial tube duct 12b opens into a discharge space 14, which is separated from the collecting space 11 above by an intermediate floor 12 and which is delimited at the bottom by a housing base 10a, into which an outlet connection 15 is introduced. Thus, the inner coaxial tube channel 12a forms the flow channel for the first heat transfer medium MI, while the outer coaxial tube channel 12b forms the flow channel for the second heat transfer medium M2 and is in thermal contact with the radially inner flow channel 12a along its entire, modified flow profile. For this purpose, the coaxial tube is made of a highly thermally conductive material. In this example, the coaxial tube coil 12 thus forms the heat exchanger unit integrated in the collector housing 10, in which the two heat transfer media M1, M2 are preferably in countercurrent, alternatively in cocurrent, in heat-transferring connection with one another.

The second heat transfer medium M2 is introduced into the collecting space 11 via a side inlet 16. As an alternative to this lateral supply, the second heat transfer medium M2 can, as indicated by dashed lines, also be introduced into the collecting space 11 via an inlet connection 16a provided on the upper side of the housing. A viscous fluid, such as lubricating oil, which may be entrained, settles on the intermediate floor 13. In this lower collecting space area, the coaxial tube is provided with one or more oil suction bores 17, via which accumulated viscous fluid can be entrained in the desired amount by the second heat transfer medium M2 flowing in the outer coaxial tube channel 12b and drawn off from the collecting space 11. The second heat transfer medium M2 is preferably sucked into the vaporized or gaseous state in the upper collecting space area in the outer coaxial tube channel 12b and leaves it at its opposite, lower end, from where it then arrives in the exhaust chamber 14 and from there out of the collector housing 10.

6 is in an analogous manner with the same properties and advantages, for example for a motor vehicle air conditioning system usable, as indicated for the examples of FIGS. 1 to 5 described above.

7 to 9 show possible designs of the coaxial tube of FIG. 6 in cross-section. Specifically, FIG. 7 shows a completely extruded coaxial tube 18 with a one-piece inner channel 12a and an outer channel 12b consisting of several parallel, circumferentially spaced channel branches. FIG. 8 shows a coaxial tube 19 which is made in two parts from a thick-walled high-pressure tube 19a and a thin-walled cladding tube 19b. The high-pressure pipe 19a contains the inner channel 12a and is provided on the outside with spacing ribs 20, which preferably lie in a fluid-tight manner against the inner surface of the cladding tube 19b, so that an outer channel 12b, which again consists of several parallel branches, is formed. The coaxial tube 21 shown in FIG. 9 consists of a thin-walled cladding tube 21b provided with axially extending spacing webs 22 and an internal high-pressure tube 21a which forms the inner flow channel 12a. The spacer webs 22 are preferably fluid-tight against the high-pressure pipe 21a, so that in turn a plurality of parallel channel branches forming the outer flow channel 12b are formed.

While, in the coaxial tube 18 of FIG. 7, the outer channel 12b can be shortened on both sides compared to the inner channel 12a, as mentioned, by machining, this can alternatively be achieved in the case of the coaxial tubes 19, 21 of FIGS. 8 and 9, that a shorter outer sheath compared to the inner high-pressure tube is used.

FIG. 10 shows a variant of the assembly of FIG. 6, elements which are functionally the same again being provided with the same reference numerals and reference is made to the description of FIG. 6. 10 are characteristically all four Inlet and outlet connections for introducing and discharging the two heat transfer media MM, M2 into and out of the collector housing 10 are jointly provided on the upper side 10b thereof. 6, the inner coaxial tube channel 12a is bent at its lower end in the extraction space 14 and is guided to the upper side 10b of the housing 10 through a straight-line inlet connection 23 which leads through the intermediate base 13 and the collecting space 11. In addition, a rectilinear suction connection 24, which penetrates the collecting space 11 and the intermediate floor 13 as far as the discharge space 14, is introduced into the upper side 10b of the housing, via which the second heat transfer medium M2 coming out of the collecting space 11 and through the converted outer coaxial tube channel 12b into the discharge space 14 is directed upwards is withdrawn through the collector housing 10.

The second heat transfer medium M2 is supplied to the collecting space 11 via an inlet connection 25 likewise inserted into the upper side 10b of the housing, which ends on the collecting space side with a tangential curve 25a. The resulting tangential supply of the second heat transfer medium M2, e.g. of refrigerant from an air conditioning system on the low-pressure side into the collecting space 11 proves to be advantageous, since the resulting rotating flow e.g. a desired separation of refrigerant and entrained oil due to their different densities. The assembly of FIG. 10 is particularly suitable for applications in which it is desirable or necessary to be able to access all connections of the integrated collector-heat exchanger assembly from one side.

FIG. 11 shows a plan view of the common connection side of the assembly of FIG. 10 with the inlet connector 23 and the outlet connector 26 for the first heat transfer medium M1 and the inlet connector 25 and the outlet connector 24 for the second heat transfer medium M2. Otherwise apply for this unit, the properties and advantages specified for the above exemplary embodiments.

FIG. 12 shows a further variant of the assembly of FIG. 6, the same reference numerals being used again for functionally identical elements and reference is made to the above description of FIG. 6. In a modification of the design of FIG. 6, the coaxial tube used in the integrated collector-heat exchanger assembly of FIG. 12 is bent at its upper end to a U-shaped coaxial tube section 27 following its heat-transferring coil region 12, which returns to the lower collecting chamber region and from there is led up again through the collector housing 10. At the lowest point of the U-bend lying radially inside the spiral region 12, an oil suction bore 28 is again provided, which connects the lower collecting space region to the outer coaxial tube channel 12b. Depending on its length, the U-shaped coaxial tube section 27 increases the heat transfer active flow length of the integrated heat exchanger unit formed by the coaxial tube.

As the examples explained above, the invention provides an integrated collector-heat exchanger assembly, in which a collector and a heat exchanger are integrated in a common assembly with few components in a compact design with little effort. In particular, the structural unit can be produced by welded connections alone, without additional soldered connections being necessary. Accordingly, there are no problems in this case that excess flux and solder flake off during operation and lead to malfunctions, for example in a refrigerant circuit, so that in the present case there is a high degree of internal cleanliness of the flow channels. The integrated collector-heat exchanger assembly according to the invention is particularly suitable for use in motor vehicle air conditioning systems, especially also for those with the refrigerant C0 ₂ . The heat exchanger unit here forms an internal heat exchanger integrated in the low-pressure collector. The high-pressure refrigerant on the back is passed through the collector housing in a pipe designed for a correspondingly high pressure, so that no soldering or welding connection of the structural unit is loaded with the high-pressure refrigerant pressure. The collector housing is then only loaded with the low-pressure refrigerant pressure and can therefore be made with a relatively small wall thickness. The forcibly helical flow guide for both heat transfer media in the heat exchanger unit results in a high heat transfer capacity given a given, compact design, which can be further increased by countercurrent guide of the two media. The heat transfer performance can be further improved by profiling the coiled tubing and / or a possible collecting container. Another advantage of the compact design is that essentially the entire collector housing can be used for the heat exchanger unit. The intermediate floor which may be provided can be quite thin, since there is a similar pressure on both sides. For this reason, the pipe section passed through the intermediate floor does not necessarily have to be welded to the intermediate floor, it may be sufficient to simply push it through.

Overall, the unit can be manufactured with a low weight. External leaks can be easily remedied from the outside. Leakages between the high and low pressure sides at connection points, as stated, cannot occur in the collector housing due to the design. As can also be seen from the various examples above, the inlet and outlet connections can be placed at practically any desired location on the collector be placed so that the conditions prevailing in the respective application can be taken into account well.

Claims

claims

1. Integrated collector-heat exchanger assembly, in particular for a motor vehicle air conditioning system, with a collector housing (1) in which there is a collecting space (2) and a heat exchanger unit (5, 6) with two separate heat exchanger channels in thermal contact, whereby - A first heat exchanger duct (5) is part of a first flow duct running from a housing inlet (5b) to a housing outlet (5a) in the collector housing and has a helical shape and the second heat exchanger duct (6) is part of one between the collecting chamber (2) and one Housing connection (8) extending, second flow channel, characterized in that the second heat exchanger channel (6) also has a helical shape and its turns are in thermal contact with at least one adjacent turn of the first heat exchanger channel (5).

2. Integrated collector-heat exchanger assembly according to claim 1, characterized in that the collecting space from an inside of the collector housing (1) arranged collecting container (2) is formed, which has a heat exchanger channel from a surrounding the heat exchanger tube coil (5) is formed axially spaced turns, with its radially inner winding surface is tightly connected to the collecting container and with its radially outer winding surface tightly to the collector housing, and the other heat exchanger channel from the spiral gap (6) is formed, which is delimited axially by the spaced tube coils (5), radially inwards by the collecting container (2) and radially outwards by the collector housing (1).

3. Integrated collector-heat exchanger assembly according to claim 2, characterized in that - the collecting tank (2) is open at the top, the second flow channel (6) between the open top tank area and a level with the lower tank area or lower, associated housing connection (8) runs and - the collecting container is provided with one or more oil suction bores (9) in a lower area connected to the second flow channel.

4. Integrated collector-heat exchanger assembly according to claim 2 or 3, characterized in that the outer wall of the collecting container (2a) has an adjacent to the adjacent heat exchanger tube coil (5) profiling through which it rests flat against the coiled tubing turns.

5. Integrated collector-heat exchanger assembly according to one of claims 2 to 4, characterized in that the heat exchanger tube coil (5a) has an outside, surface-enlarging profile.

6. Integrated collector-heat exchanger assembly according to claim 1, characterized in that the heat exchanger unit is formed by a coaxial tubular coil (12), of which a radially inner channel (12a) forms one heat exchanger channel and a radially outer channel (12b) forms the other heat exchanger channel.

7. Integrated collector-heat exchanger assembly according to one of claims 1 to 6, characterized in that the housing inlet (23) and the housing outlet of the first flow channel (12) are arranged on a common housing side (10b) and the first flow channel from , Housing entry or exit is guided with a straight pipe section into the opposite housing area and merges there into the associated helical heat exchanger channel (12a).

8. Integrated collector-heat exchanger assembly according to claim 6 or 7, characterized in that the coaxial tube coil (12) merges at one end into a U-shaped coaxial tube section (27) which is located radially within the coil area.

9. Integrated collector-heat exchanger assembly according to one of claims 6 to 8, characterized in that the coaxial tube coil (12) is arranged inside the collecting space (11) and its radially outer channel (12b) forms the second heat exchanger channel and on one end ends in the upper collecting area, while its inner channel (12a) continues on both sides up to an associated housing entry or exit.

10. Integrated collector-heat exchanger assembly according to claim 9, characterized in that the radially outer channel (12b) of the coaxial tube coil (12) via one or more oil suction bores (17) is in communication with the lower collecting area.

11. Integrated collector-heat exchanger assembly according to one of claims 1 to 10, characterized in that

Collection space supply means (25, 25a) are provided which supply the heat transfer medium to be temporarily stored in the collection space to the collection space (11) with a tangential flow component.