WO2005121682A1

WO2005121682A1 - Heat transport device

Info

Publication number: WO2005121682A1
Application number: PCT/EP2005/006096
Authority: WO
Inventors: Sepp Hanke
Original assignee: Hartmann, Eva
Priority date: 2004-06-07
Filing date: 2005-06-07
Publication date: 2005-12-22
Also published as: US20080087412A1; EP1754013A1

Abstract

The invention relates to a heat transport device (10) which is used to cool or temper a device, which is to be operated at a defined operational temperature and which comprises a cooling and/or heat exchange device, comprising at least one flow channel (14) for a heat transport fluid, which extends in a coiled or spiral-shaped manner through a block (12) which is in good thermal contact with a device or an area which is to be cooled, said block acting as a mechanical carrier for a device, sensor, bearing and electronic element which are to be tempered. The flow channel (14) guiding the heat transport means is embodied at least sectionally in such a manner that the channel coils (29) are embodied by segment sheet metal recesses (39/i) by sections arranged in a light cross-section over-lapping. The segment sheet steels (39/i) are connected together in a rigid manner by hard-soldering and surround flat channel sections in sections which are offset counter to each other about the sheet steel thickness of the segment sheet steel. A cooling gas chamber (62) is provided for a sensor (24) which is to be cooled, said cooling gas chamber comprising a pot-shaped cylindrical housing provided with a jacket tube made of titanium. Said housing is locked by a ceramic disk which is hard soldered to the titanium tube.

Description

Heat transfer device

description

The invention relates to a heat transport device for cooling or tempering a device or component to be protected against excessive temperature or a device to be operated at a defined operating temperature and with the further generic features mentioned in the preamble of claim 1.

Such heat transport devices have a cooling device or a heat exchanger device, with at least one flow channel for a heat transport fluid, which extends helically or spirally through a metal block, which is in good thermal contact with the device to be cooled or part thereof, and usually as a mechanical support for the tempering device, or machine element, e.g. B. a sensor or a bearing is used.

In known heat transport devices of this type, the coolers or heat exchangers are realized by means of helical or coil-shaped, possibly also spiral or meandering, tubes which are connected to the part of a metal block or a device housing to be cooled, e.g. B. are kept in good thermal contact by gluing or soldering, so that for the purpose of cooling, heat to be dissipated from a block can be transferred well to the heat transport fluid circulating in the tube system and can be dissipated or heat supplied via the pipe system by means of the heat transport fluid favorable efficiency can be transferred to the object to be tempered. This type of realization of heat transport devices has a number of disadvantages, of which the following are mentioned as examples:

The manufacture of the cooling and / or heat exchange unit with the appropriate geometry and its attachment or installation to / in a housing of a device to be cooled, for. B. a pyrometer, which should be usable for detecting a high process temperature, is complex and usually requires manual work that is time and cost consuming. Due to their generally circular cross-section, the available conduits have an unfavorable relationship between the heat transfer area and the transport volume, so that cooling coils or heat exchangers, which are realized with circular cross-section tubes, inevitably build a comparatively large volume. B. for use in areas where high pressures prevail, is unfavorable for reasons of stability and for reasons of tightness.

The object of the invention is therefore to provide a heat transport device of the type mentioned at the outset, which is both simple in construction and accessible for efficient production and can be implemented with a considerably more favorable ratio of heat transfer surface to fluid transport volume than a heat transport device realized with pipes of circular cross section.

According to the basic idea, this object is achieved by the characterizing features of patent claim 1.

According to this, the housing block of the device to be tempered, through which heat transport fluid flows, has a multilayer structure, such that the channels carrying heat transport fluid thereby form at least in sections are that channel coils are formed by sections of segment sheet metal recesses of the block which have a clear cross-sectional overlap, the segment sheets forming the housing block being firmly bonded to one another and bordering in part flat channel sections which are offset from one another by the sheet metal thickness of the segment sheets or by a small multiple thereof , wherein at least two cooling circuits are also provided, which can be operated with different heat transport fluids and a gas is used as the heat transport fluid in at least one of the cooling circuits.

It is particularly advantageous here if a gas is used as the heat transfer fluid in the cooling circuit in which heat is generated at a high temperature level, since the high thermal conductivity of a gas can be used particularly effectively for heat removal and for transfer to the cooling circuit at a lower temperature which a liquid is operated as a heat transfer fluid.

The heat transport device according to the invention also provides at least the following technical advantages:

The segment sheets of the block forming the channels carrying the heat transfer fluid in the assembled state can be produced automatically with high precision in an NC or CNC-controlled laser cutting process, so that a mechanical stacking of the segment sheets for the block configuration is also easily possible. When using relatively thin metal sheets, the flow channels with z. B. flat rectangular cross-sectional shapes can be realized that a particularly favorable ratio of heat transfer aisle area to the channel volume or the volume of the heat transport fluid flowing through the channels, ie, with a relatively small construction volume, a high cooling or temperature control effect can be achieved. The multi-layer technology used in block production opens up a wide range of options for designing the ducting that would not be possible or could only be achieved with great effort using tubular line elements. The joining of numerous segment sheets can also be easily automated.

In the event that the segment sheets are to be joined by gluing, a curable lacquer is suitable for this, with which the segment sheets are sprayed or wetted by immersion in a paint bath before they are brought into the layered configuration, if necessary after excess adhesive material has dripped off, in which they, e.g. B. can be added to the uniform block by thermally accelerated curing of the adhesive material. In the case of joining the block using a

Adhesive, e.g. B. a curable multi-component resin to achieve good thermal conductivity of the adhesive layer, it may be appropriate in the plastic thermally highly conductive material such. B. Embed metal dust.

When the metal block is joined by soldering, preferably in a hard or high-temperature soldering process, a thermally highly conductive connection between the individual segment sheets is achieved in any case.

With the help of segment plates, which consist of a ceramic material that can be soldered to metal plates, which has a significantly lower thermal conductivity than common metals such as steel or aluminum, which has a particularly high level Block areas to be kept at different temperature levels can be easily offset against one another, with a step-like area between a region of the block which is arranged in the vicinity of a heat source and a region of the block which is practically at ambient temperature. or cascade-like structure of the temperature profile in the block can be achieved.

Suitable for this is one provided according to claim 7

Design of the heat transport device in such a way that coolable sections of the block arranged on different sides of a ceramic plate are each associated with their own heat transport circuit.

If, as provided in accordance with claim 8, coolable block parts are connected hydraulically one after the other, so that there is a temperature gradient between successively flowable coolable areas, or if, as provided in accordance with claim 9, different areas of a block assigned to different areas of a block are hydraulically connected in parallel, so that If the same temperature can be maintained in all subregions, the feed lines and return lines required for such hydraulic line connections can each be formed by openings of the segment sheets and possibly of the ceramic intermediate pieces which are aligned with one another.

With the help of segmental sheets of different thicknesses, preferably in an arrangement such that the thickness within the block increases monotonically step by step between a minimum value and a maximum value, the temperature profile between maximum and minimum block temperature can be influenced with simple means. If the heat transport device according to the invention is designed as a cooler, segment sheets of different external diameters can be used alternately as block core parts and as parts forming cooling fins, ie in addition to the "liquid" cooling by means of the heat transport fluid guided through the core region of the block, an "outer" can also be used "Air cooling can be realized.

When using a relatively cold gas, e.g. B. a nitrogen gas obtained directly by evaporation of liquid nitrogen, the z. B. is introduced into a chamber containing a sensitive sensor, it is particularly useful to provide a direct inlet channel to the "gas" chamber, which leads in the shortest possible way from the gas connection into this chamber and is lined with a thermally poorly conductive material, for , B. a silicone or a Teflon tube, which only touches a channel formed by aligned openings of segment plates, which can be easily achieved by a corresponding design, the edges of the aligned segment sheet openings.

The invention further relates to a control unit for the operational control of a heat transport device as explained so far, or generally a drive element operated with a fluidic working pressure medium, e.g. B. a double-acting, pneumatic or hydraulic drive cylinder, for the control of which an electrically controllable solenoid valve is provided which can be controlled by output pulses from an electronic subunit, which generates these output pulses from processing command signals from a central unit and from sensor output signals. In such a control unit, the solenoid valve provided for controlling the pneumatic drive motor can generally be controlled by output pulses from an electronic subunit, which generates these output pulses from processing command signals and, if appropriate, sensor output signals which monitor the positions of the drive cylinder piston. As a rule, if a plurality of electrically controlled drive cylinders are provided, these solenoid valves are controlled by a central control unit via electrical lines.

This has the disadvantage that, in addition to the pneumatic supply lines, electrical supply lines - control lines for the solenoid valves - must also be provided, which require additional complex installation work, in particular in complex systems. Extensions of such systems to include additional drive units and their control valves are particularly cumbersome and expensive.

In this respect, the object of the invention is to create suitable control units in connection with pressure-actuated actuators, which enable the implementation of complex systems comprising numerous drive elements with considerably less effort.

According to the basic idea, this object is achieved by the characterizing features of patent claim 19 and in respect of advantageous refinements of this basic idea by the features of further claims 20 to 23.

According to this, each of the control units is assigned its own control current source, which as a chargeable charge Storage is designed, wherein an electric generator, preferably a direct current generator, which can be driven by means of a rotary pneumatic drive motor, is provided for charging the storage device, and a magnetic valve which can be controlled by output signals of the electronic subunit supplied from the storage device is provided as part of the control unit as the storage charging valve. by means of which the pneumatic drive motor can be connected to a central compressed air supply of the pneumatic system, which also includes the drive cylinder, and can be blocked against it.

In this way, as a whole, an autonomous drive unit is achieved, which can be combined in any multiplicity to form a larger system, with only the pneumatic supply system being used as the operating energy source, such that ^" there is a compressed air line starting from the pneumatic pressure source, to which the subunits only must be connected "pneumatically." Electrical installation work can be integrated into the drive sub-units to be combined.

A charge control unit, which monitors the charge state of the electrical store and is provided in accordance with claim 20, can be used to ensure in a simple manner a charge state of the electrical store used for the power supply. An electronic subunit of the control unit, which generates control signals for controlling the control valve of the respective consumer as a function of command pulses from a central unit, which manages a plurality of control units and consumers, and as a function of status output signals from electronic sensors, is of a particularly advantageous design according to claim 4 so formed that it communicates with the central unit via wireless transmission link. As a result, the installation effort for a complex, a variety of consumers, eg. B. drive units comprehensive system drastically reduced.

By designing the control valves for the drive control of drive cylinders and the accumulator charging valves for charging the respective charge accumulator according to claim 23, a particularly energy-saving operation of the entire system is achieved, i. H. the electrical storage devices can be designed for a comparatively limited capacity.

Further details of the heat transport device according to the invention result from the following description of specific exemplary embodiments with reference to the drawing. Show it:

Fig. 1 is a schematically greatly simplified view representation of a heat transport device according to the invention with a heat sink made of segment sheets;

2a to h suitable for the construction of the heat sink of the heat transport device according to FIG 1 segment plates, each in plan view;

3a shows a heat sink consisting of the segment sheets according to FIGS. 2a to 2h, in section along the line Illa-IIIa of FIG. 2h;

3b shows the heat sink according to FIG. 3a in section along the line III-IIIb of FIG. 2h; 4 shows a heat sink of a further exemplary embodiment of a heat transport device according to the invention, in which a liquid and a gaseous heat transport medium can be used for cooling, in one of the representations of FIGS. 3b corresponding, schematically greatly simplified view representation;

5a shows a segment sheet suitable for the construction of the heat sink according to FIG. 4 in a representation corresponding to FIGS. 2a to 2h;

FIG. 5b shows a detailed view of a segment plate for connecting two spiral areas of the flow channel of the heat sink according to FIG. 4;

6a shows a further exemplary embodiment of a heat transport device according to the invention in a representation corresponding to FIG. 1, but which is further schematically simplified; and

6b shows a detail of the storage of a gas supply pipe in the heat sink of the device according to FIG. 6a, in section along the line VIb-VIb of FIG. 6a,

6c shows a further exemplary embodiment of a heat transport device according to the invention in a representation corresponding to FIG. 6b and 7 shows a schematically simplified block diagram of a control unit suitable in connection with heat transport units according to FIGS. 1 to 6b

For the heat transport device designated overall by 10 in FIG. 1, for the purpose of explanation - without restricting the generality - a design as a cooler for a sensor 11, which is only indicated schematically, is required, which is used for measurement in an environment that is exposed to high temperatures a physical quantity, e.g. B. pressure, temperature, orientation of a magnetic field, intensity of radiation or the like can be used and should be protected against damage from the high ambient temperature. In this assumed case example, the cooling should result in an expansion of the temperature range within which the sensor works reliably.

A possible application of the heat transport device 10 can also be the cooling of a device, for. B. the cooling of a "small" television camera installed on a robotic vehicle intended for observation of dangerous areas, e.g. B. fire sources that would otherwise not be accessible. The uses of the heat transport device 10 described so far have in common that the smallest possible space requirement is an important prerequisite for a wide range of uses of the heat transport device according to the invention.

In the heat transport device 10 according to FIG. 1, these requirements are met by a series of structural measures which are explained in detail below: The heat transport device 10 comprises a cylindrical-tubular, "thick-walled" heat sink, designated overall by 12, in the jacket 13 of which a flow channel, designated overall by 14, for a heat transport fluid runs, to which heat transport fluid is connected via an inlet connection 16 by means of a heat sink in FIG 1, for the sake of simplicity, is supplied to a conveying device which, after flowing through the flow channel via a return connection 17 of the flow channel, flows from the heat sink 12 back to the conveying and conditioning device, in which the heat transport fluid is cooled again and thus conditioned for the heat transport circuit.

For the sensor 11, according to the schematic

Representation of Fig.l provided that it has an elongated, cylindrical-cup-shaped metal housing 18 which is in good thermal contact with the inside of the cylindrical heat sink 12, for. B. in that the metal housing 18 of the sensor 11 has an external thread 19 / a, which is in meshing engagement with an internal thread 21 / i of the cylindrical-tubular heat sink 12; it is assumed that the sensor 11 with its housing 18 can be screwed into the heat sink 12 from the connection side, ie according to the illustration in FIG. 1, from the right side, which is on its opposite side by a ceramic plate 22, for. B. a circular disc made of aluminum oxide (A1 ₂ 0 ₃ ) is completed, which is firmly connected to the heat sink 12.

In the arrangement of the sensor 11 inserted in the heat sink 12, its housing can be axially supported on the ceramic plate 12 and braced against the heat sink 12 to such an extent that the threads of the sensor housing 18 are “full” of the threads arranged opposite of the internal thread 21 / i of the heat sink 12 are pressed so that there is good thermal contact between the heat sink and the sensor housing for the temperature control. The required strength of the connection between the ceramic plate 22 and the heat sink 12 is achieved by a hard solder connection of the ceramic to the metal of the heat sink 12.

In the exemplary embodiment selected for explanation, the sensor housing 18 is axially supported on a snap ring 23 inserted into the heat sink 12, so that the ceramic plate 22 is not axially loaded and can therefore be realized with a small material thickness.

In the exemplary embodiment of the heat transport device 10 shown for explanation, the sensor element 24, which responds to the monitored physical size, is arranged in the immediate vicinity of the ceramic plate 22, ie at an axial distance therefrom, which is only a small fraction of approximately 1/20 to 1 / 10 corresponds to the length L of the heat sink 12; however, the sensor element 24 is only fastened within the central cylindrical cavity of the heat sink at a greater distance from the ceramic disk 22, which corresponds to approximately% of the length L of the heat sink 12, at its end facing away from the ceramic plate 22 in the region of an inner base step 27 of the cup-shaped cylindrical sensor housing 18 and axially supported, with which it in turn rests on an annular end face 28 / s of a support part 28 screwed into the heat sink 12 as a counter part. As a result, as well as the threaded engagement of the sensor housing 18 with the heat sink 12, the sensor element 24 is kept in thermal contact with an “inner” area of the heat sink 12, which corresponds to an average temperature of the heat sink, which can be stabilized well. The flow channel 14 through which heat transport fluid flows during operation of the heat transport device 10 is helical in that section of the heat sink 12 which surrounds the sensor housing 18, with a large number of windings 29 / W which run coaxially with respect to the central longitudinal axis 26 of the heat transport device 10 ,

On the inlet side, this spiral section 29 of the

Transport fluid flow channel 14 connected to the inlet connection 16 via a “straight line” connection section 29 / a running parallel to the central axis 26. On the return side, the coil section 29, which extends practically over the entire length L of the heat sink 12, is directly connected to the return connection 17 with its "last" - most distant - turn as seen from the ceramic plate.

In order to implement the course of the transport fluid flow channel explained in this respect, the heat sink 12 is designed using a multi-metal layer technology, at least in its part encompassing the sensor housing 18 and comprising approximately% of the length L of the heat sink, in such a way that the heat sink 12 consists of a plurality of segment plates 32 / i is manufactured, which are joined by a material connection to a uniform metal block, the comparatively complicated - helical - course of the transport fluid flow channel 14 being formed by overall communicating recesses of mutually adjacent segment sheets 32 / il, 32 / i and 32 / i + l which overlap in some areas. For a more detailed explanation of a possible design of the heat sink 12 according to FIG. 1, reference is now also made to the detailed representations of FIGS. 2a to 2h and the sectional representations of FIGS. 3a and 3b, in which suitable designs and orientations of segment sheets are provided 32/1 to 32/8 are shown, with which these segment sheets can be joined by brazing to the heat sink 12 shown in FIGS. 3a and 3b.

For the purpose of the explanation, only the case, which is mostly irrelevant in practice, is shown in FIGS. 3a and 3b, that the transport fluid flow path 14 between the inlet connection 16 and the return connection 17 has only a single turn which completely surrounds the central axis 26 of the heat sink 12 , which is formed by five segment plates 32/2 to 32/6 (Fig. 2a to 2e), which are arranged between a connecting segment plate 32/1 and a transverse channel segment plate 32/7, which one the "straight" connecting channel section 14 / a of

Transport fluid flow channel 14 with its "short" cross channel section 14 / q (Fig. 3a) communicatingly connecting its helically extending section 29 and is closed by an annular disk-shaped termination segment 32/8 on the front side of the heat sink 12 opposite the connection segment sheet 32/1.

In the design of the heat sink 12 chosen for the explanation, its segment sheets 32 / i (i = 1 to 8) are designed as annular disks of the same diameter D of their outer circular edge 33 and the same clear diameter d of their central circular openings 34, which are concentric with respect to the disk center points 26 / m are arranged. The segment sheets 32/2 to 32/7 according to FIGS. 2a to 2e are provided with kidney-shaped recesses 36 / a close to the edge - radially outer - in the illustration example chosen for explanation, which when the segment sheets 32/2 to 32/6 2a to 2e are firmly joined to the heat sink 12 according to FIGS. 3a and 3b, in an aligned alignment form the "rectilinear" straight connection section 14 / a of the heat transport medium flow channel 14, which has a circular shape Connection port opening 37 of the connection segment plate 32/1 can be connected to one of the supply connections of the means of transport conditioning.

Furthermore, the segment sheets 32/2 to 32/6 shown in FIGS. 2a to 2e are provided with radially inner, sector-shaped recesses 39/2 to 39/6, which in the case of those made from the segment sheets 32/1 to 32/8 Cooling block 12, seen along the central axis 26 thereof, alternately overlap their clear cross-sections and sections of a cooling winding of the heat transfer medium channel 14 completely surround the central axis 26 of the cooling head 12. This "one" heat transport duct winding communicates with the stretched duct section 14 / a of the heat transport medium duct 14 via the cross duct segment plate 32/7 and is connected via the radially inner connection opening 39 of the connection segment plate 32/1 (FIG. 2h) to the heat transport medium conditioning (not shown) - unit can be connected.

In the design of the heat sink 12 chosen for the explanation, the connection stub openings 37 and 39 of the connection segment plate 32/1 (FIG. 2h) are circular Openings are formed, the respective central axes 41 and 42 of which run parallel to the central axis of the respective central opening 34 of the segment plates 32 / i and which each clamp a radial plane 43 or 44 containing the central axis 26 of the heat sink, which extend along cut the central axis 26 of the heat sink 12 at right angles.

3a shows in section along the radial plane 43 of FIG. 2h that configuration of the segment plates 32/1 to 32/8 forming the heat sink 12, which results when the segment plates 32/2 to 32/8 with the in 2a to 2h superimposed on top of the connecting segment plate 32/1 and in this configuration are firmly connected to each other.

3b shows the configuration of the segment sheets 32/1 to 32/8 that results for the segment sheet stack in an analogous manner in section along the radial plane 44 of the connecting segment sheet 32/1 according to FIG. 2h, in which the cutting plane 44 passes through the radially inner connecting piece opening 39 - as the plane of symmetry thereof - runs.

The segment sheets 32/2 to 32/7 according to FIGS. 2a to 2f are each shown with the same orientation of their radial planes 43 and 44, as explained with reference to FIG. 2h, and are also cohesive in this configuration, in particular by brazing , added to the heat sink 12.

The radially outer recesses 36 / a, which form the stretched heat transport medium channel section 14 / a in an aligned arrangement (FIG. 3a), are edged in a circular arc shape radially on the inside and radially on the outside and extend at illustrated embodiment over an angular range α of about 35 °, z. B. an angular range between 30 and 40 °. These radially outer recesses 36 / a are symmetrical with respect to the radial plane 43.

The radially inner recesses 39/2 to 39/5, which are each offset by 90 ° from one another in successive segment sheets, are also radially outwardly radially outwardly and radially inward and extend over a sector area of somewhat more than 90 °, for. B. a sector range φ between 110 ° and 120 °, these radially inner recesses 39/2 to 39/5 each being formed symmetrically with respect to the radial plane 42 or the radial plane 43 (FIG. 2h).

Seen along the central axis 26 adjacent to each other, i. H. Radially inner recesses 39/2 to 39/5 offset from one another by 90 ° therefore have an overlap range between 10 ° and 15 °, depending on the amount of their azimuthal extension φ (FIG. 2c). Accordingly, at least four segment sheets, for example the segment sheets 32/2 to 32/5 with the arrangements of the radially outer and radially inner recesses 36 / a or 39/2 to 39/5 required.

Provided that only those recesses are provided which also have heat transport fluid flowing through them in the assembled state of the heat sink, three different types of are used to form a 360 ° winding

Segment sheets 32 / i required, namely a total of two segment sheets as shown in FIG. 2a, and a segment sheet 32/3 as shown in FIG. 2b, ie with an arrangement of the radially inner recess 39/3 between the radially outer one Recess 36 / a and the central len, circular recess 34 and further a segment plate 32/5, as shown in Figure 2 d, in which the central, circular recess 34 between the radially inner fluid-carrying recess 39/5 and the radially outer fluid-carrying recess 36 / a is.

In the segment sheets 32/2 and 32/5 shown in FIGS. 2b and 2d, the recesses 39/3 and 39/5 forming the elongated channel 14 and the sector-shaped winding sections are formed symmetrically with respect to the radial plane 43, which are formed by the central axis 41 of the elongated connection channel 14 / a and the central axis 26 of the heat sink 12 is spanned.

These two types of segment sheets can be replaced by a single type of segment sheet, in which, as indicated by dashed lines in FIG. 2b, in opposition to that radially outer recess 36 / a which is arranged directly adjacent to the radially inner recess 39/3 - beyond the central axis 26 - a second radially outer recess 36 / ao is provided, which can be used in the orientation of the segment sheet according to FIG. 2d to form the elongated channel 14 / a and in the orientation according to FIG. 2b "blind" - unused - remains.

The segment plate 32/7 is used to connect the end 14 / e (FIG. 3a) of the tortuous section 29 of the flow channel 14 to the elongated channel 14 / a, which is remote from the connection side on which the inlet and return connections 16 and 17 are arranged 2f that with

Cross channel recess 14 / q is provided, which mediates the connection of the turn to the elongated channel section 14 / a, which are closed off overall by the end segment plate 32/8. It goes without saying that between a segment plate 32/1 according to FIG. 2h, to which a segment plate 32/2 according to FIG. 2a is attached, and a transverse channel segment plate 32/7, which is covered by a cover segment plate 32/8 according to FIG. is covered, any number of channel windings can be arranged, which are formed in a corresponding multiplicity by the segment sheets 32/3 to 32/6 according to FIGS. 2b to 2e. With sheet thicknesses of z. B. 1 mm each turn contributes only 4 mm to the length of the heat sink 12.

Depending on the arrangement of a device to be cooled relative to the heat sink 12, as explained with reference to FIGS. 2 and 3, it may be expedient to supply cooled heat transport fluid either via the stretched channel section 14 / a, with the result that the temperature of the heat transport medium increases the end of the heat sink remote from the connection side is significantly lower than on the connection side, or, alternatively, to remove the heated heat transfer medium via the elongated connection channel 14 / a, d. H. choose the mode of operation in which the temperature of the heat transfer fluid has the minimum value on the connection side.

The heat sink designated 50 in FIG. 4 is largely similar in construction and function to the heat sink 10 explained with reference to FIGS. 1 to 3c, so that it is considered sufficient for its explanation to have structural and functional differences compared to the one already explained Heat sink 10 to enter.

The heat sink 50 differs from the heat sink 10 according to FIGS. 1 to 3c essentially in that instead of an elongated connection section in which the heat transport fluid direction in the spiral section 29 flows in the opposite direction, a spiral transport fluid channel is also provided, such that two spiral sections 29/1 and 29/2 are provided, as it were concentric with respect to the central axis 26 of the heat sink 50, the supply connections of which are located on a connection segment plate arranged on one side 52/1. To form the concentric spiral sections, segment sheets 52 / i (i = 2 to n) corresponding to the illustration in FIG. 5a are provided, all of which have the same shape.

The two helical flow paths 29/1 and 29/2 are coupled to one another by a cross-channel segment plate 52 / q arranged at the end remote from the connection in the sense of a hydraulic series connection (FIG. 5b). The cross-channel section of the cross-channel segment sheet is closed in a liquid-tight manner by a ceramic end element 52 / a which is designed as a circular disk and is soldered to the adjacent cross-channel segment 52 / q.

The segment plates 52/2 to 52 / n arranged between the cross-channel segment 52 / q and the connecting segment plate 52/1 are in turn designed as annular disks which have a slot-shaped recess 54 / a adjacent to the outer edge 53 of the segment plate and one which has an inner circular edge 56 of the respective segment sheet 52 / i have adjacent, slit-shaped recesses 54 / i which run concentrically with respect to the central axis 26 of the heat sink 50 and each have inner and outer edges curved in the shape of a circular arc and inner and outer transverse edges 57 / radially adjoining them i and 57 / a are bordered.

Seen in the direction of the central longitudinal axis of the segment sheets 52 / i or the heat sink 50, the outer ones Recesses 54 / a and the inner recesses 54 / i the same azimuthal width φ, which is greater than 180 ° and has a typical value around 200 °.

The segment plates 52 / i are formed symmetrically with respect to that plane 58 which is the bisecting plane which marks half of the azimuthal extension φ. Furthermore, the arrangement of the radially outer slot-shaped recess 54 / a and the radially inner circular slot-shaped recess 54 / i is selected such that the common angular range Δφ of their azimuthal extension is the same on both sides of the plane of symmetry 58 and corresponds to the minimum value. In the case example chosen for explanation, in which the azimuthal extension of the outer and inner recesses 54 / a and 54 / i is 200 ° in each case, the common overlap area on both sides of the symmetry plane 58 is 20 ° in each case.

The radii r / i and r / a of the radially inner edge 59 / ri and the radially outer edge 59 / ra of the radially inner one

Recesses 54 / i and the radii R / i and R / a of the radially inner edge 59 / Ri and the radially outer edge 59 / Ra of the outer slit-shaped recesses 54 / a are selected such that the radial dimensions of the between the outer edge 53 respective segment sheet and the outer edge 59 / Ra of the outer slot-shaped recess 54 / a and between the slot-shaped recesses 54 / a and 54 / i and between the inner slot-shaped recess 54 / i and the edge 56 of the central opening of the respective segment sheet 52 / i remaining narrow sector-shaped webs 61 / a and 61 / m and 61 / i each have the same amount Δr. The segment plates 52 / i are joined to the uniform heat sink 50 according to FIG. 4 in an arrangement in which the adjacent segment plates are each rotated through 120 ° relative to one another about the central axis 26, viewed along this central axis 26, the rotation from segment to segment has taken place in the same direction - clockwise or counterclockwise. This results in the opposite direction of flow in the direction of the axis 26 when the flow around the central axis 26 is in the same direction in the two spiral sections 29/1 and 29/2.

With heat sinks 12 and / or 50, as explained with reference to FIGS. 1 to 3c and 4 to 5b, complex heat transport devices can also be realized.

6a, in which between a cooling gas chamber 62, in which a sensor element 24 to be cooled is arranged, and a heat sink 50, as already described in terms of structure and function with reference to FIGS. 4 to 5b explained, a heat sink 12 is arranged, as already explained with reference to FIGS. 1 to 3b.

The heat sink 12 formed by the segment sheets 32 / i is set off from the heat sink 50 consisting of the segment sheets 52 / i by a ceramic ring disk 64 and also from the cooling gas chamber 62 by a ceramic ring disk 66; The sensor element 24 is held on the inside of this ceramic ring disk 66 facing the cooling gas chamber 62, whereby this and the ceramic ring disk 66 delimit the cooling gas chamber 62 essentially gastight against the central interior of the cooling body 12. For the purpose of the explanation, it is assumed that both in the cooling body 50, which is arranged away from the cooling gas chamber 62, and in the cooling body 12 adjacent to the cooling gas chamber 62, a liquid - e.g. B. cooling water - is used, whereas cooling in the cooling gas chamber 62 is conveyed by means of a gas which is passed through this chamber and flows around the sensor element 24.

To process the coolant flowing through the two heat sinks 12 and 50, a conditioning device 63, which is indicated only schematically, is provided, by means of which the flow temperature of the liquid passed through the heat sinks 50 and 12 can be predefined in a defined manner.

The cooling circuits represented by the two cooling bodies 12 and 50 through which cooling liquid flows are hydraulically connected in parallel in the exemplary embodiment shown for explanation, the "inlet" being connected to the stretched section 14 / a of the transport fluid flow channel of the cooling chamber-side cooling body 12, as shown is such that the coolant first flows through the turn of the flow channel 14 of the heat sink 12 immediately adjacent to the cooling gas chamber 62 and flows back over the further turns to the conditioning device 63.

The delimitation of the heat sinks 50 and 12 from one another or from the cooling gas chamber 62 with the aid of ceramic ring disks 64 or 66 is not mandatory, but is expedient if the individual areas to be cooled are to be thermally separated from each other, e.g. B. such that different "average" temperatures should be adjustable in these areas. in this connection it is assumed that the thermal conductivity of the ceramic ring disks 64 and 66 is significantly lower than that of the segment sheets 32 / i and 52 / i. If, on the other hand, an average temperature is required across the entire heat sink 12, 50, it is of course also possible to use thermally highly conductive metal disks instead of the ceramic disks 64 and 66.

In the illustrated explanatory example, the interior of the heat sink 12 is essentially gas-tightly delimited from the cooling gas chamber 62 by the ceramic ring disk 66, which carries the sensor element 64 on its inside facing the cooling gas chamber 62.

The cooling gas is supplied to the gas chamber 62 through a thin-walled stainless steel tube 67, which passes through a straight "elongated" channel, which is formed by mutually aligned recesses in the segment sheets 52 / i of the heat sink 50, the ceramic disk 64, the segment sheets 32 / i and the ceramic ring disk 66 which, together with the sensor holder, forms a bottom of the cooling gas chamber 62, which is closed off on the side facing away from the sensor element 24 by a circular ceramic disk 68.

The cooling gas is fed to the cooling gas chamber 62 by means of a blower provided as a functional unit of a cooling gas source 69, which is only indicated schematically, via the stainless steel tube 67, which through an opening of the ceramic washer 66, the diameter of which is significantly, ie two to three times larger than the outside diameter of the stainless steel tube 67, passes through and is otherwise only "punctiform" on inner radial support ribs 71 (FIG. 6b) of the heat sink 50 and / or the heat sink 12 and is thereby radially centered, which is located within Recesses of only a few segment sheets are provided.

In the exemplary embodiment according to FIG. 6a, it is - tacitly - provided that the sensor element is used for the purpose of control functions e.g. b. the sensitivity setting, the temporal function control and the communication with a central unit require an electrical power supply, which can be designed in a conventional design for a low voltage and power level. Such a supply is implemented in the exemplary embodiment chosen for explanation by means of a "small" turbine 72 which is driven by means of the cooling gas stream supplied by the cooling gas source 69 and in turn an electric generator, e.g. B. drives a DC generator 75, with the appropriately processed output voltage, the sensor element 24 can be fed. The schematically indicated electrical lines 73 required for this can be carried out within the by the

Stainless steel pipe 67 through channel can be guided through free channel sectors 74. This creates a structural unit that is electrically self-sufficient, so that more complex monitoring systems can be implemented in a simple manner with such structural units.

The heat sinks 12 and / or 50 according to FIGS. 1 and 4, which are made up of a plurality of segment sheets - multilayered - are particularly suitable for production with multiple uses, such that the segment sheets assigned to the individual layers are each formed in a defined matrix pattern in a multiple connection , so that by stacking such segment plates at the same time the stacking of a plurality of segment plates to the respective heat sink configuration takes place in which these sheets are soldered to one another, after which the separation of the bridges between the otherwise finished heat sinks is only required to separate the heat sinks.

It goes without saying that heat exchangers can also be realized in the multi-layer construction explained using coolers.

The further exemplary embodiment of a heat transport device 10 shown in FIG. 6c, to the details of which reference is now made, is largely analogous in structure and function to the exemplary embodiments explained with reference to FIGS. 1 and 6b, so that the explanation of the heat transport device is 10 can essentially be limited to design differences according to FIG. 6c. To the extent that the same reference numerals are used in FIG. 6c as already indicated in FIGS. 1 and 6a, this should include the reference to the structural and functional analogy and also the reference to the description of the correspondingly designated parts.

6c comprises a heat sink 12 and a sensor element 24, which is only shown schematically and is held in a metal housing 18, as already explained with reference to FIG. 1, which - in analogy to the exemplary embodiment according to FIG. 6a - in a cooling gas chamber 62 is arranged, in turn via a stainless steel tube 67 which passes through the heat sink 12 constructed from segment sheets 32 / i and projects into the cooling gas chamber 62, cooling air or a special pre-cooled gas, e.g. B. nitrogen or a noble gas can be introduced for cooling. The cooling gas chamber 62 is delimited by an essentially cup-shaped chamber housing, designated overall by 76, which, in the arrangement and configuration shown in FIG. 6c, is attached to the heat sink 12 in a coaxial arrangement with respect to the central longitudinal axis 26.

For the purpose of simple attachment, the terminal segment plate 32 / g of the heat sink 12, which is arranged directly adjacent to the cooling gas chamber 62, is provided with a support flange 77 which projects beyond its outer lateral surface and on which the chamber housing 76 76 can be fixed. The chamber housing comprises a flange sleeve made of stainless steel, designated overall by 78, which in turn is provided with a radial outer flange 79, which is used to fasten the chamber housing 76 to the support flange 77 of the heat sink 12 and, with the aid of screws 81, the through bores 82 of the outer flange 79 traverse the flange sleeve 78 and engage in thread 83 of the support flange 77 of the heat sink 12, can be fastened thereon.

A thin-walled jacket tube 87 is hard-soldered to the short, tubular jacket part 84 of the flange sleeve 78, adjoining an inner annular step surface 86 thereof, which at its end facing away from the heat sink 12 merges into a radially inner ring flange 88, the inner edge end face 89 of which with a circular opening 91, via which an interaction with the environment to be monitored, which is necessary for the function of the sensor element 24, is possible; H. the shielding of electrical and / or magnetic fields is removed or negligible.

This opening 91 is sealed off by a thin, between 0.3 and 1 mm thick, in turn circular ceramic disk 92 covers that is brazed in the area of the radially inner ring flange 88 on the outer ring surface. The casing tube 87 of the cooling gas chamber housing 76 is made of titanium, which can be joined with an aluminum oxide (A1 ₂ 0 ₃ ) ceramic disk by brazing in a load-resistant manner.

A thin copper ring 93, which has a thickness of 2/10 to 3/10 mm, is arranged between the flanges 77 and 78 of the segment metal sheet 32 / g of the heat sink 12 and the flange sleeve 78 as a seal.

The stainless steel tube 67 provided for the supply of cooling gas, which is held in the manner already described with reference to FIG. 6b in aligned openings of the segment plates 32 / i of the heat sink 12, extends as shown in FIG. 6c until it is in the immediate vicinity of the same the bottom of the gas chamber housing 76 forming the inner ring flange 88 or the ceramic disk 92, which is thus flowed directly by the cooling gas.

To discharge the heated gas, a stainless steel tube 94, which is correspondingly held in the heat sink 12, is likewise provided in the exemplary embodiment shown for explanation, and is provided at the same radial distance from the central axis 26 as the gas supply tube 67, but is azimuthally opposite to this - in reverse order. catch direction - is offset.

Alternatively, as indicated by a radial opening 96 of the chamber housing 76, which is arranged on its flange sleeve 78, cooling gas can also be blown out into the ambient atmosphere, if possible. Heat transport devices of the type mentioned can easily be implemented, for example, using the scale reactions shown in the drawings for the common sensor types, the diameters of which are between 10 and 40 mm.

Starting from a heat transport device such. 1 and / or 6b or βc explains the basic structure according to, there may be a need for electrical or pneumatic or hydraulic auxiliary energy for an additional consumer in that instead of a sensor element fixed in a housing, a movable A sensor or a sensor is provided which, for example, must be able to be moved back and forth in the heat sink arrangement in the axial direction, or a sensor which is to be adjustable to monitoring conditions with the aid of a mechanical actuator. An example of this is the case of a video camera which, when used in a high-temperature area, must be able to be moved in the axial direction within the heat sink assembly. B. a hydraulic or pneumatic actuating cylinder is suitable and / or electrical auxiliary energy required to adjust distances or diaphragms to enable focusing.

A heat transport device, such as. B. explained in detail with reference to Fig. 6c, is readily suitable for installation of a video camera if the ceramic disc 92 is in turn provided with a central opening which is covered by a transparent quartz glass plate, which in turn by means of a temperature-resistant ceramic putty material is connected to the ceramic disc. To explain a heat transport device which is intended for the temperature control of a more complex device which, in addition or as an alternative to an electrical consumer, can also include a pneumatic or hydraulic device, reference is now made to the relevant details in FIG. 7.

The control unit designated overall by 110 in FIG. 7 is, in general terms, intended for operating control of a consumer operated or conditioned with a fluidic working medium, generally designated 111, which communicates via the control unit 110 with a control center 12, which is only indicated schematically, Via which a plurality of different types of consumers (not shown) can be controlled, each of which is assigned its own control unit 110. Without limitation of generality, i. H. For the purpose of explanation only, it should be assumed that the consumer 111 is designed as a double-acting pneumatic linear cylinder with a piston rod 114 emerging from the housing 113 on one side, the piston 118 of the piston rod 118 being firmly displaceable with the drive pressure chamber 116 on the bottom against the rod-side pressure chamber 117 - Pneumatic - drive cylinder 111 is connected.

To control the movements of the piston 118 or the piston rod 114 of the cylinder 111 in the alternative directions represented by the double arrow 119, a 4/3-way solenoid valve 121 is provided, the P supply connection 122 of which is only schematic indicated compressed air source 123 is connected, which provides compressed air at a pressure level of 10 bar as the drive medium. The relevant supply connection of the control unit 110 is designated 123/1. A return connection 124 of the control valve 121, which in principle could be formed by a vent opening of the valve housing of the 4/3-way solenoid valve 121, is in the exemplary embodiment chosen for explanation via a return line 126 with a corresponding vent outlet 126/1 of the control unit 10 connected.

The 4/3-way solenoid valve 121 provided as a control valve has as the basic position 0 a center position centered by valve springs 127/1 and 127/2, in which the two

Supply connections 122 and 124 are blocked off from one another and against the consumer connections 128 (A) and 129 (B), which are connected to the bottom-side pressure chamber 116 and the rod-side pressure chamber 117 of the drive cylinder 111.

To actuate the solenoid valve 121, a double-stroke magnet system 131 is provided with two control windings 131/1 and 131/2, which are only indicated schematically, through the alternative energization of which the solenoid valve 121 is assigned functional positions I and II in its alternative, opposite directions of movement of the piston 118 of the drive cylinder 111 is controllable.

In the functional position I, the - z. B. - Is taken when the one control winding 131/1 is energized, the P supply connection 122 of the 4/2-way solenoid valve is connected to the A consumer connection 128, which is connected to the pressure chamber 116 on the bottom side of the drive cylinder 111 is; In this functional position I, the rod-side pressure chamber 117 of the drive cylinder 111, to which the B-consumer connection 129 of the valve is enclosed, is communicatively connected to the return connection 124 - the ventilation connection. In this functional position I is the pressure chamber on the bottom 116 of the drive cylinder 111 is connected to the high outlet pressure P of the pressure supply source 123 and the rod-side drive pressure chamber 117 of the drive cylinder 111 is relieved of pressure, and the piston 18 of the drive cylinder 111 thus moves to the right as shown in the drawing.

In the functional position II of the control valve 121 assumed when the second control winding 131/2 of the double-stroke magnet system 131 is excited, its P-

Supply connection 22 with the B-consumer connection 129 of the valve, d. H. communicatingly connected to the rod-side pressure chamber 117 of the drive cylinder 111, while the bottom-side pressure chamber 116 of the drive cylinder 111 is relieved of pressure towards the vent connection 124. The piston 18 of the drive cylinder 111 moves to the left in this functional position II.

The solenoid valve 121 is actuated in its alternative functional positions I and II by output pulses from a subunit, designated overall by 132, which individually controls the control outputs 133/1 and the control windings 131/1 and 131/2 of the 4/3 way solenoid valve 121 133/2, on which control pulses obtained from processing command signals from the control center 112 and from sensor output signals for the control windings 131/1 and 131/2 of the double-stroke magnet system 131 are emitted.

The 4/3-way solenoid valve 121 is provided with a latching device 134, which is only shown schematically, the function of which is as follows:

By alternatively energizing the control windings 131/1 or 131/2 with an output pulse from the subunit 132, the control valve 121 either reaches the functional position I or the functional position II and, after the pulse has decayed, maintains it until the other control winding is energized by an output pulse from the subunit 132, after which the functional position of the control valve thereby activated 121 is maintained until the switching pulse for the alternative functional position is emitted from the other control output of subunit 132.

To the 4/3-way solenoid valve 121 after z. B. had been switched into its functional position II by a control pulse delivered at the control output 133/2 of the subunit 132, back again into the neutral, ie. H. To switch the blocking center position 0, a short-lasting switching pulse of comparatively lower level is emitted at the other control output 133/1, which is sufficient to overcome the locking inhibition together with the prestressed return spring 127/1 and the valve body of the control valve 121 in the the

Lock position 0 to bring the corresponding middle position. The same applies analogously when the control valve 121 is to be switched back from the functional position I to the basic position 0.

The electronic subunit 132 of the control unit 110 also contains the position-characteristic output signals from position sensors 136 as information input signals, from the processing of which with output signals from the control central unit 112, the control unit 132 generates control signals for the 4/3-way solenoid valve 121 / 1 and 136/2, which emit output signals when the piston 118 of the pneumatic drive cylinder 111 shown for explanation is its left end position as shown in the drawing or its right The final position has been reached, possibly also the output signals of a displacement sensor 136/3 are supplied, which generates a voltage output signal which varies continuously with the position of the piston 118 between its line end positions and whose time profile thus contains the information about the movement of the piston 118.

Further information that can be used for processing by means of the electronic subunit 132 can be electrical output signals of a temperature sensor or a pressure sensor or a light intensity sensor that clearly vary with the respective measured variables, which are not shown for the sake of simplicity.

The subunit 132 of the control unit 110 communicates with the control center 112, which can be designed to manage a multiplicity of control units 110, is carried out wirelessly, such as by a transmitting antenna 137/1 of the subunit 132 and a receiving antenna 137/2 of the central unit 112 and Transmitting antenna 138/1 of central unit 112 and a receiving antenna 138/2 of subunit 132 of control unit 110 are shown in a schematically simplified manner.

For the electrical supply of the electronic subunit 132 of the control unit 110, an only schematically represented, needs-based rechargeable electrical memory 139 which provides the function of a direct voltage source is provided, which is realized in a manner known per se by an accumulator or buffer capacitor which can be recharged by means of a direct current generator 141 can be. To drive the direct current generator 141, which, in accordance with the relatively low electrical energy requirement of the control unit 110, can be designed as a tachometer generator of relatively small dimensions, a pneumatic rotary motor 142 designed in the manner of a small turbine and designed as a small turbine is provided , which in turn can be driven by a compressed air flow branched off from the compressed air source 123 (cf. FIG. 6a)

A 2/2-way solenoid valve 144, which is connected between the compressed air source 123 and the pressure supply connection 143 of the pneumatic drive motor 142 and has a blocking position I assigned to the standstill of the pneumatic drive motor 142 and a charging operation of the generator 141, is provided for this purpose and the flow position II assigned to this driving motor 142.

To control this charge control valve 144, a double-stroke magnet system 146 with two control windings 146/1 and 146/2 is provided, through the alternative energization of which with output pulses from a charge control unit 139 'of the electrical store 139, the charge control valve 144 in its alternative functional positions I and II can be controlled, in which the charge control valve 144 is held by a latching device 147 after a control pulse which is sent via the control line 148/1 or the control line 148/2 of the control development 146/1 or 146/2 had been forwarded again.

The pulsed activation of the accumulator charging valve 144 minimizes its consumption of electrical control power. The needs Right-hand switching on of the charging operation of the pneumatic drive motor 142 and the direct current generator 141 driven thereby is achieved by monitoring the state of charge of the electrical store 139.

As an alternative to the type of actuation of the storage charging valve 144 by output signals from the storage unit 139 illustrated in solid lines, the storage loading valve 144 can also be actuated, as indicated by dashed lines, by output signals from the subunit 132, if these also monitor the charge state of the electrical storage 139 mediated.

A drive unit formed by the pneumatic drive cylinder 111 and the control unit 110 as a whole only needs to be connected to the pneumatic pressure supply source 123 or a connection to a "ring" originating from it in order to function properly in a complex system which comprises numerous consumers. Line that mediates the function of a pneumatic "bus" line.

An expedient modification of the control unit 110 suitable for operating a sensor can also consist in installing a sensor to be cooled instead of the drive cylinder and exposing it to the air flow of the pneumatic rotary motor 42, which is then designed as a turbine, and the supply voltage by means of the generator 41 to generate for the sensor, as already explained in connection with the embodiment of FIG. 6a.

Claims

claims

1. Heat transport device (10) for cooling or tempering a device to be operated at a defined operating temperature with a cooling and / or heat exchanger device, which comprises at least one flow channel (14) for a heat transport fluid, which is helical or spiral through one to be cooled Device or area in good thermal contact block (12; 50), which acts as a mechanical support for the device to be temperature-controlled - sensor, bearing, electronic element -, characterized in that the channel (14) guiding the heat transport medium is designed at least in sections in such a way What is formed is that the channel coils (29) are formed by sections of segment sheet metal recesses (39 / i; 54 / a, 54 / i) which have a clear cross-sectional overlap, the segment sheets (32 / i; 52 / i) being firmly bonded to one another and border sections of flat channel sections that oppose each other by the sheet thickness of the segment sheets r are offset, at least two cooling circuits are provided which can be operated with different heat transport fluids and a gas is used as heat transport fluid in at least one of the cooling circuits.

2. Heat transport device according to claim 1, characterized in that the integrally fixed connection of the segment sheets (32 / i; 52 / i) is achieved by soldering.

3. Heat transport device according to claim 2, characterized in that the soldering is carried out in a hard or high temperature soldering process.

4. Heat transport device according to claim 3, characterized in that the block (12; 50) comprises at least one segment plate which consists of a ceramic material which can be joined by soldering with at least one adjacent segment plate.

5. Heat transport device according to claim 4, characterized in that the ceramic segment (64; 66) is arranged between two segment sheets and is soldered to them.

6. Heat transport device according to claim 5, characterized in that the ceramic segment (64) is arranged between sections of a housing provided with heat transport channels.

7. Heat transport device according to claim 6, characterized in that the coolable sections arranged on one side of the ceramic plate (64) are each assigned a separate heat transport circuit.

8. Heat transport device according to claim 6 or 7, characterized in that the two coolable block parts (12 and 50) are hydraulically connected in series, and that a flow line is provided which is formed by mutually aligned recesses of the segment plates and the ceramic disc and by an inlet connection from directly in leads the thermally extreme area of the multilayer block.

9. Heat transport device according to claim 5 or 6, characterized in that the different temperature ranges of the block associated transport means channels are hydraulically connected in parallel, wherein a common inlet line and a common return line are each formed by mutually aligned opening of the segment sheets and the ceramic intermediate piece.

10. Heat transport device according to one of claims 1 to 9, characterized in that segment sheets of different thickness are provided.

11. Heat transport device according to claim 10, characterized in that the thickness of the segment sheets between a value of minimum thickness and a value of maximum thickness gradually increases monotonously.

12. Heat transport device according to one of claims 1 to 11, characterized by its design as a cooler.

13. Heat transport device according to claim 12, characterized in that the segment sheets are alternately formed as core parts and as parts forming outer radial cooling fins, the means of transport provided for temperature control being arranged in the core parts and the core regions of the cooling fin segments directly adjoining them.

14. Heat transport device according to one of claims 1 to 13, characterized in that a non-combustible gas such as nitrogen or a noble gas - z. B. argon - is used, which reaches a cooling gas chamber (62) via a thermally insulated inflow line (67), in which a sensor or measuring element (24) to be cooled is arranged.

15. Heat transport device according to claim 14, characterized in that the inflow line is cylindrical-tubular and passes through coaxially arranged openings of the segment plates of the metal block and in the channel bordered by the openings by radially inwardly projecting retaining lugs (71) of opening edges of some the segment plates (32 / i; 52 / i) fixed non-positively, z. B. is jammed.

16. Heat transport device according to claim 17, characterized in that the gas supply pipe is formed as a thin-walled stainless steel pipe (67) with a thermally insulating outer coating, which consists of a flexible plastic material at normal temperature.

17. Heat transport device according to one of claims 1 to 16, characterized in that the cooling gas chamber (62) containing the sensor element (24) has a cylindrical tubular chamber jacket (84) made of titanium, which on its the heat sink (12; 12, 50) facing the end of an opening (91) which is sealed gas-tight by means of a ceramic disc (92), which is brazed to a radially inner ring flange (88) of the titanium jacket tube.

18. Heat transport device according to claim 17, characterized in that the cooling gas is guided in a circuit via a gas feed pipe (64) and a gas return pipe (92) which are guided through longitudinal channels of the heat sink arrangement (12; 12, 50) and are connected to a conditioning device.

19. Heat transport device according to one of claims 1 to 18 and with a control unit (10) for the operational control of a drive element provided as an actuator of the heat transport device, operated with a fluid working pressure medium, in particular a - double-acting - pneumatic or hydraulic drive cylinder (11 ), for the control of which an electrically controllable magnetic valve (21) is provided which can be controlled by output pulses from an electronic subunit (32) which generates these output pulses from processing command signals from a central unit (12) and from sensor output signals characterized in that a) the control unit (10), as the control current source for the solenoid valve (21), comprises an electrical charge store (39) imparting the function of a rechargeable battery or a capacitor, that b) for charging the store (39) by means of a rotary pneumatic drive motor (42) drivable electrical generator (41) of the control unit (10) is provided, and that c) the control unit (10) acts as a storage loading valve (44) by output signals from the electronic subunit (32) of the control unit supplied from the storage (39) (10) controllable solenoid valve (44), by means of which the pneumatic drive motor (42) can be connected ₍ ar and can be shut off) to a central compressed air supply (23) of the pneumatic system also comprising the drive cylinder (11).

20. The heat transport device as claimed in claim 19, characterized in that a charge control unit (39 ') which monitors the charge state of the electrical store (39) and by means of which the store charge valve (44) is located in the compressed air source (23) Function position II connecting the supply connection (43) of the pneumatic drive motor (42) can be controlled when the charge content of the store (39) has dropped below a threshold value.

21. Heat transport device according to claim 19 or claim 20, characterized in that the control unit (10) comprises an electronic sub-unit (32) which, as a function of command pulses from the central unit (12), which manages a plurality of control units (10) and drive cylinders (11) , and from status output signals from electronic sensors (36/1, 36/2 and 36/3) control signals for the control of the 4/3-way solenoid valve 21, which controls the movements of the drive cylinder (11).

22. Heat transport device according to one of claims 19 to 21, characterized in that the subunit (32) provided for controlling the 4/3 solenoid valve (21) is provided via wireless transmission links (38/1, 38/2 and 37/1, 37 / 2) communicates with the central unit (12).

23. Heat transport device according to one of claims 19 to 22, characterized in that the control valve (21) provided for the control of the drive cylinder (f) and / or that for the drive control of the rotary pneumatic drive motor (42) or the direct current generator (41) The 2/2 way solenoid valve (44) provided is designed as a pulse-controlled valve, which can be controlled by means of a double-stroke magnet system (31) or (46) and, after activation by means of a latching device (31; 46), in its activated one Position is held until a next pulse, which mediates the control into the alternative functional position, is generated.