阅读说明：本技术 用于诸如隧道掘进机传动装置等驱动和/或传动单元的温度控制装置 (Temperature control device for a drive and/or transmission unit, such as a tunnel boring machine transmission ) 是由 菲利普·弗洛伊德 约翰尼斯·布利格 于 2020-02-26 设计创作，主要内容包括：本发明大体上涉及工程机械和类似设备的驱动和/或传动单元的冷却和/或加热。本发明涉及用于冷却和/或加热这种驱动和/或传动单元的温度控制装置,该驱动和/或传动单元包括至少一个具有可流过液体的液体套的换热器模块。本发明还涉及包括至少两个通过这种温度控制装置冷却和/或加热的传动和/或驱动部分的驱动和/或传动单元。本发明还涉及隧道掘进机,其传动装置通过这种温度控制装置冷却和/或加热。根据本发明,温度控制装置的至少一个换热器模块形成夹心状地装配在两个传动和/或驱动部分之间的环形体,该环形体包括允许驱动元件穿过的中心通槽,且在相对端面上分别具有以精确配合的方式将端面连接到两个传动和/或驱动部分的连接法兰。以力或扭矩传递的方式连接例如两个传动级或两个传动和/或驱动部分的例如驱动轴或驱动轮或另一驱动元件能够被引导穿过通槽。(The present invention generally relates to cooling and/or heating of drive and/or transmission units of construction machines and similar equipment. The invention relates to a temperature control device for cooling and/or heating such a drive and/or transmission unit, which comprises at least one heat exchanger module having a liquid jacket through which a liquid can flow. The invention also relates to a drive and/or transmission unit comprising at least two transmission and/or drive sections which are cooled and/or heated by such a temperature control device. The invention also relates to a tunnel boring machine, the drive of which is cooled and/or heated by such a temperature control device. According to the invention, at least one heat exchanger module of the temperature control device forms an annular body which is fitted in a sandwich-like manner between the two transmission and/or drive parts, comprises a central through slot which allows the drive element to pass through, and has, on opposite end faces, in each case a connection flange which connects the end face to the two transmission and/or drive parts in a precisely fitting manner. For example, a drive shaft or a drive wheel or another drive element, which connects, for example, two transmission stages or two transmission and/or drive sections in a force or torque-transmitting manner, can be guided through the through-channel.)

1. A temperature control device for cooling and/or heating a tunnel boring machine drive (4) comprises at least one heat exchanger module (11) having a liquid jacket (31),

characterized in that the heat exchanger module (11) forms an annular body for fitting in a sandwich-like manner between two adjacent drive and/or transmission parts (4.1, 4.2), which annular body comprises a central through slot (13) allowing a rotatable drive and/or transmission element (32) to pass through and has, on each of the opposite end faces, a connecting flange (14, 15) for connecting the end face to the two adjacent transmission and/or drive parts (4.1, 4.2) in a precisely fitting manner.

2. Temperature control device according to the preceding claim, wherein the liquid jacket (31) forms an annular chamber (23) inside the annular body, which extends in a manner surrounding the through slot (13).

3. The temperature control device according to the preceding claim, wherein the annular chamber comprises at least one inlet (24) and at least one outlet (25) which are arranged adjacent to each other and/or in one section of the annular chamber (23) and are separated from each other by a partition plate (27) which divides the annular chamber (23) in a circumferential direction into two annular chamber portions in a split ring.

4. The temperature control device according to the preceding claim, wherein the inlet (24) and the outlet (25) are arranged on an upper side of the heat exchanger module (11).

5. A temperature control device according to any of the preceding claims, wherein radially offset turbulence plates (28) are provided in the annular chamber (23).

6. A temperature control device according to the preceding claim, wherein the turbulence plates (28) alternately protrude outwards from the inner circumference of the annular chamber (23) and inwards from the outer circumference of the annular chamber (23) and alternately define passage gaps (29) on the inner and outer circumference of the annular chamber (23) to allow circulation of a temperature control fluid.

7. Temperature control device according to any of the preceding claims, wherein the annular body of the heat exchanger module (11) comprises a solid outer ring (19), an inner ring (20) arranged inside the outer ring (19), and two preferably flat plate-shaped end walls (21, 22), on which two opposite connecting flanges (14, 15) are formed, which end walls connect the outer ring (19) and the inner ring (20) to each other and delimit the liquid jacket (21) between them.

8. Temperature control device according to the preceding claim, wherein the wall thickness of the end walls (21, 22) is smaller than the wall thickness of the outer ring (19), wherein the wall thickness of the end walls (21, 22) is preferably smaller than a third of the wall thickness of the outer ring (19) or smaller than a quarter of the wall thickness of the outer ring (19).

9. Temperature control device according to any of the preceding claims, wherein the outer ring (19) comprises an axial through slot (30) within the connecting flange (14, 15) for flow connection of the two transmission and/or drive parts (4.1, 4.2) between which the heat exchanger module (11) is arranged sandwich-like.

10. A temperature control device according to any of the two preceding claims, wherein the turbulence plates (28) are connected to both end walls (21, 22) and alternately to the inner ring (20) or the outer ring (19).

11. A transmission and/or drive unit comprising at least two transmission and/or drive portions (4.1, 4.2) between which a temperature control device designed according to any one of the preceding claims is arranged, wherein the two transmission and/or drive portions (4.1, 4.2) are fastened to the opposite connection flanges (14, 15) of the heat exchanger module (11) and are connected to one another by means of the heat exchanger module (11), wherein a transmission and/or drive element (32) which interconnects the two transmission and/or drive portions (4.1, 4.2) in a force and/or torque transmitting manner extends through the through slot (13) in the heat exchanger module (11).

12. The transmission and/or drive unit according to the preceding claim, wherein the two transmission parts connected to the heat exchanger module (11) each comprise a planetary transmission stage, wherein the drive element extending through the through slot (13) in the heat exchanger module (11) connects the sun gear of one planetary transmission stage to the planet carrier (9) of the other planetary transmission stage in a non-rotatable manner.

13. The transmission and/or drive unit according to any of the two preceding claims, wherein the at least one heat exchanger module (11) is arranged between a first transmission stage and a second transmission stage, which are connected in series to the drive motor (3) and/or which have the highest rotational speed.

14. A tunnel boring machine with a drill head (2) which can be driven by a drive motor (3) via a transmission unit (4), wherein a temperature control device designed according to any one of claims 1 to 10 is integrated in the transmission unit (4).

Technical Field

The present invention generally relates to cooling and/or heating of drive and/or transmission units of construction machines and similar equipment. The invention relates in one aspect to a temperature control device for cooling and/or heating such a drive and/or gear unit, which comprises at least one heat exchanger module having a liquid jacket through which a liquid can flow. In another aspect, the invention relates to a drive and/or transmission unit comprising at least two transmission and/or drive sections which are cooled and/or heated by such a temperature control device. Finally, the invention also relates to a tunnel boring machine, the drive of which is cooled and/or heated by such a temperature control device.

Background

In construction machines in which the drive is operated continuously for a long time, the transmission and possibly also the drive parts in the immediate vicinity thereof have a strong thermal load, so that pure air cooling is no longer sufficient to carry off the heat. It is therefore common practice to cool the drive motor and transmission with water, oil or other coolant. Here, such liquid cooling is implemented in various forms. For example, it has been proposed to cool the transmission via its end face connected to the drive motor by integrating a water flow in the motor flange for cooling, so that the heat of the transmission can be dissipated via the end face of the transmission connected to the motor. This is sufficient in itself for a shorter or single-stage transmission, whereas in an axially longer design with a plurality of transmission stages (as is customary, for example, in tunnel boring machines), such cooling of the front face of the transmission does not dissipate sufficient heat and, in particular, the transmission stages axially spaced apart from the front face overheat.

In order to cool the transmission particularly completely, it has also been proposed to lead the transmission oil in the circuit out of the transmission, cool it externally and transport it back again to the transmission. However, such circulation of transmission oil with external cooling is very complex and is subject to a number of boundary conditions regarding circulation speed and pressure in order to always ensure adequate and complete lubrication of all transmission elements.

Although cooling of the drive and/or transmission unit is usually involved, it may also be necessary or at least useful in very cold ambient conditions, for example when the drilling rig is stopped overnight or on a weekend in arctic conditions, to heat the drive and/or transmission unit and bring it to the operating temperature, for example in order to facilitate start-up and also to ensure complete lubrication when started in very cold temperatures.

Disclosure of Invention

It is therefore an object of the present invention to provide an improved temperature control device of the above-mentioned type, as well as an improved drive and/or transmission unit and an improved tunnel boring machine, which avoid the disadvantages of the prior art and further develop the prior art in an advantageous manner. In particular, robust temperature control which can withstand the harsh construction site conditions should be achieved by a device which is simple in construction and easy to replace, which can be subsequently selectively retrofitted to drive and/or transmission units which have temperature problems under certain operating conditions.

According to the invention, this object is achieved by a temperature control device according to claim 1, a transmission and/or drive unit according to claim 11 and a tunnel boring machine according to claim 14. Preferred embodiments of the invention are the subject of the dependent claims.

It is therefore proposed to design the temperature control means in the form of a separate heat exchanger module separate from the transmission means, which can be inserted in a sandwich-like manner between the two transmission and/or drive parts in order to extract or provide heat at the interface of the two transmission and/or drive parts. Due to the modular construction of the transmission and/or drive unit and the temperature control device, the transmission and/or drive unit can also be retrofitted afterwards in a very simple manner in the event of temperature problems. According to the invention, at least one heat exchanger module of the temperature control device forms an annular body for fitting in a sandwich-like manner between two transmission and/or drive parts, which annular body comprises a central through slot allowing the drive element to pass through and has, on each of the opposite end faces, a connecting flange connecting the end face to the two transmission and/or drive parts in a precisely fitting manner. Through which a drive shaft or a drive wheel or another drive element, for example, for connecting two transmission stages or two transmission and/or drive sections in a force or torque transmitting manner is guided. The heat exchanger module can thus be integrated in a simple manner into the drive or transmission unit without having to be adapted in a special manner to the transmission or drive unit. The shape of the opposing connection flanges of the heat exchanger ring body is matched to the shape of the flange of the transmission and/or drive part to be connected, so that the transmission or drive part can be fitted and connected to the connection flanges in a precisely fitting manner.

In particular, transmission or drive parts, which are to be fitted sandwich-like with the heat exchanger module between them, can be connected in a fluid-tight manner to the connection flanges of the heat exchanger, wherein the transmission and/or drive parts can be fastened to the opposite connection flanges of the heat exchanger module, in particular by means of corresponding housing parts.

The opposite connecting flanges of the annular body of the heat exchanger module can be adapted in shape to the edge-side connecting flanges of the two housing parts and fastened thereto in a fluid-tight manner, which housing parts can together form the transmission housing and/or can form separate housing parts of separate transmission stages.

In a further development of the invention, the liquid jacket of the heat exchanger module, through which liquid can flow, can form an annular chamber inside the annular body, which extends in a manner surrounding the through slot. By means of such an annular chamber surrounding the through slots, the cooling liquid can flow around the through slots and cool the walls of the annular body over a large area and thus absorb and dissipate a large amount of heat.

In order to achieve a robust and at the same time effective design in terms of heat conduction, the annular body in the modified example of the invention may comprise a solid outer ring on which two opposing connection flanges are formed, an inner ring accommodated in the outer ring, and two preferably substantially plate-shaped end walls which connect the outer ring and the inner ring to one another and delimit between them a liquid jacket, in particular the annular chamber.

Such a solid outer ring, which can be designed as a solid body made of a metallic material, for example, gives the heat exchanger module sufficient robustness for stably interconnecting the two transmission and/or drive parts and also protects the heat exchanger module itself from the harsh environmental conditions of the construction site. At the same time, the box-like structure with the plate-shaped end walls interconnecting the inner and outer rings and delimiting the liquid jacket achieves an overall simple structure, wherein the end walls form a large heat transfer surface which can transfer a large amount of heat to the flowing liquid.

In order to achieve a lightweight design of the whole, the end wall can have a significantly smaller wall thickness than a solid outer ring. For example, a thin metal plate may be provided as an end wall, which may be, for example, welded and/or glued and/or cast or otherwise liquid-tightly fastened to the solid outer and inner rings at the time of casting. In an advantageous development of the invention, the wall thickness of the plate-shaped end wall can be less than one third of the outer ring thickness (in particular the axial dimension of the outer ring) or also less than one quarter of the outer ring thickness.

The wall thickness of the inner ring can also be significantly smaller than the wall thickness of the outer ring, regardless of the wall thickness of the plate-shaped end wall. For example, the radially measured thickness of the inner ring may be less than 50% of the radially measured thickness of the outer ring, wherein the inner ring and the outer ring may have the same axial dimension, in particular when the plate-shaped end walls are arranged parallel to each other.

In general, the heat exchanger designed as a ring can be designed in a disk-shaped manner, in particular in the form of a thin plate with a through-opening in the center. For example, such a disk-shaped design of the annular body may be characterized by at least substantially parallel end faces. Independently of this, the outer surface and/or the inner surface of the annular body, which can be formed by the outer shell side of the outer ring and/or the inner shell side of the inner ring, can have a substantially cylindrical contour, in particular a roughly cylindrical contour.

Advantageously, the liquid jacket of the heat exchanger module may comprise an inlet and an outlet in order to be able to cool or, if necessary, also heat the temperature control liquid flowing through from the outside (i.e. outside the heat exchanger module or its liquid chamber). In particular, the heat exchanger module may comprise at least one inflow terminal and at least one outflow terminal, in order to be able to connect an external coolant circuit of a respective machine with respective inflow and outflow lines to the heat exchanger module in a simple manner.

Advantageously, the inflow and outflow terminals can be arranged on the outer ring of the ring body of the heat exchanger module in order to be able to feed the temperature-control liquid through the outer ring into the ring chamber and to be able to discharge it again from the ring chamber.

Advantageously, the inlet and the outlet of the annular chamber can be arranged next to one another or in the same section (Sektor) of the annular body of the heat exchanger and separated from one another by a partition plate arranged in the annular chamber, which partition plate divides the annular chamber in the circumferential direction into two annular regions in the manner of a split ring. By arranging the inlet and outlet in the same section of the annular body or annular chamber, it is ensured that the temperature control liquid surrounds and circulates through the entire annular chamber, wherein the partition plate prevents short-circuiting of the flow and ensures that the fluid has to circulate through the entire heat exchanger or the entire annular chamber.

The inlet and outlet terminals may include fluid-tight couplings, such as plug-in couplings or bolted couplings for connecting temperature control fluid lines.

Advantageously, the inlet and the outlet may be arranged on the upper side of the annular body (e.g. not far forward and backward in the 12 o' clock direction) in order to not only feed the temperature control fluid on the upper side but also to discharge it on the upper side. This arrangement of the inlet and outlet of the temperature control fluid circuit on the upper side ensures that the temperature control fluid flows through the entire liquid jacket, in particular through the entire annular chamber. In an advantageous development of the invention, it is possible to provide turbulence plates and/or distributor plates in said annular chamber through which the temperature control fluid flows, which turbulence plates and/or distributor plates are arranged in particular radially offset to one another, so that the temperature control liquid has to flow back and forth in a zigzag or serpentine manner in order to be able to pass through the turbulence plates. If the annular chamber is delimited by an inner ring and an outer ring in the manner described, the turbulence plates may be arranged to project alternately outwards from the inner ring and inwards from the outer ring. The turbulence plates can extend over the entire width or thickness of the annular chamber, i.e. they can be arranged on both sides of the two plate-shaped end walls, so that channels remain only at the radially inner ends or at the radially outer ends, respectively, of the alternately arranged turbulence plates.

Alternatively or additionally, however, it is also conceivable to arrange the turbulence plates such that the cooled or heated liquid flows back and forth in a meandering manner between two plate-shaped end walls delimiting the end faces of the annular chamber. To achieve this, the turbulence plates may each leave a channel gap with one of the two end walls, wherein the turbulence plates are alternately connected to one end wall and the other end wall.

However, a meandering flow path to and from the inner ring to the outer ring or the like lengthens the flow path through the annular chamber and accordingly lengthens the residence time of the circulating temperature control liquid in the annular chamber, so that a better heat transfer can be achieved.

In order to achieve temperature equalization of the two transmission and/or drive sections separated from each other by the heat exchanger module, the heat exchanger module may advantageously comprise a plurality of through slots in the region of the outer circumferential portion of the ring body. In particular, the above-mentioned outer ring may be provided with a plurality of through holes or through slots in order to achieve an exchange of transmission oil or lubricant from one transmission and/or drive part to another in an area close to the transmission and/or drive housing wall. For example, if a planetary gear stage comprising a ring gear on the outer circumference is provided in one of the gear parts, lubricant that is squeezed out of the teeth at the cavities can escape through the through-openings, so that the squeezed out oil gives up heat when it comes into direct contact with the heat exchanger module and overheating of the ring gear region is avoided.

The through holes may be dispersedly arranged in a circumferential direction of the heat exchanger module.

The through slots may be positioned radially inward of the opposing attachment flanges.

In a further development of the invention, gear stages, preferably in the form of planetary gear stages, can be arranged on both sides of the heat exchanger module. The two transmission stages can be connected to each other in a force and torque transmitting manner by means of a sun wheel and/or a planet carrier web, which extends through the through-slots of the ring-shaped heat exchanger module.

In a further development of the invention, at least one heat exchanger module can be arranged between the two first transmission stages closest to the drive motor in order to be able to dissipate the heat load generated there. In particular, the power losses and the heat generated thereby are greatest in the first, high-speed gear stage, so that the heat load can be reduced particularly effectively by inserting a heat exchanger module between the first two gear stages.

In a further development of the invention, a plurality of heat exchanger modules of the type described can also be arranged between a plurality of adjacent pairs of transmission stages, for example between a first and a second transmission stage and between a second and a third transmission stage. The gear stages can advantageously each be designed as a planetary gear stage.

In principle, it is also possible to arrange a heat exchanger module between the first transmission stage and the drive motor connected thereto. In this case, one of the connection flanges of the annular body of the heat exchanger module can be mounted to the drive motor housing and the other drive flange can be mounted to the transmission housing and can therefore be connected in a fluid-tight manner.

Drawings

The invention will be explained in more detail below on the basis of preferred exemplary embodiments and the associated figures.

Fig. 1 shows a schematic representation of a drive and transmission unit of a tunnel boring machine, wherein the transmission comprises a plurality of planetary transmission stages and a heat exchanger module according to an advantageous embodiment of the invention is arranged between a first transmission stage and a second transmission stage.

Fig. 2 shows a perspective view of a disc heat exchanger module of the drive and transmission unit of fig. 1.

Fig. 3 shows a partially cut-away perspective view of the disc heat exchanger module of fig. 2, showing the internal structure of the annular chamber through which fluid can flow and the turbulence plates arranged thereon.

Detailed Description

As shown in fig. 1, the tunnel boring machine 1 may comprise a rotatably driven milling rotor-like drill bit (Bohrkopf)2, which is rotationally driven by a drive motor 3 via a transmission unit 4. The drill head 2 can be driven by a gear unit 4, for example by a toothed ring, and can be supported in a known manner by means of a drill head bearing 5.

As shown in fig. 1, the gear unit 4 can be formed by a plurality of gear stages which are connected in series to convert or reduce the drive rotational speed of the drive motor 3 to the desired rotor rotational speed of the drill head 2, wherein, for example, three gear stages 4.1, 4.2 and 4.3 can be provided.

The gear stages can be planetary stages, which can each comprise a sun gear 6, a ring gear 7 and planetary gears 8 meshing therewith, which can be arranged on a planet carrier 9. Adjacent planetary stages can be connected to one another on the connecting rods (stem) of the sun gear and the planet carrier (see fig. 1).

The gear stages 4.1, 4.2 and 4.3 can each be designed independently of one another and each comprise an at least approximately cylindrical gear housing part, by means of which the gear stages can be placed next to one another, so that the gear unit 4 is constructed in a modular manner in its entirety from a plurality of gear stages which are arranged axially in succession and are connected to one another.

The first gear stage 4.1 can be connected to the drive motor 3, wherein, for example, the motor output shaft 10 can be coupled in a non-rotatable manner to the sun gear 4 of the first gear stage 4.1. The output shaft of the end transmission stage 4.3 (e.g. the connecting rod of the planet carrier 9) may be coupled to the drive shaft of the drilling rotor 2, for example by a toothed ring.

As shown in fig. 1, a heat exchanger module 11 can be inserted between two adjacent transmission ratio stages, in particular between the first and second relatively rapidly rotating transmission ratio stages 4.1 and 4.2, which heat exchanger module is fitted in a sandwich-like manner between the end faces of the adjacent transmission ratio stages 4.1 and 4.2. The heat exchanger module 11 can in this case rigidly connect the housing parts of the first and second transmission stages 4.1 and 4.2 to one another, for example, by means of screw connections for clamping the two housing parts 12.1 and 12.2 to the heat exchanger module 11.

The heat exchanger module 11 will be shown in more detail in fig. 2 and 3 and may be designed as a disc when viewed in its entirety. In particular, the heat exchanger module 11 can form an annular body which has a through slot 13 in a central portion and, on each of the opposite end faces, a connecting flange (Anschlussflansch)14 and 15, the shape and size of which is adapted to the connecting flanges of the two transmission stages 4.1 and 4.2, so that the transmission stages 4.1 and 4.2 can be fitted precisely on the two connecting flanges 14 and 15 of the heat exchanger module 11 and can therefore be connected preferably without play, in particular in a fluid-tight manner. As shown in fig. 2 and 3, the connecting flanges 14 and 15 may, for example, each have a flat, annular end face 16, which may extend substantially parallel to one another and/or in a plane perpendicular to the longitudinal axis of the transmission unit. The end faces 16 of the connecting flanges 14 and 15 can be delimited on the inner edge (but also on the outer edge) by an annular rib (ringstem) 17 projecting at the end face, which annular rib 17 can be pushed into the housing part 12.1 or 12.2 of the adjoining transmission part 4.1 and 4.2 and can bear against the inner circumferential surface of the respective housing part, for example, in a precisely fitting manner. By means of the annular rib 17, the heat exchanger module 11 can be guided in the radial direction in a precisely fitting manner onto the housing parts 12.1 and 12.2 of the adjacent transmission part.

In order to be able to rigidly connect the gear stages 4.1 and 4.2 to the heat exchanger module 11, bores 18 can be provided in the region of the connecting flanges 14 and 15 of the heat exchanger module 11 in order to be able to connect the two housing parts 12.1 and 12.2 to the heat exchanger module 11, for example by means of screws. A bolt may extend through the bore 18.

As shown in fig. 3, the heat exchanger module 11 may advantageously comprise a solid outer ring 19 made of solid material, on the end faces of which the connection flanges 14 and 15 may be formed.

Within said outer ring 19, the heat exchanger module 11 may comprise an inner ring 20, which delimits said through slots 13 of the heat exchanger module 11. The outer and inner rings 19, 20 may be interconnected by two plate-shaped end walls 21, 22 which delimit an annular chamber 23 between them and the inner and outer rings. The end walls 21 and 22 may for example be made of thin metal sheet or another highly heat conductive material.

Independently of this, the end walls 21 and 22 may be arranged parallel to each other and spaced apart from each other by a distance substantially corresponding to the axial width of the inner ring 20 and/or the outer ring 19.

The end walls 21 and 22 may be of substantially flat design, in particular forming two flat annular discs.

The end walls 21 and 22 are connected (e.g. welded and/or glued) in a fluid-tight manner to the outer ring 19 and the inner ring 20.

In order to be able to circulate the temperature-controlled liquid through the annular chamber 23, said annular chamber 23 has an inlet 24 and an outlet 25 which may advantageously extend through the outer ring 19 and may advantageously open on the outer circumference of said outer ring 19.

As shown in fig. 2, the inlet 24 and the outlet 25 may advantageously be arranged adjacent to each other and/or in the same section of the outer ring 19, in particular on the upper side of the heat exchanger module 11 when this is conventionally integrated into the drive unit 4.

In addition to the inlet 24 and the outlet 25, one or more further outlets 26 may be provided on the underside of the annular chamber 23 in order to be able to discharge cooling liquid from the annular chamber 23, wherein these outlets 26 may advantageously also extend through the outer ring 19 (see fig. 3).

To ensure that the temperature-controlled liquid flows through the entire annular chamber 23, a partition plate 27 can be provided in the annular chamber 23 between the inlet 24 and the outlet 25 arranged on the upper side, which partition plate divides the annular chamber 23 between the inlet 24 and the outlet 25 in the manner of a split ring (Schlitzrings). The partition plate 27 can be connected in a fluid-tight manner not only to the outer ring 19 and the inner ring 20 but also to the two end walls 21 and 22 spaced apart from one another.

Thus, the inlet 24 opens into the annular chamber 23 on one side of the partition plate 27, while the outlet 25 opens into the annular chamber 23 on the opposite side of the partition plate 27.

In order to guide the temperature-controlled liquid into all regions of the annular chamber 23 when it flows through the annular chamber 23, a turbulence plate (turbulenzstep) 28 may also be provided in the annular chamber 23, which turbulence plate may be arranged and designed such that the fluid flowing circumferentially through the annular chamber 23 meanders back and forth between the inner ring 20 and the outer ring 19 or flows back and forth in a serpentine manner in the direction of rotation. The turbulence plates 28 may be arranged alternately, radially offset from each other and alternately with respect to the inner ring 20 and the outer ring 19, with gaps remaining for the flow of temperature control liquid.

Independently of this, the turbulence plates 28 can extend between the two end walls 21 and 22 and connect them to each other, wherein the turbulence plates 28 can extend at least substantially in the radial direction or from the inside to the outside, i.e. in the direction from the inner ring to the outer ring, or vice versa.

In particular, said turbulence plates 28 can be connected alternately once to the inner ring 20 and once to the outer ring 19, and leave a gap 29 in each case on the other ring, through which gap 29 the temperature liquid can flow. The gaps 29 are here located alternately on the outer ring 19 and the inner ring 20 (see fig. 3).

The heat exchanger module 11 described has significant advantages. On the one hand, it is a low-cost and very robust structure which is also suitable for use in severe conditions of use, for example in tunnel boring machines, wherein in particular the strong outer ring can also withstand impact loads as occur in tunnel boring machines.

Here, both the thick outer ring 19 and the box-shaped structure, according to which the end walls 21 and 22 are connected to one another a number of times by means of the outer and inner rings and the turbulence plates, make it possible for damage to not occur even under strong vibrations, pressure peaks or other external influences. The heat exchanger module is integrated directly into the transmission unit 4 and is therefore also additionally protected against external influences.

The arrangement of the heat exchanger module 11 between the first two transmission stages 4.1 and 4.2 also produces excellent inflow conditions, wherein twice the effective area is produced by the two end walls 21 and 22 in contact with the lubricant of the transmission of the two transmission stages. The power loss is absorbed near the production site. In particular in the first high-speed gear stages 4.1 and 4.2, the power loss and the heat generated thereby are at a maximum.

Due to the radially offset arrangement of the turbulence plates or webs 28, the temperature control fluid flowing annularly around the through channel 13 is deflected several times, which ensures a maximum utilization of the overall circulating and heat transfer surface by means of the flow-dependent turbulence.

The heat exchanger module 11 is easily adaptable to existing transmission constructions. Here, the heat exchanger modules 11 can easily be placed between the planetary stages of the transmission unit 4, if desired.

Due to the modular design, a plurality of heat exchanger modules 11 can be connected in series one after the other and thus the cooling capacity can be increased almost arbitrarily.

The axial through-openings 30 or through-slots which are guided through the heat exchanger modules 11 in the axial direction allow oil which is pressed out of the tooth flanks at the level of the ring gear 7 of the planetary gear stage to flow through the through-slots 30 and to obtain a direct cooling effect. The through slots 30 also promote oil or lubricant exchange in the transmission unit 4 and ensure uniform mixing of the lubricant.