DE102018131638A1 - Motor-gear unit, in particular for a tunnel boring machine or for driving a ring gear - Google Patents

Abstract

Motor-gear unit, in particular for a tunnel boring machine or for driving a ring gear, comprising: a housing (10), an electric motor (20), in particular a synchronous motor, which has a rotor (22) which can be rotated relative to the housing (10), a drive shaft (1), which is coupled to the rotor (22) such that a rotation of the rotor (22) causes a rotation of the drive shaft (1) relative to the housing (10), a gear (80) with at least one planetary stage (50 , 60, 70) and an output member (2), the at least one planetary stage (50, 60, 70) coupling the drive shaft (1) to the output member (2) such that rotation of the drive shaft (1), in particular with a reduction in speed , is transmitted to the output member (2).

Description

The invention relates to a motor-gear unit, which is particularly adapted for use in a tunnel boring machine, for driving a drill head of a tunnel boring machine or for driving a ring gear. At the end pointing in the direction of advance, tunnel boring machines have a boring head which is rotated about an axis of rotation of the boring head in order to break down the material to be dismantled by the tunnel boring machine.

Tunnel boring machines are known from the prior art which have a boring head which is rotated about an axis of rotation of the boring head in order to break down the material to be mined by the tunnel boring machine. In order to set the drill head in rotation about its axis of rotation of the drill head, several motor-gear units are used in tunnel boring machines, which have an asynchronous motor designed as an electric motor that sets an input shaft of a gearbox in rotation, the rotation of the input shaft via the gearbox reducing the speed to Pinion is transmitted, which meshes with a ring gear. The ring gear is connected to the drill head so that it cannot rotate, so that rotation of the ring gear causes the drill head to rotate. In the case of the motor-transmission units from the prior art, it is also known to provide a holding brake which can fix the input shaft of the transmission in relation to the housing. For this purpose, the holding brake is flanged between the gear housing and the motor housing. In the prior art, an overload clutch forms the end of the motor-gear unit facing away from an output member.

The components of the known motor-gear units are usually manufactured by several suppliers and then assembled together. The motors used in the prior art for this purpose are generally heavy and massive and require a lot of space. In addition, in the known designs, the maximum permissible speeds for the motors are relatively low in order to keep the heat development on the bearing of the rotor and electrical losses within limits.

The present invention is based on the object of specifying a better motor-gear unit, in particular for a ring gear drive or for driving a drill head of a tunnel boring machine, in particular reducing the installation space of the motor-gear unit and in particular increasing the efficiency.

The object is achieved with the subject matter of claim 1. Advantageous further developments result from the dependent claims, including the independent claims 14 and 15, the description and the figures.

The invention is based on a motor-gear unit, which is designed, for example, as part of a drive for a ring gear and / or a drill head of a tunnel boring machine. The motor-gear unit can also be used for other applications besides the above. For example, the motor-gear unit can be provided and designed to drive a gear rim of a crane (slewing gear) or to drive a winch.

The motor-transmission unit comprises a housing, which can basically be made in one part, but preferably in several parts. Furthermore, the motor-gear unit comprises an electric motor which has a rotor which can be rotated relative to the housing. The electric motor can also have a stator, which is twistable or stationary with respect to the housing. The rotor is rotatable about a rotor axis of rotation. For example, the stator can have coils that are adapted to generate a rotating magnetic field. The rotor can be constantly magnetized, in particular have at least one magnet which is carried along by the rotating field generated by the stator, as a result of which the rotor is set in rotation about the axis of rotation. Alternatively or additionally, the electric motor is a synchronous motor (single-phase or three-phase synchronous machine in motor operation). The synchronous motor is more compact and efficient than asynchronous motors used for this application. This allows the installation space and weight of the motor-gear unit to be reduced.

The motor-gear unit also has a drive shaft that is coupled to the rotor such that rotation of the rotor causes the drive shaft to rotate relative to the housing. For example, the drive shaft can be in direct engagement with the rotor, in particular by means of a shaft-hub connection. Alternatively, the rotor can be coupled to the drive shaft via an overload safety device, for example a component with a predetermined breaking point or an overload clutch, which is also known as a safety clutch. This means that an overload safety device is arranged kinematically between the drive shaft and the electric motor. The overload protection (predetermined breaking point, overload clutch, safety clutch) is adapted to separate the electric motor from the drive shaft if the torque acting between the electric motor and the drive shaft exceeds a permissible limit (limit torque). This protects the electric motor and / or the drive train from damage caused by impermissibly high torques.

A component with a predetermined breaking point can have a point, for example a notch, a section with a diameter reduction or the like, at which the component breaks - or is generally destroyed - if the limit torque is exceeded. Since the component is destroyed when the limit torque is exceeded, it can then be exchanged or replaced.

The overload clutch can have, for example, a clutch input member and a clutch output member which, as long as the limit torque is not exceeded, are non-rotatable relative to one another about the axis of rotation. If the limit torque is exceeded, the clutch input member and the clutch output member can be rotated relative to one another about the axis of rotation. For example, a non-positive and / or positive connection, in particular with other components, can be provided between the clutch input member and the clutch output member. These components can be balls and springs, for example. The clutch input member can be connected directly or indirectly to the rotor, for example in a rotationally fixed manner. Rotation of the rotor can cause rotation of the clutch input member. The clutch output member can be connected indirectly or directly, for example by means of a shaft-hub connection, to the drive shaft, in particular non-rotatably. The overload clutch can be designed such that - in contrast to a component with a predetermined breaking point - it separates the rotor from the drive shaft without destruction. For example, the overload clutch can be designed so that it engages automatically, i.e. connects the rotor to the drive shaft in a torsion-proof manner when the torque falls back to or below the limit torque. Alternatively, the overload clutch can be designed such that it must be engaged by hand or by further intervention, i.e. the rotor must be connected to the drive shaft in a torsion-proof manner when the torque drops to or below the limit torque. Without further action, the clutch would remain disengaged, even if the torque fell back to or below the limit torque.

The motor-transmission unit further comprises a transmission with at least one planetary stage, for example a single, two, three, four, five or even more planetary stages, and an output element. The at least one planetary stage is adapted to couple the drive shaft to the output member in such a way that rotation of the drive shaft, in particular with a reduction in speed, is transmitted to the output member. A transmission of the speed reduction is understood to mean that the speed of the rotor of the electric motor is higher than the speed of the output member.

The output member can be, for example, a shaft, a hub or a pinion, for example for engagement in a toothed ring. The output member designed as a shaft or hub can be adapted for a shaft-hub connection. For example, a shaft can be connected non-rotatably to the output element configured as a hub, in particular by means of the shaft-hub connection. Alternatively, a hub, in particular by means of the shaft-hub connection, can be connected non-rotatably to the output element designed as a shaft. For example, the shaft or hub connected to the output member can be part of a drive train following the motor-transmission unit. In particular, the shaft or hub connected or connectable to the output member can be connected in a rotationally fixed manner to a pinion (gear).

The invention further relates to a ring gear drive, in particular for a tunnel boring machine or the slewing ring of a crane or generally for an application in which a ring gear is to be driven by a motor-gear unit. The sprocket drive comprises a sprocket rotatably mounted about a sprocket axis of rotation. The ring gear can be designed as an external gear or as an internal gear. The ring gear drive can at least one, d. H. have a single or multiple engine-transmission units described herein. The axis of rotation of the respective motor-gear unit can be offset, in particular offset parallel to the axis of rotation of the ring gear. In the case of several, for example two, four, eight, twelve or sixteen, motor-gear units, these can be distributed over the circumference of the ring gear, in particular evenly or unevenly distributed. For example, designs are possible in which at least one of the motor-gear units has a holding brake. In particular, one or more, for example two, of the motor-gear units can each have a holding brake, the rest of the motor-gear units being designed without a holding brake. Alternatively, ring gear drives are possible in which the motor-gear unit has no holding brake or none of the several motor-gear units has a holding brake. Alternatively, ring gear drives are possible in which the motor-gear unit or each of the several motor-gear units has a holding brake.

One pinion can be provided for each motor-gear unit, which meshes with the toothing of the ring gear and is coupled to the output member, in particular non-rotatably, or corresponds to the output member, so that rotation of the output member, in particular about the axis of rotation, of its motor-gear unit causes rotation of the ring gear about the axis of rotation of the ring gear. Each motor-gear unit can be coupled to the toothed ring via the pinion, which meshes with the toothing of the toothed ring or, in other versions, to a drilling head of a tunnel boring machine. The invention further relates to a tunnel boring machine which comprises a ring gear drive described herein and a drilling head. The gear rim axis of rotation can be arranged, for example, in or parallel to the direction of advance of a tunnel boring machine.

The drill head is arranged at the end of the tunnel boring machine pointing in the direction of advance of the tunnel boring machine or forms the end pointing in the direction of advance of the tunnel boring machine. The drill head can be rotated about an axis of rotation of the drill head to remove the material to be removed from the tunnel boring machine or is rotated for removal. The ring gear and the drill head are coupled, in particular non-rotatably or by means of an intermediate gear, that rotation of the ring gear causes the drill head to rotate about the axis of rotation of the drill head. For example, the axis of rotation of the drill head and the axis of rotation of the ring gear can be parallel to one another. In particular, the axis of rotation of the drill head can be the axis of rotation of the ring gear. The rotation of the drill head around the axis of rotation of the drill head or the axis of rotation of the ring gear or of the ring gear around the axis of rotation of the ring gear is brought about by the rotation of the rotor of the motor / gear unit (s).

In further developments, the electric motor can be arranged between, in particular geometrically between, the overload protection, in particular overload clutch, and the at least one planetary stage or the gear. This means that the transmission with the at least one planetary stage and the overload protection, in particular overload clutch, are arranged on one end of the electric motor. The drive shaft can extend through the rotor, in particular through a passage or a hollow shaft of the rotor. In general, it is preferred that the drive shaft rotates about the axis of rotation about which the rotor also rotates. The axis of rotation of the drive shaft corresponds to its central axis. The drive shaft can be mounted on the rotor without torque transmission, so that rotation of the drive shaft relative to the rotor is fundamentally possible. The torque between the rotor and drive shaft is then transmitted via the optional overload protection. If the overload safety device separates the drive shaft from the rotor when the limit torque is exceeded, the drive shaft and rotor can rotate relative to one another about the axis of rotation.

The drive shaft can protrude from the end face of the electric motor on which the transmission with the at least one planetary stage is located. Alternatively or additionally, the drive shaft can protrude from the end face of the electric motor on which the overload protection or overload clutch is located.

For example, the overload safety device or clutch can be located on a first side of the electric motor and the transmission with the at least one planetary stage can be located on a second side of the electric motor. The drive shaft can connect a part of the overload protection device, in particular a clutch output element or a predetermined breaking point, to a part of the at least one planetary stage, for example a sun gear of the at least one planetary stage. Alternatively, the drive shaft can form the overload protection, in particular the component with a predetermined breaking point.

For example, the sun gear driven by the drive shaft can be part of a first planetary stage. The first planetary stage can have a ring gear which is connected in a rotationally fixed manner to the housing, in particular a gear housing, or is formed by the housing or gear housing. One or more planet gears can mesh with both the sun gear of the first planetary stage and the ring gear of the first planetary stage. A planet carrier on which the planet gears are rotatably arranged can be rotated about the axis of rotation by rotating the sun gear of the first planetary stage. For example, the planet carrier of the first planetary stage can form the output member or be connected to the output member in a rotationally fixed manner, in particular if only a single planetary stage is provided. In the case of a plurality of planetary stages, the planet carrier of the first planetary stage can form a sun gear of a second planetary stage or can be connected in a rotationally fixed manner to the sun gear of the second planetary stage. The second planetary stage can have a ring gear which is connected in a rotationally fixed manner to the housing, in particular the transmission housing, or which is formed by the housing or transmission housing. One or several planet gears can mesh with the ring gear of the second planetary stage and the sun gear of the second planetary stage. Rotation of the second sun gear about the axis of rotation causes rotation of the second planet carrier about the axis of rotation.

The second planet carrier can form the output member or can be connected to the output member in a rotationally fixed manner, in particular if two planetary stages are provided. Alternatively, a third planetary stage can be provided, the planet carrier of the second planetary stage forming the sun gear of the third planetary stage or being connected to it in a rotationally fixed manner. A ring gear of the third planetary stage can be non-rotatably connected to the housing, in particular the gear housing, or can be formed by the housing or gear housing. One or more planet gears can mesh with the ring gear of the third planetary stage and the sun gear of the third planetary stage. Rotation of the sun gear of the third planetary stage causes rotation of the planet carrier of the third planetary stage about the axis of rotation. The planet carrier of the third planetary stage can be non-rotatably connected to the output member or form the output member. Alternatively, a fourth planetary stage can be provided, which, like the aforementioned planetary stages, can be connected to the third planetary stage and the output element. The aforementioned interconnection of several planetary stages is only an example. Other interconnections of planetary stages or other intermediate gears are also possible.

The motor-gear unit can also have a brake, in particular a holding brake, which is adapted to be able to fix the drive shaft in a rotationally fixed manner with respect to the housing of the motor-gear unit. The holding brake serves to fix the drive shaft with respect to the housing at standstill or almost at standstill in order to block rotation of the drive shaft relative to the housing. Alternatively, the brake can be a service brake or a combined service and holding brake.

The overload clutch can be arranged between, in particular geometrically between, the brake and the electric motor. I.e. The electric motor is arranged on a (first) side of the overload clutch, the brake being arranged on the other (second) side of the overload clutch. In particular, the brake can form the end of the motor-transmission unit opposite the output member. Such an arrangement of the brake increases the serviceability of the motor-transmission unit, since both the accessibility of the brake and the accessibility of the safety clutch are simplified. In contrast to designs in which the brake is arranged between the transmission and the electric motor, in addition to increasing the ease of servicing, advantages can also be achieved with regard to the “transmission - electric motor” interface, as described below.

Alternatively or additionally, the electric motor can be arranged between, in particular geometrically between, the brake, which is located on a first side of the electric motor, and the transmission with the at least one planetary stage, which is located on a second side of the electric motor.

The brake can have at least one first brake body and at least one second brake body. The at least one second brake body can be connected or connectable to the drive shaft such that it cannot rotate about the axis of rotation. For example, the at least one second brake body can be held by a second brake body carrier, which is connected in a rotationally fixed manner, in particular by means of a shaft-hub connection, to the drive shaft or engages in the drive shaft. For example, in versions with an overload or safety clutch, the second brake body carrier can be separate from the clutch output member, or alternatively it can be mounted on the clutch output member in a rotationally fixed manner, or it can be formed by the clutch output member. The at least one first brake body can be held non-rotatably about the axis of rotation by a first brake body carrier, which is formed by the housing, in particular a brake housing or a clutch housing of the overload or safety clutch, or non-rotatably with the housing, in particular the brake housing or the clutch housing, connected is. For example, an electromechanically, hydraulically or pneumatically actuated pressure piece can be provided, which presses the at least one first brake body and the at least one second brake body against one another to produce a frictional engagement, in particular static frictional engagement, acting between the first and second brake bodies. Alternatively, one or more springs, in particular mechanical springs, can be provided for pressing against one another, which are preloaded in such a way that they press the at least one first brake body and the at least one second brake body against one another. To release the brake, the pressure piece can be moved, for example, electromechanically, hydraulically or pneumatically against the spring force, in order to reduce the force with which the first and second brake bodies are pressed against one another, as a result of which the brake is released.

One of the at least one first brake body and the at least one second brake body can be a brake disk or a multiplicity of brake plates, the other of the at least one first brake body and the at least one second brake body one or more brake shoes which can interact with the brake disk, or a plurality of brake disks, which can interact with the brake disks that form the at least one first brake body.

In further developments, a first roller bearing and a second roller bearing can be provided, by means of which the rotor of the electric motor is supported on the housing, in particular an electric motor or motor housing, so that it can rotate about the axis of rotation. For example, the motor housing can have a first end wall on which the first roller bearing is supported or on which the first roller bearing is mounted, and have a second end wall on which the second roller bearing is supported or on which the second one Rolling bearing is stored. The first end wall of the motor housing can be formed, for example, by a bottom of a pot-shaped motor housing or alternatively by a housing cover. Alternatively or additionally, the second end wall of the motor housing can be formed by a bottom of a pot-shaped motor housing or a housing cover.

In further developments, the at least one planetary stage can be arranged in a receiving space formed by the housing, in particular the transmission housing, the receiving space being connected to at least one of the two rolling bearings in a liquid-communicating, in particular lubricant-communicating manner. This advantageously has the effect that the roller bearing, which communicates with the receiving space in a liquid-communicating manner, is wetted by the in particular liquid lubricant, for example lubricating oil of the transmission, whereby the roller bearing is lubricated on the one hand and heat is removed from the roller bearing on the other.

The lubrication of the at least one planetary stage in the receiving space is preferably carried out as splash lubrication. A minimum fill level can be provided for splash lubrication, which is designed such that the roller bearing or bearings are wetted in the intended operating position. In the intended operating position, the axis of rotation of the motor-transmission unit preferably extends essentially horizontally with respect to the earth's gravitational field.

The end wall, in particular a housing cover, of the electric motor, on which the roller bearing, for example the second roller bearing, is arranged, can have an opening which enables the lubricant to get into the roller bearing from the receiving space of the transmission.

For example, the receiving space in which the at least one planetary stage is arranged and a receiving space formed by the housing, in particular the motor housing and in which the rotor is arranged, can be sealed off from one another in a liquid-tight manner. The seal prevents lubricant from getting into the receiving area of the engine from the receiving area of the transmission. Since the second roller bearing, which rotatably supports the rotor on the motor housing, for example a housing base or a housing cover, about the axis of rotation, is wetted by the lubricant from the receiving space of the transmission and, on the other hand, it is to be prevented that lubricant gets into the receiving space of the motor, For example, a seal can be provided, in particular a shaft sealing ring or a radial shaft sealing ring, which seals at least one of the first and second rolling bearings to the receiving space of the motor. This has the effect that, on the one hand, the first and / or the second rolling bearing can be wetted with lubricant from the receiving space and, on the other hand, prevents lubricant from penetrating into the receiving space of the engine. For example, an end wall, in particular the housing cover, arranged between the gear housing and the motor housing can have an inner circumferential surface which forms a bearing seat for a roller bearing, in particular the second roller bearing, in particular for its outer ring. The rotor can have an outer peripheral surface, which forms a bearing seat for the rolling bearing, in particular the inner ring of the rolling bearing. As a result, the rotor can be supported on the end wall, in particular the housing cover, so that it can rotate about the axis of rotation.

Alternatively or additionally, the end wall of the electric motor, in particular a housing cover, arranged between the clutch housing and the motor housing can have an inner peripheral surface which forms a bearing seat for a rolling bearing, in particular the first rolling bearing and / or the outer ring of the rolling bearing. The rotor can have an outer peripheral surface, which forms a bearing seat for the rolling bearing, in particular its inner ring. As a result, the rotor can be supported on the end wall of the motor housing, in particular the housing cover, so that it can rotate about the axis of rotation. The end wall arranged between the electric motor and the transmission, in particular the housing cover, of the motor housing and / or the end wall arranged between the overload clutch and the motor, in particular housing cover, of the motor housing, can have an inner peripheral surface on which a seal, in particular a shaft sealing ring or radial shaft sealing ring, is seated which forms a sealing gap with an outer peripheral surface of the rotor. The seal can seal the first roller bearing, or preferably the second roller bearing, from the receiving space in which the rotor is located in a liquid-tight manner. In particular, a seal can be arranged between the second roller bearing and the receiving space and / or a seal between the first roller bearing and the receiving space.

In preferred developments, the motor-gear unit can have a housing cover between the gear housing, in which the at least one planetary stage is arranged, and the motor housing, in which the rotor is arranged, which cover forms the end wall, in particular the second end wall, of the motor housing . The housing cover can form a cover for the front end of the gear housing facing the electric motor as well as a cover for the front end of the motor housing facing the gear. That is, that for both the transmission case and the motor case common cover is provided. Compared to conventional solutions, in which the gear housing has its own cover and the motor housing has its own cover, the present embodiment can further shorten the overall length of the motor-transmission unit and reduce the weight. In addition, the common housing cover in particular can be used to lubricate the second roller bearing with the lubricant of the transmission.

In further developments, in which the at least one planetary stage is arranged in a receiving space formed by the gear housing, the gear housing can have one or more grooves or one or more channels, in particular grooves or channels that are open towards the electric motor, on its end face that faces the electric motor connects or connects a coolant supply connection, which is formed on the transmission housing, in a liquid-communicating manner to a coolant discharge connection, which is also formed on the transmission housing. This means that the coolant, which is fed via the coolant supply connection to the coolant discharge connection, flows through the groove (s) or the channel (s) and in the process removes heat from the transmission housing and any adjacent components. In particular, the at least one groove or the at least one channel can be closed off from the end wall arranged between the transmission and the electric motor, in particular the front cover of the housing, to the electric motor. The end wall or the housing cover thus form a wall of the fluid channel closed thereby in cross section, which connects the coolant supply connection to the coolant discharge connection in a fluid-communicating manner.

For example, the fluid path leading from the coolant supply connection to the coolant discharge connection, i. H. the fluid channel formed by the one or more grooves can be fluidically separated from the receiving space, in which the at least one planetary stage is arranged, or be sealed off from the receiving space. This enables a different liquid, such as water, to be used for cooling the transmission and / or the electric motor than the lubricant, such as lubricating oil, which lubricates the at least one planetary stage and possibly the first and / or second rolling bearing .

Characterized in that the end wall of the electric motor closes the groove or pointing grooves pointing towards the electric motor, the end wall, in particular the housing cover of the motor housing, can also be cooled by means of the coolant flowing through the groove or grooves, whereby an improved motor cooling is achieved.

• 1 eine Schnittansicht/Skizze einer erfindungsgemäßen Motor-Getriebe-Einheit,
• 2 eine perspektivische Ansicht eines Zahnkranzantriebs, insbesondere einer Tunnelbohrmaschine, mit einer Motor-Getriebe-Einheit aus 1.

The invention has been described with reference to several embodiments and examples. An embodiment of the invention is described below with reference to figures. The features disclosed in this case ₌ advantageously form the subject of the invention individually and in any combination of features. Show it:

• 1 2 shows a sectional view / sketch of a motor-transmission unit according to the invention,
• 2nd a perspective view of a ring gear drive, in particular a tunnel boring machine, with a motor-gear unit 1 .

2nd describes a ring gear drive, for example for a tunnel boring machine. 1 shows the engine-gearbox unit 2nd in a sectional view. The motor-gear unit is on a machine frame 100 attached, in particular attached so that a housing 10th the motor-gear unit around the axis of rotation D is rotatably attached to the machine frame. For example, the housing 10th placed on the machine by means of bolts 100 be or will be attached.

The ring gear drive also has a ring gear 110 on, which is rotatably mounted on a ring gear carrier, for example by means of a rolling or sliding bearing about a gear wheel axis of rotation. The ring gear 110 has external teeth in the example shown. Alternatively, the ring gear can have internal teeth. A pinion engages in the ring gear 120 a, which has an external toothing and engages in the outer toothing of the ring gear or alternatively in the inner toothing of the ring gear or meshes therewith. A rotation of the pinion 120 thus causes the ring gear to rotate 110 around the ring gear rotation axis. The pinion 120 is by means of a shaft-hub connection with an output member 2nd ( 1 ) non-rotatably connected. A rotation of the output member 2nd causes the pinion to rotate 120 and thus indirectly a rotation of the ring gear 110 . The ring gear 110 can be rotatably connected or coupled to a drill head (not shown) of a tunnel boring machine, with a rotation of the ring gear 110 around the sprocket axis of rotation causes the drill head to rotate about a drill head axis of rotation. Like from the 1 and 2nd is recognizable, the motor-gear unit has an electric motor 20th , an overload or safety clutch 30th , a brake 40 , in particular holding brake, and a transmission 80 with a first planetary stage 50 , a second planetary stage 60 , a third planetary stage 70 and the output link 2nd on.

The electric motor 20th is designed as a synchronous machine in the example shown. The electric motor has a stator 21st with multiple windings around a soft iron core. The stator 21st is adapted, an electric rotating field for driving a rotor 22 to create. The rotor 22 has at least one permanent magnet which is generated by the rotating electrical field of the stator 21st around the axis of rotation D is rotatable. The rotor 22 is by means of a first rolling bearing 4th and a second roller bearing 5 around the axis of rotation D rotatable on a motor housing 25th of the electric motor supported. The engine case 25th forms a section of the multi-part housing 10th the engine-gearbox unit. The engine case 25th holds a recording room 12 one in which the rotor 22 and the stator 21st are arranged.

Due to the compact design of the motor-gear unit and the use of a synchronous motor, there may be a lot of heat that can be dissipated through the surface of the motor housing, for example. For this purpose, the motor housing can have cooling fins on its outside, for example. For example, the motor housing 25th a coolant supply port 29a and a coolant discharge port 29b exhibit. Via the coolant supply connection 29a can the electric motor 22 Coolant supplied and via the coolant discharge connection 29b can coolant from the electric motor 20th be dissipated. The coolant supply connection 29a and the coolant discharge connection 29b can via at least one coolant channel 29c of the motor housing 25th be connected so that this via the coolant supply connection 29a supplied coolant on the way to the coolant discharge connection 29b heats up and thus heat from the electric motor 22 dissipates. The engine case 25th has a first drum-shaped peripheral wall 27th and a second drum-shaped peripheral wall arranged concentrically thereto 26 on. The second peripheral wall 26 surrounds the first peripheral wall 27th circumferential. The peripheral walls 26 , 27th extend concentrically around the axis of rotation D . Between the first peripheral wall 27th and the second peripheral wall 26 is a spiral around the turning axis D extending coolant channel 29c educated. The coolant channel 29c extends from the coolant supply port 29a that on the second peripheral wall 26 is arranged helically around the axis of rotation D up to the coolant discharge connection 29b that on the second peripheral wall 26 is arranged. The outer circumference of the first circumferential wall 27th has at least one helical around the axis of rotation D circumferential protrusion on the inner circumference of the second circumferential wall 26 and therefore the helical channel 29c forms. The channel 29c is used to conduct a coolant for cooling the electric motor 20th , especially the stator 21st which is in particular thermally conductive with the first peripheral wall 27th connected, in particular on the inner circumference of the first circumferential wall 27th is arranged. On a first face of the peripheral walls 26 , 27th is that of the peripheral wall 27th edged recording room 12 to an overload clutch 30th towards a first end wall, that of a first housing cover 28 is formed, limited or closed. Instead of an overload clutch 30th the motor-gear unit can have another overload protection, for example a component with a predetermined breaking point (not shown). The first housing cover 28 has a connecting flange on which a clutch housing 31 attached or flanged by means of several bolts. To increase the stability of the first housing cover 28 this can optionally point up several reinforcing ribs to the connecting flange. The first housing cover 28 is by means of several bolts with the first peripheral wall 27th and the second peripheral wall 26 added.

The end face of the peripheral walls opposite the first end wall 26 , 27th is by means of a second end wall, which is supported by a second housing cover 7 is formed, limited or closed. The second housing cover 7 is by means of several bolts with the first peripheral wall 27th and / or the second peripheral wall 26 added. The second housing cover 28 has a connecting flange with a gear housing 81 of the transmission 80 can be connected, especially with the help of several bolts. In particular, the gear housing 81 by means of several bolts on the motor housing 25th , in particular the second housing cover 7 be flanged.

The first housing cover 28 and the second housing cover 7 each have an opening through which a drive shaft extends 1 extends.

It also extends through the passage of the first housing cover 28 a section of the rotor 22 that has a passage for the drive shaft 1 and forms an outer peripheral surface. The outer peripheral surface forms a bearing seat for a first roller bearing 4th , especially its inner ring. At the section of the rotor is the clutch input member 32 the clutch 30th is attached or flanged in a rotationally fixed manner, in particular by means of several screw bolts. The clutch input link 32 and the rotor 22 are about the axis of rotation D non-rotatably connected or joined.

The housing cover 28 forms an inner peripheral surface, which is a bearing seat for the rolling bearing 4th , in particular forms its outer ring. The recording room 12 is by means of a shaft seal 28a that on the first housing cover 28 is arranged and with the rotor 22 forms a sealing gap, in Regarding the first rolling bearing 4th sealed. Furthermore, the first housing cover 28 another sealing element 28b on which also with the rotor 22 , especially with the through the passage of the housing 28 extending portion of the rotor 22 forms a sealing gap and the first rolling bearing 4th to the overload clutch 30th seals off. The first rolling bearing 4th can thus be lubricated, for example by means of grease or oil lubrication, whereby through the seals 28a , 28b prevents lubricant from the first rolling bearing 4th in the recording room 12 and to the overload clutch 30th can exit.

The second housing cover 7 also has a passage through which a portion of the rotor extends 22 extends. The section of the rotor extending through the passage 22 forms an outer peripheral surface, which has a bearing seat for the second rolling bearing 5 , especially its inner ring. An inner peripheral surface of the second housing cover 7 forms a bearing seat for the rolling bearing 5 , especially its outer ring. Between which is in the passage of the second housing cover 7 extending portion of the rotor 22 and an inner peripheral surface of the passage of the second housing cover 7 a gap, in particular an annular gap is formed, which is the second rolling bearing 5 liquid-communicating with that of the gearbox 81 edged recording room 11 in which the at least one planetary stage 50 , 60 , 70 is arranged, connects. This enables the lubricant, for example from the splash lubrication of the transmission 80 the second rolling bearing 5 can wet so that the rolling bearing 5 lubricated and also heat from the rolling bearing 5 can be dissipated.

The second housing cover 7 has an inner peripheral surface on which a seal is seated, which with an outer peripheral surface of the rotor 22 , in particular with an outer circumferential surface, which is in the passage of the second housing cover 7 extending portion of the rotor 22 is formed, forms a sealing gap. The seal 6 seals the second rolling bearing 5 to the recording run 12 liquid-tight. The level of the lubricant in the receiving space 11 is chosen so that the second rolling bearing 5 of the lubricant that is in the receiving space 11 is contained, is wetted.

The housing cover 7 limits or closes that to the electric motor 20th pointing end of the gearbox 80 . Furthermore, the second housing cover limits or closes 7 the gearbox 80 open electric motor 20th . The housing cover 7 forms a housing cover for both the motor housing 25th as well as for the gearbox 81 .

The gearbox 81 has a first gear housing part 82 and a second gear housing part arranged concentrically thereto 83 on which the first gear housing part 82 surrounds the circumference. The transmission case parts 82 , 83 extend concentrically around the axis of rotation D . Between the first gear housing part 82 and the second gear housing part 83 is at least partially around the axis of rotation D extending coolant channel formed. The second gear housing part has a coolant supply connection 90 and a coolant discharge port 91 on. The coolant supply connection 90 is via in or from the first gear housing part 82 formed coolant channel 92 with the coolant discharge connection 91 liquid communicating connected. About that from the coolant supply port 90 via the coolant channel 92 to the coolant discharge connection 91 flowing coolant will heat from the transmission 80 and / or the electric motor 20th dissipated. The coolant channel 92 points groove-shaped to the electric motor 20th open recesses on the to the electric motor 20th pointing end of the first gear housing part 82 on. The groove-shaped coolant channel sections of the coolant channel and / or the gap or gaps between the first gear housing part 82 and the second gear housing part 83 are to the electric motor 20th towards the second housing cover 7 covered. The second housing cover 7 thus forms a wall of the coolant channel 92 . As a result, the coolant flowing through the coolant channel 92 flows, especially heat from the second housing cover 7 and therefore from the electric motor 20th dissipated.

Between the first housing part 82 and the second housing cover 7 is a ring around the axis of rotation D extending seal 82a arranged, which causes the coolant to be fluidly separated from the lubricant in the receiving space 11 remains. Between the second gear housing part 83 and the second housing cover 7 is a ring over the axis of rotation D extending seal 83a arranged, and between the second gear housing part 83 and the first gear housing part 82 is a ring around the axis of rotation D extending seal 83b appropriate. The seals 83a and 83b prevent coolant from escaping to the environment.

The rotor 22 , in particular the section on which the second roller bearing 5 is located, has an inner circumferential surface which coincides with the outer circumferential surface of the drive shaft 1 forms a gap. The gap is to prevent lubricant from escaping from the receiving space 11 by means of a ring around the axis of rotation D extending seal 1a sealed.

The overload clutch 30th has a clutch output member 33 on, which with a shaft-hub connection rotatably with the drive shaft 1 connected is. The overload clutch 30th connects the rotor 22 torsion-proof with the drive shaft 1 as long as the transmitted torque does not exceed a limit torque. If the limit torque is exceeded, the overload clutch disengages 30th the rotor 22 from the drive shaft 1 by the clutch input link 32 and the clutch output member 33 relative to each other about the axis of rotation D are rotatable.

The overload clutch 30th is on the first face of the electric motor 20th arranged that the second side on which the transmission 80 is arranged, is opposite. The electric motor 20th is, regarding the geometry, between the gearbox 80 and the overload clutch 30th arranged. There is also a brake 40 , in particular holding brake, provided between the and the electric motor 20th the overload clutch 30th is arranged or bordered. The brake 40 that forms the output link 2nd opposite end of the motor-gearbox unit. In that the brake 40 - unlike conventional motor-gearbox units - the brake is not enclosed between the electric motor and the gearbox 40 easier to access, for example for service work. In addition, the lubrication and cooling of the second roller bearing can be done 5 this way simply with the one in the recording room 11 contained lubricant of the transmission 80 realize.

The brake 40 is in the in 1 shown example a multi-disc brake, which is designed as a holding brake. Alternatively, however, other brakes can also be provided, for example a disc brake.

The brake 40 has a second plate carrier 45 on, by means of a shaft-hub connection, here a wedge connection, on the drive shaft 1 around the axis of rotation D sits twist-proof. The brake 40 has several first slats 41 (first brake body) on which around the axis of rotation D torsion-proof with the brake housing 43 or a first plate carrier 44 , the torsion-proof with the brake housing 43 connected, connected. The brake 40 has several second slats 42 (second brake body) on the axis of rotation D non-rotatable with the second disc carrier 45 are connected. Between two first slats 41 is a second slat 42 arranged, being between two second slats 42 a first slat each 41 is arranged. In other words, along the axis of rotation D alternating first and second slats 41 , 42 arranged. The first and second slats 41 , 42 can over a pressure piece 46 the brake 40 be pressed against each other, creating friction between the fins 41 , 42 and thus as the braking torque or the holding torque of the brake 40 can be generated or increased. The pressure piece 46 is, for example, by means of one or more prestressed springs 47 against the slats 41 , 42 pressed. The at least one feather 47 is supported on a cover of the brake housing 43 on the one hand and on the pressure piece 46 on the other hand. The at least one spring thus generates the pressing force required for the braking or holding torque on the plates 41 , 42 . The at least one feather 47 is a helical spring that acts as a compression spring. The pressure piece 46 forms the wall of a pressure chamber (not shown) which can be printed with a fluid, in particular pressure fluid or hydraulic oil, via a channel. The brake housing 43 , in particular its cover, has on its outside a connection for connecting a supply line for the pressure chamber. By supplying fluid into the chamber, the pressure piece can 46 so that on the one hand the at least one spring 47 excited and the slats 41 , 42 on the contact pressure of the pressure piece 46 are relieved, reducing the braking torque of the brake 40 decreases. The at least one spring can be removed by discharging fluid from the pressure chamber, in particular by relieving the pressure in the pressure chamber 47 the pressure piece 46 by increasing the contact pressure on the slats 41 , 42 press, causing the braking or holding torque of the brake 40 increases. By moving the pressure piece accordingly 46 or by pressurizing the pressure chamber with fluid, the braking torque of the brake 40 can be set almost arbitrarily, ie continuously. A stepless adjustment of the braking torque is advantageous if the brake is to be used as a service brake. If the brake 40 to be used as a holding brake, a continuous adjustment of the pressure piece is not absolutely necessary, since the holding brake preferably only needs to be switchable between an open and a closed state. In the open state, the brake is fully open, while in the closed state, the brake is fully closed, ie the pressure chamber is relieved of pressure. Preferably the brake 40 designed as a holding brake.

The braking torque is via the brake housing 44 or generally via the housing 10th the motor-gear unit in particular in the machine frame 100 derived. The drive shaft 1 protrudes from a first end face of the engine 20th from and is with the protruding portion torsionally with the clutch output member 33 and the second disk carrier 45 connected. The drive shaft 1 protrudes from the front of the electric motor on the second side 20th and with the protruding section is twist-proof with a sun gear 51 the first planetary stage 50 connected. The rotation of the drive shaft 1 causes the sun gear to rotate 51 around the axis of rotation D . The first planetary stage 50 , the second Planetary stage 60 and the third planetary stage 70 each have a sun gear 51 , 61 , 71 which around the axis of rotation D are rotatable, each a ring gear 53 , 63 , 73 which around the axis of rotation D torsion-proof on the gear housing 81 are attached, and each have several planet gears 52 , 62 , 72 , on. The planet gears 52 the first planetary stage 50 comb with the ring gear 53 and the sun gear 51 the first planetary stage 50 and are rotatable on a journal of a planet carrier 54 the first planetary stage 50 arranged. The planet gears 62 the second planetary stage 60 comb with the ring gear 63 and the sun gear 61 the second planetary stage 60 and are rotatable on a journal of a planet carrier 64 the second planetary stage 60 arranged. The planet gears 72 the third planetary stage 70 comb with the sun gear 71 and the ring gear 73 the third planetary stage 70 and are rotatable on a journal of a planet carrier 74 the third planetary stage 70 arranged. The planet carrier 54 is twist-proof with the sun gear 61 connected. The planet carrier 64 is twist-proof with the sun gear 71 connected. The planet carrier 54 is non-rotatable with the output member 2nd connected or forms - as shown in this example - the output link 2nd . The planet carriers 54 , 64 , 74 are about the axis of rotation D rotatable.

If by rotating the rotor 22 the drive shaft 1 and thus also the sun gear 51 around the axis of rotation D are rotated, the sun gear rolls 51 on the planet wheels 52 off, causing the planet gear 52 on the ring gear 53 passes on. The planet carrier 54 taken and about rotation about the axis of rotation D transferred. This rotation is on the sun gear 61 transfer. The sun gear 61 rolls on the planet wheels 62 off, which in turn on the ring gear 63 roll off and thereby the planet carrier 64 and the sun gear 71 in rotation around the axis of rotation D offset. The sun gear 71 rolls on the planet wheels 72 starting on the ring gear 73 pass on. The planet carrier 74 taken and together with the output member 2nd in rotation around the axis of rotation D transferred.

For example, an external cooling device can be provided, which has a first line pair with the coolant supply connection 29a and the coolant discharge connection 29b connected is. Furthermore, a second pair of lines can be provided, for example, which connects the coolant supply connection 90 and the coolant discharge connection 91 connects with the or another cooling device. The cooling circuits of the motor-gear unit can thus be operated in parallel.

Alternatively, a pair of lines can connect the external cooling device to the coolant supply connection 29a and the coolant discharge connection 91 connect, with another line connecting the coolant discharge 29b with the coolant supply connection 90 connects. Alternatively, a line pair can be provided which connects the external cooling device with the coolant supply connection 90 and the coolant discharge connection 29b connects, wherein a further line is provided which the coolant discharge connection 91 with the coolant supply connection 29a connects. The two last-mentioned alternatives allow the coolant channels of the engine-transmission unit to be operated in series, ie in series.

Reference symbol list

1

drive shaft

1a

poetry

2nd

Output link

3rd

4th

first rolling bearing

5

second rolling bearing

6

Seal, shaft seal

7

second housing cover

10th

casing

11

Gearbox receiving space

12

Recording room of the electric motor

13

20th

Electric motor

21st

stator

22

rotor

25th

Engine housing

26

second peripheral wall

27th

first peripheral wall

28

first housing cover

28a

poetry

28b

poetry

29a

Coolant supply connection

29b

Coolant discharge connection

29c

Coolant channel

30th

Overload protection, overload clutch, safety clutch

31

Clutch housing

32

Coupling input link

33

Coupling output link

40

Brake, holding brake

41

first brake body, plates

42

second brake body, plates

43

Brake housing

44

first slat carrier

45

second disk carrier

46

Pressure piece

47

feather

50

first planetary stage

51

Sun gear

52

Planet gear

53

Ring gear

54

Planet carrier

60

second planetary stage

61

Sun gear

62

Planet gear

63

Ring gear

64

Planet carrier

70

third planetary stage

71

Sun gear

72

Planet gear

73

Ring gear

74

Planet carrier

80

transmission

81

Gear housing

82

first gear housing part

83

second gear housing part

82a

poetry

83a

poetry

83b

poetry

90

Coolant supply connection

91

Coolant discharge connection

92

Coolant channel / groove

100

Machine frame

110

Sprocket

120

pinion

D

Axis of rotation

Claims (15)

Motor-gear unit, in particular for a tunnel boring machine or for driving a ring gear, comprising: - a housing (10), - an electric motor (20), in particular a synchronous motor, which has a rotor (22) which can be rotated relative to the housing (10), a drive shaft (1) which is coupled to the rotor (22) such that rotation of the rotor (22) causes rotation of the drive shaft (1) relative to the housing (10), a gear (80) with at least one planetary stage (50, 60, 70) and an output member (2), the at least one planetary stage (50, 60, 70) coupling the drive shaft (1) to the output member (2) in such a way, that a rotation of the drive shaft (1), in particular while reducing the speed, is transmitted to the output member (2). Motor-gear unit according to the preceding claim, characterized in that the rotor (22) is coupled to the drive shaft (1) or the output member (2) via an overload safety device (30), in particular an overload clutch, the electric motor (20) For example, between the overload protection (30) and the at least one planetary stage (50, 60, 70) is arranged. Motor-gear unit according to the preceding claim, characterized in that the drive shaft (1) extends through the rotor (22) and part of the overload protection (30) which is located on a first side of the electric motor (20), with a part of the at least one planetary stage (50, 60, 70), which is located on a second side of the electric motor (20), non-rotatably connects. Motor-transmission unit according to one of the two preceding claims, characterized by a brake (40), in particular a holding brake, the overload safety device (30), in particular an overload clutch, being arranged between the brake (40) and the electric motor (20). Motor-transmission unit according to one of the preceding claims, characterized by a brake (40), in particular holding brake, the electric motor (20) between the brake (40), which is located on a first side of the electric motor (20), and the at least one planetary stage (50, 60, 70), which is located on a second side of the electric motor (20). Motor-transmission unit according to one of the two preceding claims, characterized in that the brake (40) has at least one first brake body (41) and at least one second brake body (42) which is connected to the drive shaft (1) about the axis of rotation (D) is non-rotatably connected or connectable, the at least one first brake body (41) and the at least one second brake body (42) being able to be pressed against one another in order to achieve a braking action based on frictional engagement. Motor-gear unit according to one of the preceding claims, characterized by a first roller bearing (4) and a second roller bearing (5), by means of which the rotor is supported on the housing (10) such that it can rotate about the axis of rotation (D). Motor-gear unit according to the preceding claim, characterized in that the at least one planetary stage (50, 60, 70) is arranged in a receiving space (11) formed by the housing (10), in particular a gear housing (81), wherein the receiving space (11) is connected in a liquid-communicating manner to at least one of the first and second roller bearings (4, 5). Motor-gear unit according to the preceding claim, characterized in that the receiving space (11), in which the at least one planetary stage (50, 60, 70) is arranged, and one of the housing (10), in particular a motor housing (25 ), the receiving space (12) formed, in which the rotor (22) is arranged, are sealed off from one another, a seal (6) in particular being provided which comprises at least one of the first and second rolling bearings (4, 5) to the receiving space (12 ) of the motor (20) seals. Motor-gear unit according to one of the preceding claims, characterized by one between a gear housing (81) in which the at least one planetary stage (50, 60, 70) is arranged and a motor housing (25) in which the rotor (22 ) is arranged, arranged housing cover (7), which has both a cover for the front end of the gear housing (81) facing the electric motor (20) and a cover for the front end of the motor housing (25) facing the gear (80) forms. Motor-gear unit according to the preceding claim, characterized in that the housing cover (7) has an inner peripheral surface which forms a bearing seat for a roller bearing (5), the rotor (22) having an outer peripheral surface which has a bearing seat for the roller bearing (5) forms, whereby the rotor (22) is rotatably supported on the housing cover (7) about the axis of rotation (D). Motor-gear unit according to the preceding claim, characterized in that the housing cover (7) has an inner peripheral surface on which sits a seal (6) which forms a sealing gap with an outer peripheral surface of the rotor (22), the seal (6 ) seals the roller bearing (5) to the receiving space (12), in which the rotor (22) is located, in a liquid-tight manner. Motor-gear unit according to one of the preceding claims, characterized in that the at least one planetary stage (50, 60, 70) is arranged in a receiving space (11) formed by a gear housing (81), the gear housing (81) on it The end facing the electric motor (20) has one or more grooves (92) which connect or connect a coolant supply connection (90) in a liquid-communicating manner to a coolant discharge connection (91), the groove (92) or the grooves coming from an end housing cover (7) Electric motor (20) are closed, it being preferred that the fluid path leading from the coolant supply connection (90) to the coolant discharge connection (91) from the receiving space (11), in which the at least one planetary stage (50, 60, 70) is arranged , fluidically separated or sealed from the receiving space (11). Sprocket drive, in particular for a tunnel boring machine, comprising a sprocket (110) rotatably mounted about a sprocket axis of rotation (Z), one or more motor-gear units according to the preceding claims, each motor-gear unit one pinion (120), which with the The toothing of the toothed ring (110) meshes and is coupled to the driven member (2), so that rotation of the driven member (2) causes the toothed ring (110) to rotate. A tunnel boring machine comprising a ring gear drive according to the preceding claim and a drill head at the end pointing in the direction of advance of the tunnel boring machine, wherein the boring head, which is rotated about an axis of rotation of the drill head in order to remove the material to be removed from the tunnel boring machine, and the ring gear (110) are coupled such that rotation of the ring gear (110) causes rotation of the drill head.

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