GEARBOX WITH AN OIL GUIDE CHANNEL PART

Description

State of the art

[0001] In the current state of the art, transmissions for motor vehicles are often used in combination with an electric motor drive. As with conventional transmissions, the transmission elements must be lubricated with oil. To increase transmission efficiency and reduce costs, an oil pump for transmission lubrication, which is often used in conventional transmissions, can be dispensed with. The lubrication and cooling of the transmission elements is preferably achieved through passive oil distribution. The lubrication of the rotating transmission elements is important for the reliability of the transmission. Insufficient lubrication can result in an insufficient supply of oil to the bearings of the transmission elements and the sealing rings. This can lead to increased wear and even failure of the transmission elements.

[0002] DE 10 2017 108 748 B3 discloses a transmission for a motor vehicle, which has a transmission housing and at least one transmission gear arranged in the transmission housing, wherein the transmission gear is at least partially arranged in an oil sump of the transmission. A section of the rotating transmission gear rolls through the oil sump and absorbs oil in the process. This process is often described in technical terms as splashing. In order to distribute oil absorbed by the transmission gear more precisely within the transmission, an oil guide channel part is provided, which is inserted into the transmission as an insert. The oil guide channel part is designed like a pair of glasses and has a plurality of apertures and a guide channel with a receiving opening and an outlet opening, wherein the guide channel has an oil guide direction from the receiving opening to the outlet opening and a channel wall that is closed all the way around and perpendicular to the oil guide direction.In DE 10 2017 108 748 B3, the channel wall is formed by a semi-circular hollow body curved around a gear axis of a transmission gear of the transmission, which, in a predetermined installed state of the oil guide channel part, is located predominantly above an oil sump level of the transmission. The curved guide channel has a receiving opening designed as a collecting mouth for receiving oil thrown up by another transmission gear, which meshes with the transmission gear surrounded by the semi-circular hollow body, and transported further by the second transmission gear to the collecting mouth. An end section of the semi-circular hollow body facing away from the collecting mouth and closed except for a throttle bore forms an oil collection area for collecting oil conveyed through the guide channel in DE 10 2017 108 748 B3.The throttle bore forms the only outlet opening of the guide channel and therefore simultaneously represents an outlet for the oil from the at least one oil collection area. The throttle bore is located vertically above the tooth engagement area of ​​the two transmission gears, so that the outflowing oil flow flows into their tooth engagement area and wets the contact surfaces of the teeth.

[0003] From EP 2 700 849 A1 a transmission with an oil guide channel part with a guide channel is known, wherein the guide channel has an oil guide direction from a receiving opening on an end face of a transmission gear to an outlet opening and has a channel wall that is closed all the way perpendicular to the oil guide direction, wherein the oil guide channel part further has at least one oil collection area for collecting oil guided through the guide channel, wherein the oil guide channel part has at least one outlet for oil from the at least one oil collection area, wherein oil thrown up from the oil sump by a transmission gear reaches the receiving opening and along the oil guide direction of the guide channel to the outlet opening.The oil collection area is formed by a collection basin with a basin bottom, wherein the oil guide channel part is arranged in the transmission housing such that the basin bottom is positioned above the transmission gear and the oil guide direction runs from the receiving opening to the outlet opening against the force of gravity.

[0004] Other transmissions with an oil guide channel part are known from JP 2005 083491 A and from DE 1 291 966 B. Disclosure of the invention

[0005] The invention relates to a transmission, in particular a motor vehicle transmission, with a transmission housing and at least one transmission gear arranged in the transmission housing, wherein the transmission gear is arranged at least partially in an oil sump of the transmission, wherein the transmission has an oil guide channel part, wherein the oil guide channel part has a guide channel with a receiving opening and with an outlet opening, wherein the guide channel has an oil guide direction from the receiving opening to the outlet opening and a channel wall that is closed all the way around and perpendicular to the oil guide direction, wherein the oil guide channel part further has at least one oil collection area for collecting oil guided through the guide channel, wherein the oil guide channel part has at least one outlet for oil from the at least one oil collection area, wherein the oil guide channel part is arranged in the transmission housing in such a way,that during operation, oil thrown up from the oil sump by the transmission gear reaches the receiving opening and along the oil conduction direction of the guide channel to the outlet opening, wherein the at least one oil collection area comprises a first collecting basin, wherein the first collecting basin has a first basin wall and a first basin bottom, wherein the oil guide channel part, in a predetermined installed state, which defines an orientation of the oil guide channel part in the transmission housing relative to gravity, is arranged in the transmission housing such that the receiving opening is positioned on the end face of the transmission gear arranged at least partially in the oil sump and the first basin bottom is positioned above the transmission gear, and the oil conduction direction runs from the receiving opening to the outlet opening against gravity. According to the invention, the transmission has a drive shaft and an output shaft,wherein the output shaft is drivable by means of the transmission gear, wherein a coupling element is coupled to the transmission gear such that the transmission gear can be driven by means of the coupling element, wherein a clutch device with a clutch element is provided in the transmission, wherein the clutch element is coupled in a rotationally fixed manner to the drive shaft, wherein the clutch element can be coupled in a rotationally fixed manner to and uncoupled from the coupling element by means of the clutch device, and wherein the oil guide channel part has a first outlet which projects above the first basin bottom from the first basin wall and has a drain opening through which draining oil is guided to a bearing of a pinion which is rotatably mounted on the drive shaft and is rotationally fixedly coupled to the coupling element.

[0006] In the context of this application, "oil" refers to a liquid lubricant suitable for transmissions, regardless of whether it is marketed as oil. In particular, it can be a lubricant known as ATF (Automatic Transmission Fluid) or similar substances.

[0007] A predetermined installation state, which defines an orientation of the oil guide channel part in the transmission housing relative to gravity, is understood to be an installation state which represents a specific orientation of the oil guide channel part relative to the transmission housing when the orientation of the associated transmission relative to the Earth's gravity field is known. The orientation of the transmission relative to the Earth's gravity field is generally known for a normal position of the transmission, whereby the normal position is the position in which the transmission is aligned relative to gravity in its intended use. If the transmission is a motor vehicle transmission, the transmission assumes a specific orientation relative to the Earth's gravity field when the motor vehicle is aligned horizontally relative to the Earth's gravity field in the normal position. This applies regardless of whether the motor vehicle is actually moved horizontally to the Earth's gravity field or is driving up an incline with an angle of inclination.From a previously known installation position of the transmission in the vehicle, it is therefore possible to deduce in principle how an oil guide channel component should be installed in the transmission so that the oil guide channel component assumes a specific orientation relative to gravity in the normal position. Since, in most possible driving conditions of the vehicle, the inclination angle deviates only very moderately by + / - 20° from the horizontal when driving downhill or uphill, the geometric design of the oil guide channel component is adapted to a horizontal vehicle position.

[0008] An oil guide channel part is understood to be a component that has at least one guide channel for oil transport. The oil guide channel part can also be designed to distribute oil supplied to the oil guide channel part within the oil guide channel part under the influence of gravity. The oil guide channel part can, in particular, be designed as an insert that is inserted into the transmission during assembly. However, it is also possible to form the oil guide channel part using inwardly projecting structures on the housing part of the transmission housing. Preferably, however, the oil guide channel part is a separately manufactured insert. This can be made of plastic or metal, or a plastic-metal composite. The oil guide channel part can be constructed in one or more parts.In particular, it is possible to assemble the oil guide channel part from two or more shell parts which are mechanically connected to one another via snap connections or clip connections.

[0009] In the context of the present application, relative to an assumed reference point, the terms "bottom" or "below" denote a position at a point located lower in the direction of gravity, and the terms "top" or "above" denote a position at a point located higher in the direction of gravity, wherein an orientation of the oil guide channel part is assumed which corresponds to the predetermined installation state.

[0010] A transmission oil sump is an area within the transmission housing where oil accumulates under the influence of gravity. A transmission gear that is at least partially arranged in a transmission oil sump is defined as a transmission gear with a lower part immersed in the oil sump, in the direction of gravity, while an upper part of the transmission gear protrudes from the oil sump. As the transmission gear rotates, it absorbs oil from the oil sump and transports it against the force of gravity to a release point or knock-off point. This process is called "splashing." The circulation and delivery rate of the oil through the transmission gear depend directly on the speed and, via the viscosity, also on the temperature. The amount of oil transported from the oil sump by at least one transmission gear causes the level of the oil sump to drop during operation.The at least one transmission gear can therefore be considered an oil-feeding transmission gear. Oil splashed by the at least one transmission gear and possibly other transmission gears during rapid rotation in the transmission housing can reach locations from which there is no rapid return to the oil sump. These oil quantities are called splash losses. To ensure that sufficient oil is nevertheless delivered by the at least one transmission gear and that the transmission does not run dry, the oil sump must contain an appropriate amount of oil. On the other hand, an excessive amount of oil in the oil sump is undesirable, as this increases the detrimental drag losses of the transmission.As a compromise, it is therefore desirable to supply the amount of oil transported by the transmission gear as precisely as possible to the lubrication points in the transmission in order to avoid splashing losses and to be able to reduce the level in the oil sump to a level at which drag losses of the transmission are as low as possible.

[0011] A rotationally fixed coupling or connection between two parts means that a first part cannot rotate relative to a second part. This does not preclude the first part from being axially displaceable relative to the second part.

[0012] The at least one transmission gear can be any gear in a set of gears. In particular, the transmission gear can mesh with another transmission gear and serve within the transmission to transmit torque from a drive shaft to an output shaft. This does not preclude the possibility of multiple oil-feeding transmission gears being present in the transmission. Advantages of the invention

[0013] The transmission according to the invention with the oil guide channel part enables a more targeted oil supply to bearings of rotating transmission elements within the transmission housing. This is achieved by forming a first collecting basin on the oil guide channel part, which has a first basin wall and a first basin bottom in combination with a specially designed guide channel. In a predetermined installed state, which defines an orientation of the oil guide channel part in the transmission housing relative to gravity, the oil guide channel part is arranged in the transmission housing such that the receiving opening is positioned on the end face of the transmission gear and the first basin bottom is positioned above the transmission gear, and the oil flow direction runs from the receiving opening to the outlet opening against gravity.The oil guide channel part is advantageously used in a transmission having a drive shaft and an output shaft, the output shaft being drivable by means of the transmission gear, a coupling element being coupled to the transmission gear in such a way that the transmission gear can be driven by means of the coupling element, a clutch device having a clutch element being provided in the transmission, the clutch element being coupled in a rotationally fixed manner to the drive shaft, the clutch element being able to be coupled in a rotationally fixed manner to and uncoupled from the coupling element by means of the clutch device, and the oil guide channel part having a first outlet which projects from the first basin wall above the first basin bottom and having an outlet opening through which draining oil is guided to a bearing of a pinion which is rotatably mounted on the drive shaft and is connected in a rotationally fixed manner to the coupling element.In such a transmission, the drive shaft, which is driven directly or indirectly by an electric motor, for example, can be decoupled from the output shaft of the transmission. The output shaft can be coupled to the wheels of a motor vehicle, for example. If the electric motor is deactivated, the output shaft can be decoupled from the drive shaft by means of the clutch device. When the motor vehicle is in motion, the at least one transmission gear and the pinion meshing therewith continue to be driven via the wheels of the motor vehicle, but not the drive shaft. By means of the oil guide channel part, the bearing of the rotating pinion located on the drive shaft can now advantageously be supplied with oil even in a decoupling stage of the clutch device, without rotation of the drive shaft being necessary for this purpose.

[0014] In contrast to the solutions known from the prior art, in which the oil collection area forms the end region of a semi-circular hollow body curved around a gear axis, in the present invention the oil collection area comprises a first collection basin arranged above the oil-delivering transmission gear. The supply of oil contained in the first collection basin causes the oil sump at the bottom of the transmission housing to sink during operation. The guide channel is designed as a simple, circumferentially closed channel, which can extend, preferably in a straight line, from the receiving opening to an outlet opening. The opening cross-section of the receiving opening can correspond to the opening cross-section of the outlet opening.The gear oil, which is fed into the guide channel's receiving opening by the paddle movement of the rotating gear wheel, travels upwards through the guide channel without encountering any obstacles, against the force of gravity, until it exits the outlet opening and collects in the first reservoir. The guide channel, with its surrounding channel wall, represents a guide channel integrated into the oil guide channel section. Advantageously, oil is pumped through the guide channel even at low speeds.

[0015] The oil is not collected in the guide channel, but outside the guide channel in the first collection basin, so that sufficient lubrication of the gearbox bearings is possible even in the event of speed fluctuations, since the supply contained in the first collection basin can be used. At least one outlet, but preferably several outlets can be provided on the first collection basin in order to supply oil to different, lower-lying bearings in the gearbox. Advantageously, compared to the prior art, the amount of oil conveyed through the guide channel during operation can be made more independent of the amount of oil draining from the oil collection area via a drain. The guide channel serves only to fill the first collection basin, while the outflow of oil from the first collection basin can be adjusted via the geometric design of the collection basin and the geometric design of the at least one outlet.The oil supply to the bearing points of the transmission elements can therefore be advantageously optimized both locally and over time. This improves the lubrication of the bearing points, particularly in transmissions where rotating transmission elements are arranged in several planes, one above the other, relative to gravity.

[0016] Since the first reservoir is advantageously used as an intermediate storage tank, faster lubrication is available when the electric motor driving the transmission is reactivated, even during short deactivation periods. However, during longer downtimes, the first reservoir can also drain completely toward the oil sump via a small drain opening in the first reservoir base.

[0017] Advantageous embodiments and further developments of the invention are made possible by the features specified in the dependent claims.

[0018] Advantageously, an end of the guide channel wall facing away from the receiving opening can form a circumferential wall that protrudes beyond the first basin floor of the first collection basin and delimits the outlet opening, such that oil escaping from the outlet opening of the guide channel collects in the first collection basin, flowing in the direction of gravity. Oil flowing over the circumferential wall can thus advantageously flow directly into the first collection basin and fill it.

[0019] Advantageously, the guide channel can be linear and, at least in the area of ​​the gear wheel, run tangentially to one end face of the gear wheel, with the receiving opening positioned in close proximity to the end face of the gear wheel. In this context, "in close proximity to the end face of the gear wheel" means that the receiving opening is positioned so close to the gear wheel that the gear oil can be fed directly from the end face to the receiving opening.

[0020] The receiving opening can be designed as a catch mouth, with the circumferential edge of the receiving opening being chamfered to match the tangential angle of the guide channel, so that the receiving opening is as close as possible to the face of the gear. The contour of the circumferential edge can be adapted to the radius of curvature of the face of the gear. The oil pumped by the gear, some of which is thrown away under the influence of centrifugal force, enters the guide channel at the location of the receiving opening. The momentum of the oil separating from the gear largely corresponds to the oil flow direction of the guide channel, so that the oil preferably reaches the outlet of the guide channel without any obstacles. The oil escaping from the outlet of the guide channel flows in the direction of gravity and collects in the first collecting basin, which is thereby filled.The oil flowing from the reservoir reaches the designated lubrication points of the gearbox in a somewhat "passive" manner (namely under the influence of gravity).

[0021] In one embodiment, the drive shaft is designed as a hollow shaft with an axial bore. When the pinion meshes with the transmission gear, oil draining from the drain opening of the first drain can be fed to the axial bore of the drive shaft and from there, for example, via at least one radial bore, to the pinion bearing. The pinion bearing can, for example, be designed as a pinion bearing, whose oil lubrication must be reliably ensured.

[0022] In this context, it is advantageous if the oil draining from the drain opening of the first drain under the influence of gravity reaches a chamber formed on a first housing part of the gearbox housing, in which chamber a baffle plate is arranged, wherein a channel section is formed centrally on the baffle plate, wherein the channel section engages in the axial bore of the drive shaft, wherein oil contained in the chamber drains via the baffle plate into the channel section and thus reaches the axial bore of the drive shaft. The oil supplied to the chamber wets the baffle plate and runs along the baffle plate into the channel section. Since this engages in the axial bore of the drive shaft, the baffle plate advantageously ensures a permanent supply of oil to the axial bore even when the drive shaft is stationary or slowly rotating, so that the pinion bearing of the pinion rotating on the drive shaft can be easily lubricated.

[0023] In one embodiment, a rotor shaft of an electric machine can be provided which is mounted in at least one bearing in the transmission housing, wherein the drive shaft can be driven by means of the rotor shaft. For example, in this case it is advantageous if the oil collection region of the oil guide channel part comprises a second collection basin, wherein the second collection basin has a second basin wall and a second basin bottom, wherein the second collection basin is connected to the first collection basin via a connecting channel, wherein a second drain protrudes in the predetermined installation direction above the second basin bottom from the second basin wall of the second collection basin and has a drain opening through which oil is guided in the direction of the bearing of the rotor shaft.Due to the geometric design and position of the second collecting basin and the second drain, the oil supply for the rotor shaft bearing can be designed independently of the oil supply to the pinion bearing.

[0024] Of course, additional collecting basins can also be provided on the oil guide channel part and / or additional drains on the first or second collecting basin, with which additional bearings of rotating gear elements are lubricated with oil.

[0025] Advantageously, the edge of the circumferential wall on a side facing the first collection basin can be spaced from the first basin floor at a distance that is less than the distance between the edge of the circumferential wall and the second basin floor on a side facing the second collection basin. When the gearwheel rotates and oil is conveyed through the guide channel, oil first enters the first collection basin and at least partially fills it before the oil flows into the second collection basin via the connecting channel. This prevents the oil from draining too quickly toward the second drain and ensures that the first drain is always supplied with oil.In a certain respect, therefore, in this exemplary embodiment, the oil drains via the first drain and the second drain in a cascade-like manner, with the first collecting basin being filled first until oil drains out of the oil guide channel part via the first drain and at the same time, shortly before or shortly after, the supplied oil begins to fill the second collecting basin via the connecting channel, so that in this example oil only drains via the second drain after it has already drained via the first drain.

[0026] Furthermore, the transmission housing can advantageously have a first housing part with a first housing wall region and a second housing part placed on the first housing part with a second housing wall region, wherein a third housing wall region is arranged in the contact region of the first housing part and the second housing part, wherein the first housing wall region, the second housing wall region and the third housing wall region enclose an end of the transmission gear facing away from the oil guide channel part in the oil sump on three sides. Without further aperture elements or additional measures, this advantageously forms a region which is always filled with oil from the oil sump and in which the at least one transmission gear rotates. The distances between the housing wall regions and the transmission gear are dimensioned with a gap that enables reliable wetting and oil delivery through the transmission gear.The first housing wall area, the second housing wall area, the third housing wall area, the gear wheel and the guide channel form a pump system through which, when the gear wheel rotates, oil is transported from the oil sump through the guide channel against gravity to the outlet opening of the guide channel.

[0027] The transmission gear can be rotationally coupled to a differential of the transmission, with a first output shaft and a second output shaft being coupled to the differential, with the first output shaft and the second output shaft being rotationally driven by the differential. The transmission gear can, for example, be fixed as a spur gear to a differential cage of the differential. Since the differential can be installed in the transmission housing together with the other transmission elements, the housing parts surrounding the differential can advantageously be used very easily to flank the end of the transmission gear facing away from the oil guide channel part in order to achieve the above-described effect of a pump system. Short description of the drawings

[0028] Possible embodiments of the invention are explained below with reference to the accompanying drawings. The drawings show: Fig. 1 shows a cross section through a transmission of a motor vehicle which is driven by an electric machine, Fig. 2 shows a perspective view of an embodiment of an oil guide channel part for use in a transmission, as shown in Fig. 1 Fig. 3 is a plan view of the oil guide channel part from Fig. 2 , Fig. 4 another perspective view of the oil guide channel part from Fig. 2 und Fig. 3 , Fig. 5 an enlarged detailed view of Fig. 6 for a transmission according to the invention with the oil guide channel part from the Figuren 1 bis 4 , Fig. 6 a cross section through a transmission according to the invention with the oil guide channel part from the Figuren 1 bis 4 , Fig. 7a side view of the gearbox from Fig. 6 with the oil guide channel part, Fig. 8a perspective top view of a gearbox with the oil guide channel part, Fig. 9a detail of the gearbox housing from Fig. 8 with a baffle plate, which can be used in conjunction with the oil guide channel part. Embodiments of the invention

[0029] Fig. 1 shows a drive device for a motor vehicle, which comprises a transmission 100. The transmission 100 is connected on the input side to an electric machine 110, which has a rotor shaft 103. The rotor shaft 103 meshes with a gear 104, which is coupled in a rotationally fixed manner to a drive shaft 101 of the transmission. The drive shaft 101 is supported over its outer circumference at two axially spaced bearing points 171 and 172 in a (in Fig. 1 not shown) gearbox housing is rotatably mounted.

[0030] The transmission 100 further comprises a clutch device 120, which can be controlled, for example, by means of a preferably electrically actuated rotary actuator 123. The electric actuator 123 can act, for example, via a spindle drive and a shift fork 129 on a clutch element 121 that is mounted axially displaceably on a guide hub 105. The clutch element 121 is, for example, annular and can rotate relative to the shift fork 129. The clutch element 121 can have internal teeth that engage with external teeth of the guide hub 105, so that the clutch element 121 is displaceable on the guide hub 105 parallel to the axis of the drive shaft 101. The guide hub 105 and the clutch element 121 engaging therewith are mounted on the drive shaft 101 in a rotationally fixed manner. Furthermore, a coupling element 122 is provided, which is non-rotatably coupled to a pinion 106.The pinion 106 is rotatably mounted on the drive shaft 101, for example, with a bearing 176 designed as a nail bearing. The coupling element 122 can have external teeth. Upon actuation of the rotary actuator 123, the spindle drive displaces the coupling element 121 in the axial direction via the shift fork until the internal teeth of the coupling element 121 engage with the external teeth of the coupling element 122, whereby the coupling element 121 is rotationally fixedly coupled to the coupling element 122. Due to the coupling, the gear 104, the drive shaft 101, the guide hub 105, the clutch element 121, the coupling element 122 and the pinion 106 rotate as a block around the axis of the drive shaft 101. During decoupling, the clutch element 121 is separated from the coupling element 122 by means of the rotary actuator 123. Fig. 1 to the left, thereby removing the coupling between the pinion 106 and the drive shaft 101. The pinion 106 can now rotate around the drive shaft 101.

[0031] The pinion 106 meshes with a transmission gear 107. In the illustrated embodiment, the transmission gear 107 is rotationally fixedly coupled to a differential 130. The differential 130 has an output shaft 102 in the form of a first output shaft 102a and a second output shaft 102b, which can be rotationally driven by the differential 130. The transmission gear 107 is fixedly connected to the differential cage 108 of the differential 130. As shown in Fig. 7 As shown, the differential 130 may be integrated into the transmission housing 140 of the transmission 100.

[0032] As already described, in the decoupled state, the coupling between the pinion 106 and the drive shaft 101 is canceled by means of the coupling device 120. If, for example, the electric motor is also switched off while a motor vehicle is in motion, the rotor shaft 103 and the drive shaft 101 are no longer driven. The wheels of the still-rolling motor vehicle now drive the transmission gear 107 via the output shaft 102, which meshes with the pinion 106, so that the pinion 106 rotates around the drive shaft 101. Even in this state, it must be ensured that, for example, the bearing 176 of the pinion 106, arranged above the oil sump of the transmission 100, is sufficiently supplied with oil.

[0033] Fig. 2, Fig. 3 and Fig. 4 show an embodiment of an oil guide channel part 1, which is shown for example in the Fig. 1 The oil guide channel part 1 can be installed in the illustrated transmission 100. The oil guide channel part 1 can, as shown here, be designed as an insert, which is inserted into the transmission 100 during assembly of the transmission 100. The oil guide channel part 1 can be made of plastic or metal or a plastic-metal composite and can be constructed in one piece or in multiple pieces. In particular, it is possible to assemble the oil guide channel part from two or more shell parts, which are mechanically connected to one another via snap-in connections or clip connections.

[0034] The oil guide channel part 1 has a guide channel 2 with a receiving opening 11 and with an outlet opening 12, wherein the guide channel 2 has an oil guide direction F (shown in Fig. 5 ) and a channel wall 21 which is closed all the way around and perpendicular to the oil guide direction F. The oil guide channel part 1 further has an oil collection area 13a for collecting oil conveyed through the guide channel 2 and an outlet 15a for oil from the oil collection area 13a.

[0035] The oil collection area 13a comprises a first collection basin 13. The first collection basin 13 has a first basin wall 25 and a first basin bottom 24. An end of the channel wall 21 facing away from the receiving opening 11 of the guide channel 2 forms a circumferential wall 21a projecting beyond the first basin bottom 24 of the first collection basin 13 and delimiting the outlet opening 12, as shown in Fig. 2, Fig. 3 and especially in Fig. 5 can be clearly seen. The oil guide channel part 1 further has a first drain 15, which projects above the first basin bottom 24 from the first basin wall 25 and has a drain opening 17. The first drain 15 is designed as an angled groove. In addition, a further drain 19 can be formed on the upper edge of the first basin wall 25, which acts as an overflow. The first collecting basin 13 can have a small drain opening 20 in the form of a bore in the first basin bottom 24, through which the first collecting basin 13 can be emptied during longer downtimes. The diameter of the drain opening 20 is designed to be so small that the amount of oil draining through the drain opening 20 during operation is significantly smaller than the amount of oil supplied to the guide channel 2.

[0036] As continued in Fig. 2, Fig. 3 and Fig. 4 As shown, the oil collection area 13a of the oil guide channel part 1 comprises a second collection basin 14, wherein the second collection basin 14 has a second basin wall 27 and a second basin bottom 26. As shown in Fig. 3 As can be seen, the second collecting basin 14 is connected via a connecting channel 29 ( Fig. 3 ) is connected to the first collection basin 13. A second drain 16 protrudes above the second basin bottom 26 from the second basin wall 27 of the second collection basin 14 and has a drain opening 18. The second drain 16 can also be channel-shaped. In addition, the second drain 16 can, for example, have a further drain opening 18a that is angled from the drain 16.

[0037] The edge of the circumferential wall 21a preferably has, on a side facing the first collecting basin 13, a distance from the first basin bottom 24 which is smaller than the distance of the edge of the circumferential wall 21a from the second basin bottom 26 on a side facing the second collecting basin 14.

[0038] The Figuren 2 bis 4 The oil guide channel part 1 shown is designed to be arranged in a predetermined installation state, which defines an orientation of the oil guide channel part relative to the force of gravity G, in the transmission housing 140 of the transmission 100. Without being limited thereto, the oil guide channel part 1 is preferably intended to be inserted into the Fig. 1 illustrated gearbox 100. For this purpose, the oil guide channel part 1 has retaining cams 23 projecting from the sides of the oil guide channel part 1, with which the oil guide channel part 1 can be installed and anchored in a gearbox housing 140 of a gearbox 100 in a predetermined orientation relative to the normal position of the gearbox 100. As shown in Fig. 2 As can also be seen, the oil guide channel part 1 can be provided with reinforcing ribs 22 to increase stability.

[0039] Fig. 6 and the enlarged detailed view of the Fig. 5 show a gearbox 100, the basic structure of which is similar to that shown in the Fig. 1 shown gearbox, with the oil guide channel part 1 installed therein from Fig. 2 bis 4 . It can be seen that the receiving opening 11 of the guide channel 2 is positioned on the front side of the gear wheel 107 and in the immediate vicinity of the front side of the gear wheel 107, while the first basin bottom 24 of the first collecting basin 13 is positioned above the gear wheel 107.

[0040] The oil guide direction F therefore runs from the receiving opening 11 to the outlet opening 12 against the force of gravity G, the orientation of which for the normal position of the gear 100 in Fig. 6 is shown.

[0041] As in the Figuren 5 and 6As shown, the guide channel 2 is preferably designed to be rectilinear and runs, at least in the region of the gear wheel 107, preferably tangentially to an end face of the gear wheel 107. The receiving opening 11 can be designed as a catch mouth, wherein the peripheral edge of the receiving opening 11 can be bevelled in accordance with the angle formed by the direction of gravity and the conveying direction F, so that the receiving opening 11 can be brought as close as possible to the end face of the gear wheel 107. The contour of the peripheral edge can be adapted, as shown, to the radius of curvature of the end face of the gear wheel 107.

[0042] The gear wheel 107 is partially arranged in an oil sump 150, as will be explained later with reference to the Fig. 7 The gear wheel 107 receives oil from the oil sump 150 and transports it into the receiving opening 11 of the guide channel 2. The movement impulse of the oil pushes it in the guide channel 2 in the oil conduction direction F to the outlet opening 12.

[0043] How best in Fig. 5 As can be seen, the oil emerging from the outlet opening 12 of the guide channel 2 runs over the circumferential wall 21a in the direction of gravity G and thus towards the first collecting basin 13, where it collects. Since the edge of the circumferential wall 21a on the side facing the first collecting basin 13 is at a distance from the first basin base 24 that is smaller than the distance between the edge of the circumferential wall 21a and the second basin base 26 on a side facing the second collecting basin 14, the oil first flows over the edge of the circumferential wall 21a on the side facing the first collecting basin 12, so that the latter is filled first. As soon as the oil reaches the connecting channel 29, the second collecting basin 14 also fills with oil via this.The oil level rising in the first collecting basin 13 and the second collecting basin 14 reaches the first outlet 15 and the second outlet 16 after a short time and flows out of the oil guide channel part 1 via the first outlet opening 17 and the second outlet opening 18 and third outlet opening 18a under the influence of gravity G.

[0044] Fig. 7 shows a side view of the gearbox 100 and the oil guide channel part 1 installed therein. The direction of the gravity force G is in the figure plane of the Fig. 7 directed vertically from top to bottom. It can be seen that the gear housing 140 has a first housing part 141 and a second housing part 142. However, further housing parts can also be provided. The first housing part 141 and the second housing part 142 can, for example, form housing half-shells which can be placed on top of one another and connected to one another. In the lower region of the gear housing 140, the first housing part 141 is provided with a first housing wall region 143 and the second housing part 142 is provided with a second housing wall region 144. The first housing wall region 143 and the second housing wall region 144 can be easily manufactured by appropriately shaping cast parts.

[0045] A third housing wall region 145 is located in the contact area of ​​the first housing part 141 and the second housing part 142. The third housing wall region 145 is formed by the inner side of the collar surfaces of a collar formed in the lower region of the transmission housing 140 on the first housing part 141 and the second housing part 142, respectively. The first housing wall region 143, the second housing wall region 144, and the third housing wall region 145 enclose the end of the transmission gear 107 facing away from the oil guide channel part 1 in the oil sump 150 on three sides. A narrow gap remains between the outer surfaces of the transmission gear 107 and the housing wall regions, which gap is always filled with transmission oil from the oil sump 150, the level of which is located directly above the housing wall regions.The first housing wall region 143, the second housing wall region 144, the third housing wall region 145, the transmission gear 107 and the guide channel 2 form a pump system through which oil is transported from the oil sump 150 into the guide channel 2 upon rotation of the transmission gear 107.

[0046] Fig. 8 illustrates how the oil flowing out of the oil guide channel part 1 via the first outlet 15 and the second outlet 18 can be guided to the bearings in the gearbox 100. In Fig. 8 a baffle plate 180 mounted on the drive shaft 101 can be seen. An enlarged, mirror-image representation of the baffle plate 180 can be found in Fig. 9 . As in Fig. 8 and Fig. 9 As can be seen, the oil flowing from the drain opening 17 of the first drain 15 can enter a chamber 146 formed on the first housing part 141 of the transmission housing 140, in which the baffle plate 180 is arranged. The baffle plate 180 is formed with a circular ring-shaped base body made of, for example, metal, which is mounted with its outer edge between the first housing part 141 and a bearing 172 of the drive shaft 101. As shown in Fig. 9 As can be seen, a cylindrical channel section 181 is formed in the center of the baffle plate 180, which engages in an axial bore 173 of the drive shaft 101, which is designed as a hollow shaft. The oil supplied via the outlet opening 17 of the chamber 146 flows through the baffle plate 180 into the channel section 181 and thus reaches the axial bore 173 of the drive shaft 101. From there, the oil reaches the bearing 176 of the pinion 106 via at least one radial bore 174 in the drive shaft.

[0047] As continued in Fig. 8 As can be seen, the outlet 16 can be designed to drain oil towards a bearing 175 of the rotor shaft 103. The bearing 175 can be designed, for example, as a ball bearing. The outlet opening 18 of the second outlet 16 in the area of ​​the bearing 175 is also shown in Fig. 6 easy to recognize.

[0048] Consequently, completely different bearings within the transmission 100 are supplied with lubricating oil via the oil guide channel part 1. In the illustrated embodiment of a transmission with a clutch device (so-called disconnect transmission), this advantageously occurs independently of the clutch state of the clutch device, so that sufficient lubrication of the bearings is always present in different clutch states.

[0049] However, the transmission with the oil guide channel part 1 can fundamentally be constructed differently. It is understood that, by means of the at least one first collecting basin and the outlets and / or connecting channels branching off from it to further collecting basins, an optimal supply of lubricating oil to the bearings of rotating transmission elements can be optimally adapted even for transmissions with a different design.

Claims

1. Transmission (100), in particular motor vehicle transmission, having a transmission housing (140) and having at least one gearwheel (107) arranged in the transmission housing (140), wherein the gearwheel (107) is arranged at least partially in an oil sump (150) of the transmission (100), wherein the transmission (100) has an oil guide channel part (1), wherein the oil guide channel part (1) has a conducting channel (2) with a receiving opening (11) and with an outlet opening (12), wherein the conducting channel (2) has from the receiving opening (11) to the outlet opening (12) an oil conducting direction (F) and a channel wall (21) which is peripherally closed perpendicular to the oil conducting direction (F), wherein the oil guide channel part (1) further has at least one oil collecting region (13a) for collecting oil conducted through the conducting channel (2), wherein the oil guide channel part (1) has at least one outflow (15a) for oil out of the at least one oil collecting region (13a), wherein the oil guide channel part (1) is arranged in the transmission housing (100) in such a way that oil discharged from the oil sump (150) by the gearwheel (107) during operation passes into the receiving opening (11) and along the oil conducting direction (F) of the conducting channel (2) to the outlet opening (12), wherein the at least one oil collecting region (13a) comprises a first collecting basin (13), wherein the first collecting basin (13) has a first basin wall (25) and a first basin base (24), wherein, in a predetermined installation state, which defines an orientation of the oil guide channel part (1) in the transmission housing (140) relative to gravitational force (G), the oil guide channel part (1) is arranged in the transmission housing (140) in such a way that the receiving opening (11) is positioned at the end face of the gearwheel (107), which is arranged at least partially in the oil sump (150), and the first basin base (24) is positioned above the gearwheel (107), and the oil conducting direction (F) from the receiving opening (11) to the outlet opening (12) extends counter to gravitational force (G), characterized in that that the transmission has a drive shaft (101) and an output shaft (102), wherein the output shaft (102) is able to be driven by means of the gearwheel (107), wherein a coupling element (122) is coupled to the gearwheel (107) in such a way that the gearwheel (107) can be driven by means of the coupling element (122), wherein a clutch device (120) with a clutch element (121) is provided in the transmission, wherein the clutch element (121) is coupled in a rotationally conjoint manner to the drive shaft (101), wherein, by means of the clutch device (120), the clutch element (121) can be coupled in a rotationally conjoint manner to the coupling element (122) and decoupled from the latter, and wherein the oil guide channel part (1) has a first outflow (15) which protrudes above the first basin base (24) from the first basin wall (25) and which has an outflow opening (17) through which outflowing oil is guided to a bearing (176) of a pinion (106) mounted rotatably on the drive shaft (101) and coupled in a rotationally conjoint manner to the coupling element (122).

2. Transmission (100) according to Claim 1, characterized in that an end of the channel wall (21) of the conducting channel (2) remote from the receiving opening (11) forms a peripheral wall (21a), which projects over the first basin base (24) of the first collecting basin (13) and delimits the outlet opening (12), in such a way that oil exiting from the outlet opening (12) of the conducting channel (2) accumulates in the first collecting basin (13) in a manner flowing out in the direction of gravitational force (G).

3. Transmission (100) according to either of the preceding claims, characterized in that the conducting channel (2) is straight and, at least in the region of the gearwheel (107), runs tangentially to an end face of the gearwheel (107), and the receiving opening (11) is positioned in the immediate vicinity of the end face of the gearwheel (107).

4. Transmission (100) according to Claim 1, characterized in that the drive shaft (101) is in the form of a hollow shaft with an axial bore (173), wherein the pinion (106) meshes with the gearwheel (107), wherein oil flowing out from the outflow opening (17) of the first outflow (15) passes into the axial bore (173) of the drive shaft (101) and, from there, to the bearing (176) via at least one radial bore (174), wherein the bearing (176) is in particular in the form of a needle roller bearing.

5. Transmission (100) according to Claim 4, characterized in that the oil flowing out from the outflow opening (17) of the first outflow (15) passes into a chamber (146) which is formed at a first housing part (141) of the transmission housing (140) and in which a pressure disc (180) is arranged, wherein a channel portion (181) is formed centrally on the pressure disc (180), wherein the channel portion (181) engages into the axial bore (173) of the drive shaft (101), wherein oil contained in the chamber (146) flows out into the channel portion (181) via the pressure disc (180) and thus passes into the axial bore (173) of the drive shaft (101).

6. Transmission (100) according to one of the preceding claims, characterized in that a rotor shaft (103) of an electrical machine (110), which rotor shaft is mounted in the transmission housing in at least one bearing (175), is provided, wherein the drive shaft (101) can be driven by means of the rotor shaft (103), and in that the oil collecting region (13a) of the oil guide channel part (1) comprises a second collecting basin (14), wherein the second collecting basin (14) has a second basin wall (27) and a second basin base (26), wherein the second collecting basin (14) is connected to the first collecting basin (13) via a connecting channel (29), wherein a second outflow (16) protrudes in the predetermined installation direction above the second basin base (26) from the second basin wall (27) of the second collecting basin (14) and has an outflow opening (18) through which oil is guided in the direction of the bearing (175) of the rotor shaft (103).

7. Transmission (100) according to Claim 6, characterized in that the edge of the peripheral wall (21a), on a side facing towards the first collecting basin (13), is at a distance from the first basin base (24) which is smaller than the distance of the edge of the peripheral wall (21a) from the second basin base (26) on a side facing towards the second collecting basin (14), and in that, when the gearwheel (107) rotates, firstly oil passes into the first collecting basin (13) before oil passes into the second collecting basin (14) via the connecting channel (29).

8. Transmission (100) according to one of the preceding claims, characterized in that the transmission housing (140) has a first housing part (141) with a first housing wall region (143) and has a second housing part (142), mounted onto the first housing part (141), with a second housing wall region (144), wherein, in the bearing region of the first housing part (141) and the second housing part (142), a third housing wall region (145) is placed, wherein the first housing wall region (143), the second housing wall region (144) and the third housing wall region (145) surround on three sides an end of the gearwheel (107) remote from the oil guide channel part (1) in the oil sump (150).

9. Transmission according to Claim 8, characterized in that a pump system is formed by the first housing wall region (143), the second housing wall region (144), the third housing wall region (145), the gearwheel (107) and the conducting channel (2), by way of which oil is transported from the oil sump (150) through the conducting channel (2) counter to gravitational force (G) to the outlet opening (12) of the conducting channel (2) when the gearwheel (107) rotates.

10. Transmission (100) according to one of the preceding claims, characterized in that the gearwheel (107) is coupled in a rotationally conjoint manner to a differential (130) of the transmission (100), wherein a first output shaft (102a) and a second output shaft (102b) are coupled to the differential (130), wherein the first output shaft (102a) and the second output shaft (102b) are driven in rotation by way of the differential (103).