Interlocking radial surface claw coupling

Abstract

A transmission comprising: a hollow shaft with at least two sets of radial through-holes, including a first set and a second set of radial through-holes; a plurality of gears arranged around the hollow shaft; a plurality of sliding keys arranged to extend through the radial through-holes of the hollow shaft and to engage in a plurality of recesses of a selected gear to engage and couple the selected gear; a plurality of sliding sleeves, each of the sliding keys being arranged between two sliding sleeves, the two sliding sleeves being spring-loaded and bearing against the sliding keys in such a way that only one gear is selected, thereby achieving a locking action for the sliding keys;and a rod configured to move coaxially to and along the hollow shaft, the rod comprising a cam-shaped section configured to actuate the plurality of sliding keys of the selected gear.

Description

TECHNICAL AREA

[0001] The present description refers to a system of a jaw coupling with a hollow shaft in which a rod is housed. BACKGROUND AND DETOUR

[0002] Vehicles can have a transmission containing a gear train with multiple sets of gears offering different gear ratios. The vehicle may be electrified, for example, a fully electric vehicle (EV) or a hybrid vehicle. A gear shifting mechanism with one or more clutches can be used to select different speeds. The gear shifting mechanism can be bulky and take up a significant amount of space within the transmission. Furthermore, a device located outside the shaft, referred to here as an external device, can be incorporated to limit the number of gears that the shifting mechanism can select simultaneously.

[0003] The volume occupied by the gearbox can affect the installation space available for additional gears and the overall volume of the gearbox. The external device for reducing the engagement of more than one gear can be removed from the gearshift mechanism, thereby reducing the installation space occupied by the gearshift mechanism. However, even without the external device, the gears in a gearbox assembly can still slip on the shaft, particularly at high speeds such as those encountered in an electric vehicle. Furthermore, engaging multiple gears simultaneously at high speeds can damage the selected gears, the shaft optionally coupled to those gears, and other components of the gearbox assembly.

[0004] The inventors here have recognized these and other problems with such systems and have found a way to solve them, at least in part. Thus, a transmission is disclosed comprising: a hollow shaft with at least two sets of radial through-holes, including a first set and a second set of radial through-holes; a plurality of gears arranged around the hollow shaft; a plurality of sliding wedges arranged to extend through the radial through-holes of the hollow shaft and engage in a plurality of recesses of a selected gear to engage and couple the selected gear; a plurality of sliding sleeves, each of the sliding wedges being arranged between two sliding sleeves, the two sliding sleeves being spring-loaded and bearing against the sliding wedges in such a way that only one gear is selected, thereby achieving a locking action for the sliding wedges;and a rod configured to move coaxially to and along the hollow shaft, the rod comprising a cam-shaped section configured to actuate the plurality of sliding keys of the selected gear.

[0005] The rod can be configured to simultaneously reduce radial contact and displacement with the first set of sliding wedges, the second set of sliding wedges, and the sliding wedges of other sets. Reducing contact decreases the selection of more than one gear at a time, while preventing the use of an external device, such as one comprising a fork and sleeve, to reduce the selection of multiple gears. The absence of an external device reduces the packing space of the jaw coupling assembly and gear train, while increasing the volume and packing space within the transmission. This approach addresses these problems by providing a gear selection system that reduces the volume and installation space of a gear train and prevents and / or reduces faulty gear selection.

[0006] It should be noted that the foregoing summary serves to present, in simplified form, a selection of concepts that are further explained in the detailed description. It does not serve to identify essential features of the claimed subject matter, the scope of which is defined exclusively by the claims following the detailed description. Furthermore, the claimed subject matter is not limited to implementations that eliminate the disadvantages mentioned above or in any part of this disclosure. BRIEF DESCRIPTION OF THE FIGURES Fig. Figure 1 shows a schematic example of a vehicle with a transmission and a gear selection arrangement as described in the present disclosure. Fig. Figure 2 shows a section of a claw coupling assembly comprising a hollow shaft with a rod. Fig. Figure 3 shows a section of the claw coupling arrangement. Fig. Figure 4 shows a side view and a section of the claw coupling assembly. Fig. Figure 5A shows a side view and a section of the rod of the claw coupling assembly in a first position. Fig. Figure 5B shows a side view and a section of the rod of the claw coupling in a second position. Fig. Figure 5C shows a side view and a section of the rod of the claw coupling in a third position. Fig. 5D shows a side view and a section of the rod of the claw coupling in a fourth position. Fig. Figure 6 shows a side view and a section of the rod of the claw coupling in the first position. Fig. Figure 7A shows a side view and a section of the rod of the claw coupling in the fourth position. Fig. Figure 7B shows the side view and section of the claw coupling in the fourth position with a variety of forces. Fig. Figure 8 shows a schematic representation of a claw coupling, a rod and a gear as defined in the present disclosure. Fig. Figure 9 shows a perspective view and a section of the claw coupling, a gear and a set of wedges. Fig. Figure 10 shows a front view and a section of the claw coupling, the gear, the wedges and a rod. Fig. Figure 11 shows a section of a sliding wedge of the present revelation. Fig. Figure 12 shows a side and perspective view of a gear of the present disclosure. DETAILED DESCRIPTION

[0007] The following description refers to a transmission of a drive train, wherein the transmission comprises one or more jaw coupling assemblies. Each jaw coupling assembly includes a hollow shaft with at least two sets of radial through-holes, including a first and a second set of radial through-holes. A plurality of gears may be arranged around the shaft. Additionally, there are a plurality of sliding keys configured to extend through the through-holes of the shaft and engage in the recesses of a selected gear. The geometry of the keys and a plurality of features of a plurality of sliding sleeves, such as surface finishes and / or other geometries of the sleeve, may achieve a locking action.The locking mechanism allows one, several, or all of the wedges in a set of wedges to be extended radially outward to engage with the selected gear and rigidly couple to it. The locking mechanism also secures the other wedges in the other sets of wedges in the arrangement. The locked wedges can be displaced closer to the shaft than the wedges engaging the selected gear, or they can be prevented from moving radially at all. In other words, the sleeves and the geometry of the wedges can create a locking mechanism that prevents more than one wedge from projecting radially outward to engage a gear and thus a gear speed. The locking mechanism prevents more than one gear from being selectively coupled to the shaft.

[0008] The jaw coupling assembly comprises a plurality of sliding sleeves, each sliding wedge being arranged between two spring-loaded sliding sleeves. The majority of the sliding sleeves can be accommodated via the shaft. The jaw coupling assembly includes a rod configured to move coaxially with and along the shaft. The rod is located within the shaft of the jaw coupling assembly. The rod includes a cam-shaped section configured to actuate the sliding wedges of the selected gear. Two sliding sleeves are configured to bear against each sliding wedge, and the cam-shaped section is configured to contact sets of sliding wedges, so that only one gear can be selected. At least two gears with two sets of sliding wedges can be arranged around the shaft, each set of sliding wedges being able to slide radially outward to engage with one of the two gears and selectively couple the gear to the shaft.There can be at least two sets of radial through-holes, wherein the wedges of each set of sliding wedges are accommodated in and slidable through the two sets of radial through-holes. Likewise, there can be at least two sets of recesses, wherein each set of recesses is specific for each of the at least two gears.

[0009] The following description also relates to a jaw coupling arrangement as defined in the present disclosure. The jaw coupling arrangement can be an example of a jaw coupling arrangement used in a transmission. The jaw coupling arrangement can selectively couple three gears to a shaft, while selectively coupling two or more gears to the shaft is reduced. The shaft can accommodate the three sets of splines via three sets of slots and a rod with a cam-shaped section. The cam-shaped section can contact a set of splines and displace it radially outward to engage with a specific gear among the three gears. The cam-shaped section is configured to reduce contact with more than one set of splines simultaneously. The cam-shaped section can be configured to prevent simultaneous engagement of more than one set of splines with a single gear.

[0010] The following description also refers to a method for selectively coupling gears via the jaw coupling assembly by moving the rod to different positions along a central axis of the shaft and the jaw coupling assembly. The rod can be advanced by increasing the pressure in a pressure cylinder or other pressure body responsible for actuating the rod. The rod can be retracted by decreasing the pressure on the pressure cylinder or other pressure body responsible for actuating the rod. It is understood, however, that the rod can also be additionally or alternatively actuated electrically, e.g., by a purely electric or electro-hydraulic actuator. The rod can be driven by an electric machine, e.g., an electric motor.The gears can be optionally coupled or uncoupled by moving the rod back and forth to different positions along the central axis.

[0011] Fig. Figure 1 shows a schematic example of a vehicle with a transmission and a gear selection arrangement as defined in the present disclosure. The transmission may be a dual-clutch hybrid transmission with a first electric motor and a second electric motor. Fig. Figure 2 shows a section of a jaw coupling assembly comprising a hollow shaft with a rod. The jaw coupling assembly includes a plurality of through holes extending from an inner surface to an outer surface of the shaft and arranged radially around a central axis of the shaft. Each of the multiple through holes can accommodate a sliding wedge, the sliding wedges extending radially outward from the shaft through the through holes. The through holes can be slots. The through holes and their respective sliding wedges can be arranged in sets, each set being radially arranged around a separate point along the central axis. A gear can be arranged radially around each set of through holes and sliding wedges, the gear being selectable (e.g., a selected gear) so that the sliding wedges are selectively coupled to the shaft.The sliding wedges of a set can extend radially outward into a plurality of recesses of a particular gear and slide, engaging in the recesses to selectively couple the particular gear to the shaft. When selectively coupled, the sliding wedges of the set can rigidly couple the gear to the shaft. When the gear is selectively coupled, all sets of wedges and all sliding sleeves of the jaw coupling assembly achieve a locking action, with the other sliding sleeves of the jaw coupling assembly, by achieving this locking action, reducing the distance that other sets of wedges can be displaced radially outward compared to the set of wedges selectively coupled to the gear. The rod includes a cam-shaped section that can contact the set of sliding wedges, thereby displacing the set of sliding wedges radially outward.The claw coupling assembly contains a plurality of sleeves, with each set of sliding wedges arranged between a pair of sleeves.

[0012] Fig. Figure 3 shows a side view and a section of the claw coupling assembly. Fig. Figure 4 shows a side view and a section of the claw coupling assembly. Fig. Figure 5A shows a side and sectional view of the rod of the jaw coupling assembly in a first position in which the cam-shaped section rests against a plurality of first sliding wedges. In the first position, the cam-shaped section contacts the sliding wedges at a portion of the cam-shaped section where the diameter is largest. Fig. Figure 5B shows a side view and a section of the jaw coupling rod in a second position. In the second position, the cam-shaped section contacts the sliding wedges on another part of the cam-shaped section, the diameter of which is smaller than the maximum diameter. Fig. Figure 5C shows a side view and a section of the jaw coupling rod in a third position. In the third position, the cam-shaped section is in a neutral position axially between the first sliding wedges and a plurality of second sliding wedges. Fig. 5D shows a side view and a section of the jaw coupling rod in a fourth position. In the fourth position, the cam-shaped section contacts the second set of wedges. Fig. Figure 6 shows a side view and a section of the rod of the claw coupling in the first position. Fig. Figure 6 shows additional features of the sliding wedges and sleeves. Fig. Figure 7A shows a side view and a section of the rod of the claw coupling in the fourth position. Fig. Figure 7B shows the side view and section of the claw coupling in the fourth position with a variety of forces. Fig. Figure 8 shows a schematic representation of a claw coupling, a rod and a gear as defined in the present disclosure. Fig. Figure 9 shows a perspective view and a section of the claw coupling, a gear and a set of wedges. Fig. Figure 10 shows a front view and a section of the claw coupling, the gear, the wedges and a rod. Fig. Figure 11 shows a section of a sliding wedge of the present revelation. Fig. Figure 12 shows a side and perspective view of a gear of the present disclosure. Fig. Figure 12 shows a perspective view of the recesses and their arrangement around the gear.

[0013] It is understood that the specific arrangements and systems shown in the accompanying drawings and described in the following description are exemplary embodiments of the inventive concepts defined herein. For the sake of clarity, the drawings are described together. Therefore, identical elements can be designated with the same reference numerals and need not be introduced again.

[0014] Fig. 1 and Fig. Figure 8 shows schematic representations of example configurations with relative positioning of the various components. Fig. 2-7B and Fig. Figures 9-12 show example configurations with approximate positions. Fig. 2-7B and Fig. Figures 9-12 are shown approximately to scale; however, other relative dimensions may also be used. In this context, the term "approximately" should be understood to include plus or minus five percent of the range, unless otherwise stated.

[0015] Furthermore, they Fig. Figures 1-12 show example configurations with the relative arrangement of the various components. If these elements are in direct contact with each other or directly coupled, they can be described as being in direct contact or directly coupled, respectively, in at least one example. Similarly, elements shown side by side or adjacent to each other can be described as being adjacent to each other or adjacent to each other, respectively, in at least one example. For instance, components that are in planar contact with each other can be described as being in planar contact. As another example, elements that are separated from each other, with only a gap between them and that have no other components, can be described as such in at least one case.In yet another example, elements that are displayed above / below each other, on opposite sides, or to the left / right of each other can be described as such, relative to one another. Furthermore, in at least one example, as shown in the figures, a topmost element or the highest point of an element can be referred to as the "top" of the component, and a bottommost element or the lowest point of the element can be referred to as the "bottom" of the component. The terms top / bottom, upper / lower, and above / below used here can refer to a vertical axis of the figures and be used to describe the positioning of elements within the figures relative to each other. Thus, in one example, elements displayed above other elements are arranged vertically above the other elements.As a further example, the shapes of the elements depicted in the figures can be described as such (e.g., circular, straight, planar, curved, rounded, beveled, angled, etc.). Furthermore, the depicted elements that intersect each other can be described as intersecting elements or mutually intersecting elements in at least one example. In addition, an element depicted inside or outside another element can be described as such. Finally, the components can be described with respect to the reference axes included in the drawings.

[0016] Features described as axial can be approximately parallel to a reference axis unless otherwise specified. Features described as anti-axial can be approximately perpendicular to the referenced axis unless otherwise specified. Features described as radial can circumferentially surround or extend outward from an axis, such as the reference axis, or a component or feature previously described as radial to a reference axis, unless otherwise specified.

[0017] Features described as longitudinal can run approximately parallel to a longitudinal axis. A lateral axis can be perpendicular to both a longitudinal axis and a vertical axis. Features described as lateral can run approximately parallel to the lateral axis. A vertical axis can be perpendicular to both a lateral axis and a longitudinal axis. Features described as vertical can be approximately parallel to a vertical axis.

[0018] Features described as drivingly coupled are coupled in such a way that they drive each other. Or, put another way: A first component that is drivingly coupled to a second component can drive the second component, and vice versa. In other words, torque can be transferred from a first component to a second component if the first component drives the second component. A component described as a driving component can drive another component. A component described as a driven component can be driven by another component.

[0019] In Fig. Figure 1 shows a vehicle 100 comprising a drivetrain 101 and a transmission 103. The vehicle 100 may have a front end 102 and a rear end 104 located on opposite sides of the vehicle 100. Objects, components, and features of the vehicle 100 described as being near the front may be closest to the front end 102 compared to the rear end 104. Objects, components, and features of the vehicle 100 described as being near the rear may be closest to the rear end 104 compared to the front end 102. The vehicle 100 may have a longitudinal axis 129. The drivetrain 101 and the transmission 103 may have a length parallel to the longitudinal axis 129. The vehicle 100 may have a transverse axis 130.

[0020] Vehicle 100 can be a commercial vehicle, a light, medium, or heavy commercial vehicle, a passenger vehicle, an off-road vehicle, a utility vehicle, an agricultural vehicle, and / or a sport utility vehicle. In one embodiment, Vehicle 100 can be a wheeled vehicle, such as an automobile. Additionally or alternatively, Vehicle 100 can also be an aircraft, a boat, or another vehicle system. Additionally or alternatively, Vehicle 100 and / or one or more of its components, such as components of the powertrain 101 and / or the powertrain 103, can be used in industrial, locomotive, military, agricultural, and / or aerospace applications. In one example, Vehicle 100 is a fully electric vehicle or a vehicle with fully electric operation, such as a plug-in hybrid vehicle.

[0021] The drive train 101 can be electrified, and the drive train 103 and the drive train within it can also be electrified. The drive train 103 and the drive train can be an electrified drive train or an electrified drive train. The drive train 101 can comprise a first electric machine 124, a second electric machine 126, and a gearbox 108. The first electric machine 124 and the second electric machine 126 are drives such as electric motors or electric motors / generators. The first electric machine 124 can be in a first position (P1) and the second electric machine 126 in a second position (P3). The first position can be closer to the front end 102 and the second position closer to the rear end 104. The electric machines 124 and 126 can supply the gearbox with torque via inputs.For example, the first electric machine 124 can be coupled to a first drive shaft 122 to drive it. The first electric machine 124 can be coupled to the gearbox via the first drive shaft 122 and supply it with torque. The second electric machine 126 can be coupled to a second drive shaft 128 to drive, for example, the second drive shaft 128. The second electric machine 126 can be coupled to the gearbox via the second drive shaft 128 and supply it with torque.

[0022] The powertrain 101 can also include a motor 120. The motor 120 can be an internal combustion engine (ICE) or a non-electric motor drive. The motor 120 can supply the transmission 108 with torque. For example, the motor 120 can be coupled to a second drive shaft 128 to drive the second drive shaft 128. The motor 120 can be coupled to the transmission via the second drive shaft 128 and supply it with torque.

[0023] The vehicle 100 and the drive train can include a drive motor. The drive motor can be, for example, an internal combustion engine (ICE) such as the motor 120. Another example: The drive motor can be an electric machine, such as the first electric machine 124 or the second electric machine 126. The drive motor is operated to supply the transmission 108 with rotational power. The transmission 108 receives the rotational power generated by the drive motor as input and delivers the rotational power to the drive train 103 according to a selected gear or set.

[0024] The drive motor can be supplied with energy from an energy storage device 105. The energy storage device 105 could be, for example, a battery, such as a drive battery, that can store electrical energy. Alternatively, the energy storage device 105 could be another device that stores electrical energy, such as a capacitor. An inverter 107, configured to convert direct current (DC) to alternating current (AC), can be arranged between the energy storage device 105 and the first electric motor 124. Similarly, an inverter 109, configured to convert direct current to alternating current, can be arranged between the energy storage device 105 and the second electric motor 126. The inverters 107 and 109 can contain a variety of components and circuits with thermal requirements that affect the efficiency of the inverters.

[0025] The powertrain 103 is shown in a rear-wheel-drive configuration, although other configurations are possible. In one or more examples, the powertrain 103 may include a front-wheel-drive, all-wheel-drive, or four-wheel-drive configuration. Thus, the powertrain 103 may also have other configurations without deviating from the scope of this disclosure, and those described in Fig. The configuration shown is for illustrative purposes only and does not represent a limitation.

[0026] The drivetrain 103 can include an axle assembly 112. The axle assembly 112 can be or include an axle configured to drive a set of wheels 114. The axle of the axle assembly 112 is a drive axle. In one example, the axle assembly 112 is located near the rear of the vehicle 100 and thus includes a rear axle. In another example, the axle assembly 112 can be located near the front of the vehicle 100 and thus includes a front axle. Furthermore, the drivetrain 103 can include one or more tandem axle assemblies. In other examples, there can be one or more axle assemblies in addition to the axle assembly 112. For example, an additional axle assembly, separate from the axle assembly 112, can be located at the front of the vehicle 100. The additional axle assembly can be coupled to a transmission for driving.The additional axle can, for example, be driven by the transmission 108 or another transmission. The vehicle 100 can have additional wheels and axles that are not coupled to the drive train 103. Thus, the drive train 103 can also have other configurations without deviating from the scope of this disclosure, and those described in . Fig. The configuration shown is for illustrative purposes only and does not represent a limitation.

[0027] The vehicle 100 can have a first drive shaft 122. The transmission 108 can be coupled to the axle assembly 112 via the first drive shaft 122. In other words, the transmission 108 can be coupled to the first drive shaft 122, and the first drive shaft 122 can be coupled to the axle assembly 112. In some configurations, such as in Fig. As shown in Figure 1, the drive train 103 includes a transfer case designed to receive the rotational power supplied by the gearbox 108. The first drive shaft 122 can be coupled to the transfer case and connected to the gearbox 108 via the transfer case.

[0028] The transmission 108 can be a gearbox. Alternatively, the transmission 108 can also be an axle gearbox or a transaxle gearbox and can be arranged in or part of an axle assembly such as the axle assembly 112. In some embodiments, the transmission 108 can additionally or alternatively be a first transmission, and the vehicle 100 can have one or more other transmissions, e.g., a second transmission. The second transmission can be located closer to the rear or in a different position on the vehicle 100 than the transmission 108.

[0029] The axle assembly 112 can include a differential 116 and a first set of axle shafts. The differential 116 can drive the first set of axle shafts by transmitting torque to and driving them. The first set of axle shafts can include a first shaft 118a and a second shaft 118b. The first shaft 118a and the second shaft 118b can be axle half-shafts. The differential 116 can distribute unequal torque to the wheels that are drive-coupled at opposite ends of the axle assembly 112. For example, the differential 116 can distribute unequal torque to the first shaft 118a and the second shaft 118b.

[0030] The transmission 108 can be coupled to the axle assembly 112 via the differential 116 and transmit torque to it. Furthermore, the first drive shaft 122 can be coupled to the output torque of the axle assembly 112 via the differential 116 and drive it. The first drive shaft 122 can be rigidly coupled or include a gear 150. The gear 150 can mesh with and be coupled to the gear set of the differential 116. The gear set of the differential 116 includes a ring gear 152. The pinion 150 can mesh with the gear 152 and drive the ring gear 152. The ring gear 152 can drive the gears of the differential and other gears of the differential 116, driving the first shaft 118a and the second shaft 118b.

[0031] The transmission 108 can, for example, be a transversely mounted dual-clutch hybrid transmission comprising one or more clutch arrangements of the present disclosure. The gear selector 142 can comprise a first jaw clutch arrangement 143 and / or a second jaw clutch arrangement 145. The first jaw clutch arrangement 143 and the second jaw clutch arrangement 145 can optionally be coupled to the outer drum 147 of a disengaging arrangement. The disengaging device comprising the outer drum 147 can be a clutch, for example, a friction clutch. The outer drum 147 can accommodate one or more clutches, e.g., friction clutches, and can optionally be coupled to them. The clutches housed in the outer drum 147 can be wet clutches. The transmission 108 can include a gear 140. The gear 140 comprises a bevel gear set.

[0032] The first claw coupling assembly 143 can be selectively coupled to the motor 120 and / or the second electric machine 126 via the outer drum 147 of a separating device. When the first claw coupling assembly 143 is selectively coupled via the outer drum 147, it can be driven by the motor 120 and / or the second electric machine 126. In other words, the first claw coupling assembly 143 can be driven by the motor 120 and the second electric machine 126 and absorb rotational energy, e.g., torque. Furthermore, the second claw coupling assembly 145 can selectively be coupled to the motor 120 and the second electric machine 126 via the outer drum 147. If it is optionally coupled via the outer drum 147, the second claw coupling arrangement 145 can be driven by the motor 120 and / or the second electric machine 126.In other words: The second claw coupling arrangement 145 can be driven by the motor 120 and the second electric machine 126 and receive rotational energy.

[0033] The couplings of the outer drum 147 can comprise a first coupling and a second coupling, wherein a first coupling can selectively couple the first claw coupling assembly 143 to the drum 147 and the second coupling can selectively couple the second claw coupling assembly 145 to the drum 147. In other words, the couplings can comprise an odd coupling and an even coupling, wherein the odd coupling can selectively be coupled to the drum 147 with an odd claw coupling assembly and the even coupling can selectively be coupled to the drum 147 with the even claw coupling assembly. The odd claw coupling assembly can be the second claw coupling assembly 145, which can be used to shift the odd gears of the transmission 108. The even-numbered claw clutch arrangement can be the first claw clutch arrangement 143 with which the even-numbered gears of the transmission 108 can be shifted.

[0034] The drum 147 can be selectively coupled to either the first claw coupling assembly 143 or the second claw coupling assembly 145 via a plurality of plates. For example, a first set of plates can be rigidly coupled to the drum 147, a second set of plates can be rigidly coupled to the first claw coupling assembly 143, and a third set of plates can be rigidly coupled to the second claw coupling assembly 145. The drum 147 can selectively couple the first claw coupling assembly 143 via the contact between the first and second sets of plates. The first coupling of the drum 147, which selectively couples the first claw coupling assembly 143, can encompass both the first and second sets of plates. Likewise, the drum 147 can selectively couple the second claw coupling arrangement 145 via the contact between the first set of lamellae and the third set of lamellae.The second coupling of the drum 147, which selectively couples the second jaw coupling assembly 145, can include the first set of plates and the third set of plates. The first jaw coupling assembly 143 can include a third shaft 146. The second plates can be rigidly coupled to the third shaft 146. The second jaw coupling assembly 145 can include a fourth shaft 148. The third plates can be rigidly coupled to the fourth shaft 148. The third shaft 146 can be referred to as an even-numbered shaft, for example, if the first jaw coupling assembly 143 is an even-numbered jaw coupling assembly. Likewise, the fourth shaft 148 can be referred to as an odd-numbered shaft, for example, if the second jaw coupling assembly 145 is an odd-numbered jaw coupling assembly.

[0035] The gear 140 can drive the motor 120 and the second electric machine 126 to the outer drum 147, so that the rotational energy can be transferred from there to the outer drum 147. The second drive shaft 128 can be driven by the gear 140, for example, to transmit torque and drive the gear 140. The gear 140 can be driven by the gear selector assembly 142, for example, to transmit torque and drive the components of the gear selector assembly 142. In particular, the gear 140 can be driven by the gear selector assembly via the drum 147. For example, the gear 140 can drive the first jaw coupling assembly 143 if the first jaw coupling assembly 143 is optionally driven by the outer drum 147.Another example: The gear can drive the second claw coupling arrangement 145 if the second claw coupling arrangement 145 is optionally coupled to the outer drum 147.

[0036] The third shaft 146 and the fourth shaft 148 can run parallel to the transverse axis 130. The third shaft 146 and the fourth shaft 148 can be arranged radially around the transverse axis 130. The first jaw coupling arrangement 143 and the second jaw coupling arrangement 145 are jaw coupling arrangements within the meaning of the present disclosure, each comprising an interlocking radial surface jaw coupling arrangement. The interlocking radial coupling has an integrated mechanical locking mechanism that allows the first jaw coupling arrangement 143 and the second jaw coupling arrangement 145 to interlock and be selectively coupled to certain gears of gear sets.

[0037] The adjustment of the powertrain 103 between the different operating modes, as well as the control of operation within each operating mode, can be based on a vehicle control system 132, including a controller 134. The controller 134 can be a microcomputer, including components such as a microprocessor unit, input / output connectors, an electronic storage medium for executable programs and calibration values ​​(e.g., a read-only memory chip), working memory, diagnostic memory, and a data bus. The storage medium can be programmed with computer-readable data representing instructions that can be executed by a processor to perform the procedures described below, as well as other variations that are expected but not explicitly listed. In one example, the controller 134 can be a powertrain control module (PCM).

[0038] The control unit 134 can receive various signals from sensors 136 that are connected to different areas of the vehicle 100. These sensors 136 may include, for example, sensors on the drive motor or another drive motor of the vehicle 100 for measuring the speed and temperature of the drive motor; a pedal position sensor for detecting the depressing of a pedal operated by the driver, such as an accelerator or brake pedal; a lever position sensor for detecting the movement of a lever, such as a brake lever; speed sensors on the wheelsets 114; and so on. In this example, the sensors 136 may include sensors that detect the engagement of a gear selector, which can select gear sets with different gear ratios of the transmission 108, for example, if the transmission 108 is an automatic transmission. The clutch selector device may be a lever or another clutch switch.After receiving the signals from the various sensors 136 . Fig. 1. The controller 134 processes the received signals and uses various actuators 138 of the vehicle 100 to adjust the operation of the transmission based on the received signals and the instructions stored in the controller 134's memory. For example, the controller 134 can receive a signal indicating the depressurization of the brake pedal, signaling a desire for a lower vehicle speed. The vehicle braking can be directly proportional to the position of the accelerator pedal, e.g., the degree of depressurization. Another example is that the controller 134 receives a signal indicating the depressurization of the accelerator pedal, signaling a desire for a higher vehicle speed. The vehicle acceleration can be directly proportional to the accelerator pedal position, e.g., the degree of depressurization. Subsequently, the controller 134 can command operations such as shifting gears and selecting gears of the transmission 108.Alternatively, the gears of the 108 transmission can also be shifted manually, e.g. if the 108 transmission is a manual transmission.

[0039] Returning to the transmission 108, several first gear sets, such as at least two gear sets (e.g., one gear set and another gear set), can be driven by the third shaft 146, so that they are driven by or drive the third shaft 146. Likewise, several second gear sets, such as at least two gear sets, can be driven by or drive the fourth shaft 148. The first jaw coupling assembly 143 and the second jaw coupling assembly 145 are configured to have a locking function that prevents more than one gear from selectively coupling either the third shaft 146 or the fourth shaft 148.Each of the first gear sets has at least one gear that can selectively couple the third shaft 146 and another gear that rigidly couples the second shaft, so that one of the several gear sets can selectively couple the third shaft 146 and drive the third shaft 146 with the second drive shaft 128. The locking of the first jaw coupling arrangement 143 ensures that the third shaft 146 can selectively be coupled to only one gear of the first gear set. Likewise, each of the second gear sets can have at least one gear that can selectively couple the fourth shaft 148 and another gear that rigidly couples the second drive shaft 128, so that the two gear sets therein can selectively be coupled to the fourth shaft 148 and drive the fourth shaft 148 with the second drive shaft 128.The capability of the second jaw coupling arrangement 145 ensures that the fourth shaft 148 can be selectively coupled to only one gear of the second gear set. A gear set selected to drive either the third shaft 146 or the fourth shaft 148 to the second shaft can be referred to here as a selected gear set. A gear that is selectively coupled to either the third shaft 146 or the fourth shaft 148 can be referred to here as a selected gear.

[0040] The gear selection arrangement can include hollow shafts, each hollow shaft accommodating a rod and a plurality of keys. The rod can be displaced through a hollow shaft to press against a set of keys from the plurality of keys. When the hollow shaft is contacted and pressed by the rod, the key from the plurality of keys can rotate the hollow shaft to a specific gear set, the key selectively coupling the shaft to a gear of the gear set. For example, the third shaft 146 can accommodate a first rod 192 and a plurality of first keys 196. The first rod 192 can be displaced coaxially along the transverse axis 130 or any other axis about which the third shaft 146 is centered. A set of first keys 196 can be pressed by the first rod 192 to selectively couple the third shaft 146 to a gear of a selected gear set from the first gear sets.Likewise, the fourth shaft 148 can accommodate a second rod 194 and a plurality of second splines 198. The second rod 194 can be displaced coaxially along the transverse axis 130 or another axis around which the fourth shaft 148 is centered. A set of second splines 198 can be pressed by the second rod 194 to selectively couple the fourth shaft 148 to a gear from a selected set of second gear sets.

[0041] The first gear sets can, for example, comprise a first gear set 154, a second gear set 156, a third gear set 158, and a fourth gear set 160 with different gear ratios. The third shaft 146 can be rotatably coupled and driven via the first gear set 154, the second gear set 156, the third gear set 158, or the fourth gear set 160 to the first drive shaft 122 by selectively engaging one gear from each gear set. Each of the first gear sets comprises at least one first gear and one second gear. The first gear set 154, for example, comprises a first gear 171 and a second gear 172. The second gear set 156 comprises a third gear 173 and a fourth gear 174. The third gear set 158 ​​comprises a fifth gear 175 and a sixth gear 176. The fourth gear set 160 comprises a seventh gear 177 and an eighth gear 178.

[0042] The first rod 192 can be moved so that it presses against a set of keys of the first keys 196 to selectively couple the third shaft 146 to either the first gear 171, the third gear 173, the fifth gear 175, or the seventh gear 177. Only one gear at a time from the first gear 171, the third gear 173, the fifth gear 175, or the seventh gear 177 can be selectively coupled to the third shaft 146 via the first rod 192. The first drive shaft 122 can be rigidly coupled to the second gear 172, the fourth gear 174, the sixth gear 176, and the eighth gear 178. The first gear 171 can mesh with the second gear 172. The third gear 173 can mesh with the fourth gear 174. The fifth gear 175 can mesh with the sixth gear 176. The seventh gear 177 can mesh with the gear 178.Alternatively, one or more idle gears can mesh between the first gear 171 and the second gear 172, the third gear 173 and the fourth gear 174, the fifth gear 175 and the sixth gear 176 and / or the seventh gear 177 and the eighth gear 178.

[0043] Additionally or alternatively, the second gear sets can comprise a fifth gear set 162, a sixth gear set 164, a seventh gear set 166, and an eighth gear set 168 with different gear ratios. The fourth shaft 148 can be rotatably coupled and driven to the first drive shaft 122 via the fifth gear set 162, the sixth gear set 164, the seventh gear set 166, or the eighth gear set 168 by selectively engaging one gear from each gear set. Each of the second gear sets comprises at least a third and a fourth gear. The fifth gear set 162 comprises a ninth gear 179 and a tenth gear 180. The sixth gear set 164 comprises an eleventh gear 181 and a twelfth gear 182. The seventh gear set 166 comprises a thirteenth gear 183 and a fourteenth gear 184. The eighth gear set 168 comprises a fifteenth gear 185 and a sixteenth gear 186.

[0044] The second rod 194 can be moved so that it presses on a set of sets of the second splines 198 to selectively couple the fourth shaft 148 to either the ninth gear 179, the eleventh gear 181, the thirteenth gear 183, or the fifteenth gear 185. Only one gear at a time from the ninth gear 179, the eleventh gear 181, the thirteenth gear 183, or the fifteenth gear 185 can be selectively coupled to the fourth shaft 148 via the second rod 194. The first drive shaft 122 can be rigidly coupled to the tenth gear 180, the twelfth gear 182, the fourteenth gear 184, and the sixteenth gear 186. The ninth gear 179 can mesh with the tenth gear 180. The eleventh gear 181 can mesh with the twelfth gear 182. The thirteenth gear 183 can mesh with the fourteenth gear 184. The fifteenth gear 185 can mesh with the sixteenth gear 186.Alternatively, one or more idle gears can mesh between the ninth gear 179 and the tenth gear 180, the eleventh gear 181 and the twelfth gear 182, the thirteenth gear 183 and the fourteenth gear 184 and / or the fifteenth gear 185 and the sixteenth gear 186.

[0045] Each gear set that can be engaged by the first and second dog clutch assembly can correspond to a different gear of the transmission. Odd gears (e.g., odd gears) and even gears (e.g., even gears) can be selected by different dog clutch assemblies of the transmission 108. For example, the first dog clutch assembly 143 is an even-numbered dog clutch assembly that can select even-numbered gears for the transmission 108. Likewise, the second dog clutch assembly 145 is an odd-numbered dog clutch assembly that can engage odd gears of the transmission 108. The gears can be in a larger ratio and designated with larger numbers. The gears for selecting a gear set can be marked with a Roman numeral indicating the gear number. Fig. 1 reproduces.

[0046] In this example, the ninth gear 179 is marked with the Roman numeral I for one, and when the ninth gear 179 is engaged via the second dog clutch assembly 145, first gear can be selected for the transmission 108. In other words, selecting the fifth gear set 162 selects first gear for the transmission 108. The eleventh gear 181 is marked with the Roman numeral III for three, and when the eleventh gear 181 is engaged via the second dog clutch assembly 145, third gear can be selected for the transmission 108. In other words, selecting the sixth gear set 164 selects third gear for the transmission 108. The thirteenth gear 183 is marked with the Roman numeral V for five, and when the thirteenth gear 183 is engaged via the second claw clutch arrangement 145, a fifth gear can be selected for the transmission 108.In other words, selecting the seventh gear set 166 selects the fifth gear for the transmission 108. The fifteenth gear 185 is marked with the Roman numeral VII for seven, and when the fifteenth gear 185 is engaged via the second dog clutch assembly 145, a seventh gear can be selected for the transmission 108. In other words, selecting the eighth gear set 168 selects the seventh gear for the transmission 108.

[0047] Additionally or alternatively, the first gear 171 is marked with the Roman numeral II for two, and when the first gear 171 is engaged via the first dog clutch assembly 143, a second gear can be selected for the transmission 108. In other words, selecting the first gear set 154 selects the second gear for the transmission 108. The third gear 173 is marked with the Roman numeral IV for four, and when the third gear 173 is engaged via the first dog clutch assembly 143, a fourth gear can be selected for the transmission 108. In other words, selecting the second gear set 156 selects the fourth gear of the transmission 108. The fifth gear 175 is marked with the Roman numeral VI for six, and when the fifth gear 175 is engaged via the first dog clutch assembly 143, a sixth gear can be selected for the transmission 108.In other words: Selecting the third gear set 158 ​​selects the sixth gear of the transmission 108. The seventh gear 177 is marked with the Roman numeral VIII for eight, and when the seventh gear 177 is engaged via the first dog clutch assembly 143, an eighth gear can be selected for the transmission 108. In other words: Selecting the fourth gear set 160 selects the eighth gear of the transmission 108.

[0048] The number of gears selectable by the 108 transmission is unlimited; it can offer more or fewer than eight gears. For example, the 108 transmission could be a six-speed transmission with six selectable gears. Alternatively, it could be a four-speed transmission with four selectable gears.

[0049] The number of gears selectable by the first dog clutch assembly 143 is unlimited, and the first dog clutch assembly 143 may select more or fewer than four gears. Likewise, the number of gears selectable by the second dog clutch assembly 145 is unlimited, and the second dog clutch assembly 145 may select more or fewer than four gears. For example, at least two gears may be selectable by the first dog clutch assembly 143 and / or at least two gears by the second dog clutch assembly 145.

[0050] This is how the transmission of a drive train is represented, wherein the transmission comprises one or more jaw coupling assemblies. Each jaw coupling assembly comprises a hollow shaft with at least two sets of radial through-holes, including a first and a second set of radial through-holes; a plurality of gears is arranged around the shaft. Each jaw coupling assembly comprises a plurality of sliding keys arranged to extend through the through-holes of the shaft and engage in the recesses of a selected gear. In the engaged state, the selected gear is selectively coupled to the shaft so that it rotates and turns with the shaft. Each jaw coupling assembly comprises a plurality of sliding sleeves, wherein each sliding key is arranged between two sliding sleeves that are spring-loaded and bear against the sliding key such that only one gear can be engaged.Each claw coupling assembly comprises a rod configured to move coaxially to and along the shaft, the rod comprising a cam-shaped section configured to actuate the plurality of sliding keys of the selected gear.

[0051] A set of reference axes 201 is used for comparison between the views in Fig. 2-3 provided. The reference axes 201 specify a y-axis, an x-axis, and a z-axis. In one example, the z-axis can be parallel to the direction of gravity, and the xy-plane can be parallel to a horizontal plane on which a claw coupling arrangement 202 is mounted. Fig. 2. A circle can represent an axis of the reference axes 201 that runs perpendicular to a view. A circle can represent an axis of the reference axes 201 that runs perpendicular to a view. A filled circle can represent an arrow and an axis that point towards a view or are positive to it. An unfilled circle can represent an arrow and an axis that point away from a view direction or are negative to it.

[0052] In Fig. Figure 2 shows a first view 200 of the claw coupling arrangement 202. The first view 200 is a sectional view of the claw coupling arrangement 202. The claw coupling arrangement 202 has a first side 204 and a second side 206, with the first side 204 facing the second side 206. The claw coupling arrangement 202 can be the axle arrangement 112 of Fig. 1. Act.

[0053] The claw coupling assembly 202 is centered about an axis 210. The axis 210 can be a central axis. Furthermore, the axis 210 can be a rotational axis around which the rotating elements of the claw coupling assembly 202 can rotate radially. The axis 210 can be a longitudinal axis for the claw coupling assembly 202, and directions parallel to the axis 210 can be referred to here as the longitudinal direction. However, it should be understood that the axis 210, with respect to a vehicle such as vehicle 100, Fig. 1, a transverse axis 130 of Fig. It can be 1.

[0054] The jaw coupling arrangement 202 comprises a first shaft 212, a body 213, and several gears. The body 213 can be arranged radially around the shaft 212, and the shaft 212 can rotate independently of the body 213. The gears can optionally be coupled to the shaft 212, with each gear being supported on at least one bearing arrangement that allows the gears to rotate freely on the shaft 212. The gears can be idle gears.

[0055] The jaw coupling arrangement 202 can, for example, comprise a first gear 214, a second gear 216, and a third gear 218 arranged radially around the shaft 212. A first bearing arrangement 222 can be arranged radially between the first gear 214 and the shaft 212, the first bearing arrangement 222 having a common surface with the first gear 214 and the shaft 212. The second bearing arrangement 224 can be arranged radially between the second gear 216 and the shaft 212, the second bearing arrangement 224 having a common surface with the second gear 216 and the shaft 212. The third bearing arrangement 226 can be arranged radially between the third gear 218 and the shaft 212, the third bearing arrangement 226 having a common surface with the third gear 218 and the shaft 212.The first bearing arrangement 222, the second bearing arrangement 224, and the third bearing arrangement 226 can be rolling bearings, each comprising a plurality of rolling bearing elements between an inner and an outer ring. It is understood that the first gear 214, the second gear 216, and the third gear 218 can be supported by additional bearings.

[0056] A fourth bearing arrangement 228 can be arranged radially around the body 213 and be in surface contact with it. The body 213 is a disc that carries one or more coupling drums for the bearing arrangement, such as the drum 147 in Fig. 1. The fourth bearing arrangement 228 can carry a coupling arrangement and one or more coupling drums, which can optionally be coupled to the jaw coupling arrangement 202. The fourth bearing arrangement 228 can be located closer to the second side 206 than the first bearing arrangement 222. A fifth bearing arrangement 230 can be arranged radially around the shaft 212 and in planar contact with it. The fifth bearing arrangement 230 can be located closer to the first side 204 than the third bearing arrangement 226. The fifth bearing arrangement 230 can contain one or more bearings. The fifth bearing arrangement 230 can, for example, contain a double-row angular contact ball bearing. The fifth bearing arrangement 230 can be coupled to the shaft 212 by means of a lock nut 238. The lock nut 238 can prevent displacement or other movement of the fifth bearing arrangement 230, e.g. B. in directions parallel to axis 210.

[0057] Some of the additional bearings are arranged axially between adjacent gears or between a gear and another component to support them and allow their rotation. For example, each of the first gear 214, the second gear 216, and the third gear 218 can be supported by a pair of bearings. A first pair of bearing assemblies supporting the first gear 214 can include the first bearing assembly 222 and a sixth bearing assembly 225. The sixth bearing assembly 225 can be inserted between the first gear 214 and the second gear 216. More precisely, the sixth bearing assembly 225 can be arranged radially between the first gear 214 and the second gear 216. A second pair of bearing assemblies supporting the second gear 216 can include the second bearing assembly 224 and a seventh bearing assembly 227. The seventh bearing arrangement 227 can be inserted between the second gear 216 and the third gear 218.More precisely, the seventh bearing arrangement 227 can be arranged radially between the second gear 216 and the third gear 218. A third pair of bearing arrangements supporting the third gear 218 can comprise the third bearing arrangement 226 and an eighth bearing arrangement 229. The eighth bearing arrangement 229 can be arranged between the third gear 218 and the fifth bearing arrangement 230. Likewise, another component can be inserted between the third bearing arrangement 226 and the fifth bearing arrangement 230. The sixth bearing arrangement 225, the seventh bearing arrangement 227, and the eighth bearing arrangement 229 can be or include a bearing, such as a roller bearing. For example, the sixth bearing arrangement 225, the seventh bearing arrangement 227, and the eighth bearing arrangement 229 can be or include a needle roller bearing comprising a plurality of needle roller elements.

[0058] The first gear 214, the second gear 216, and the third gear 218 can be idle gears. The first gear 214 can be a gear like the seventh gear 177 or the fifteenth gear 185 of Fig. 1. The second gear 216 can be a gear like the fifth gear 175 or the thirteenth gear 183 of Fig. 1. The third gear 218 can be a gear like the third gear 173 or the eleventh gear 181 of Fig. Be 1.

[0059] The shaft 212 can have a first fluid passage 232 and a second fluid passage, both radially centered around the axis 210. The second passage comprises a first section 234 and a second section 236 with different diameters. The second diameter of the second section 236 can be larger than the first diameter of the first section 234. The first section 234 can be coupled to the first passage 232 via an opening 240. The first section 234 can have a recess 242 extending radially from the opening 240.

[0060] The lock nut 238 can be rigidly coupled to the shaft 212 via the second section 236. The lock nut 238 can be a plug. The lock nut 238 can have a flange that extends radially and abuts the fifth bearing assembly 230. The lock nut 238 can have an opening 244, which can be coupled to the second section 236. Fluid can exit the shaft 212 and the second section 236 via the opening 244. The opening 244 can be concentric with the lock nut 238, and the lock nut 238 and the opening 244 can be radially centered about the axis 210. The opening 244 can direct lubricant and / or actuating fluid to another coupling, e.g., another jaw coupling. For example, if the claw coupling arrangement 202 is an even coupling, the opening 244 can supply lubricant to an odd coupling and vice versa.The opening 244 can also accommodate lubricant and / or actuating fluid. Fluid can be supplied to the second passage via the opening 244, thereby increasing the pressure there.

[0061] The shaft 212 can be equipped with a hydraulic cylinder. The first section 234 can accommodate a rod 246 and a frame 248, which can be radially centered around the axis 210. The frame 248 can be the body (e.g., a pressure body) of the hydraulic cylinder and be arranged radially around the rod 246. The frame 248 can approximately center the rod 246 around the axis 210 and prevent the rod 246 from moving in a direction perpendicular to the axis 210 or at an angle of more than ±5% to it. The frame 248 can be fixed so that it is rigidly coupled to the shaft 212. The rod 246 can be displaced in directions parallel, e.g., coaxial, to the axis 210. If the rod 246 is moved beyond one or more distance thresholds, it can come into contact with the frame 248, thus preventing further movement of the rod 246 in one direction.For example, the rod 246 can be prevented from moving beyond a first or second point along the axis 210 by abutting the frame 248, with the surfaces at opposite ends of the frame 248 abutting and thus reducing the movement of the rod 246. The hydraulic cylinder can actuate the rod 246 by changing the hydraulic pressure. During actuation, the rod 246 can be moved to different positions along the axis 210.

[0062] It goes without saying that the rod 246 can also be operated electrically, either additionally or alternatively, e.g., by a purely electric or electro-hydraulic actuator. The rod 246 can be driven by an electric machine, e.g., an electric motor.

[0063] Fig. Figure 8 shows a seventh view 800 of a jaw coupling assembly 802 with a shaft 812, a gear 814, and a cam 846 radially centered about an axis 810. The jaw coupling assembly 802 is shown schematically with relative positioning and dimensions. The axis 810 can be aligned with the axis 210. Fig. 2. The claw coupling arrangement 802 can be the claw coupling arrangement 202 from Fig. 2. Likewise, wave 812 and cam 846 can replace wave 212 and cam 294. Fig. 2 be. The rod 246 of Fig. 2 can encompass the cam 294 or be rigidly coupled to it. Furthermore, the gear 814 can engage the first gear 214, the second gear 216, or the third gear 218 of Fig. 2. A plurality of axes 816 can extend radially outwards and run perpendicular to the axis 810.

[0064] The shaft 812 comprises a plurality of through holes 852 extending from an outer surface 822 to an inner surface 824 through the shaft 812. The gear 814 may have a plurality of recesses 864. The through holes 852 are arranged radially around the shaft 812 and extend radially outward; the through holes 852 may alternatively be referred to as radial through holes 852. The through holes 852 may be slots. The shaft 812 may also accommodate a plurality of keys 858 via the through holes 852, each through hole of the through holes 852 being able to accommodate at least one key of the keys 858. The through holes 852 may be slots having a rectangular shape and a rectangular cross-sectional area, and the through holes 852 may have a prismatic volume.

[0065] The through-holes 852 are dimensioned such that the sliding wedges 858 can be displaced radially outwards and inwards through the through-holes 852; they can also be referred to here as sliding wedges 858. When each sliding wedge of the sliding wedges 858 is displaced, the sliding wedge slides radially outwards or inwards from the axis 810. The sliding wedges 858 can be forced to move radially outwards from the shaft 812 by contact with the cam 846. When sliding wedges, such as sliding wedges 858, are displaced and extended in this way, they can be described as being withdrawn from the shaft 812. The sliding wedges 858 can be forced to displace and retract radially inwards towards the shaft 812 by releasing the contact with the cam 846. When each sliding wedge of the sliding wedges 858 is retracted, the sliding wedge can slide inwards in the direction of the axis 810 along an axis of the axes 816.When they are moved radially inwards in this way, the sliding wedges 858 can be described as being retracted.

[0066] The gear 814 can have a plurality of recesses 864 extending radially outward from an inner surface of the gear 814. The recesses 864 can be slots with a rectangular shape and cross-sectional area, or they can have a prismatic volume. The number of recesses 864 can be a multiple of the number of through holes 852, thereby increasing the engagement speed and making the shaft 812 more robust during engagement. The greater the ratio of recesses 864 to through holes 852, the faster the engagement can occur.

[0067] The through holes 852 can be grouped and arranged in a set corresponding to the gear 814, the gear 814 being positioned radially around the through holes 852 such that each through hole of the through holes 852 can be aligned with at least one recess of the recesses 864, each through hole of the through holes 852 being centered about a common axis with a recess of the recesses 864. For example, each of the through holes 852 can be centered with a recess of the recesses 864 about an axis of the axes 816. Likewise, the sliding wedges 858 can be grouped into another set corresponding to the set of through holes 852 and the gear 814, the sliding wedges 858 being drawn out of the shaft 812 and inserted into recesses 864. To engage in the recesses 864, each of the sliding wedges 858 can slide along one axis of the axes 816.When they engage in the recesses 864, the sliding wedges 858 can optionally couple the gear to the shaft 812.

[0068] For each gear of the jaw coupling assembly 802, there is a corresponding set of through holes and sliding keys, the corresponding set of sliding keys engaging in recesses of the gear to selectively couple the gear to the shaft 812. The jaw coupling assembly 802 can comprise at least a first and a second set of through holes and a first and a second set of sliding keys. The first sets of through holes and sliding keys correspond to a first gear and selectively couple it. The second set of through holes and sliding keys corresponds to a second gear and selectively couples it.

[0069] There can be at least three sliding wedges for each set of sliding wedges and at least three through holes for each set of through holes. The three sliding wedges are intended to ensure the balancing of the system for the jaw coupling assembly 802, since just one wedge from a set of wedges can unbalance the system due to centrifugal force. With fewer than three sliding wedges, the correct positioning of the rod for contact with the sliding wedges of a set may not be ensured, since the rod can be held centered along the axis 810 and held in position by the sliding wedges, the sliding wedges 858. However, it is understood that there can be more than three sliding wedges for each set of sliding wedges and three through holes for each set of through holes. For example, there can be four sliding wedges 858 and four through holes 852.

[0070] Back to Fig. 2. The shaft 212 can have a plurality of through holes, each of which can accommodate a key that can be fitted into and extend through it. The radial through holes can be arranged radially around the axis 210 and extend radially outward through the material of the shaft 212. The radial through holes can be arranged in a plurality of sets. Each radial set of through holes can be arranged in an annular pattern around the axis 210. Each set of through holes can have a complementary set of keys, each key of the set of keys fitting into and sliding through a radial through hole of the set of radial through holes. Each set of through holes is specific to a gear, the gear being arranged radially around the set of radial through holes.The shaft 212 can contain at least two sets of radial through holes with a set of keys. However, the shaft 212 can have more than two sets of radial through holes, whereby a set of radial through holes can be provided on the shaft 212 during manufacturing for each gear that is to be engaged via the jaw coupling.

[0071] The sets of keys complementary to the radial through-holes can be displaced radially outward and abut features of the gear. These features include recesses, where each key can be pulled out by sliding into a volume of the recess. Each key can rest against and contact the surfaces of the recess and, upon withdrawal, snap into place. The radial through-holes have geometries that reduce the self-locking of each set of sliding keys. For example, the radial through-holes have a larger cross-sectional area and width than the keys, allowing the keys to be pushed into them.However, the cross-sectional areas and widths are below a first threshold for area and a second threshold for spacing, thus reducing the number of wedges and preventing the wedges from sliding without an intentional force above a third force threshold. Similarly, a pair of sleeves on opposite sides of each set of wedges, and the geometries of the sleeves, can reduce the self-locking of the wedges by limiting their radial movement without a force greater than a fourth force threshold. Above the fourth force threshold, the sleeves can be spread apart, allowing a set of wedges to be displaced radially outward through the radial through-holes.

[0072] The second passage, more precisely the second section 236, can accommodate a variety of springs. The second passage can also accommodate multiple hard stops, for example, a first hard stop 270 and a second hard stop 272. Each wedge can be located axially along the axis 210 between a pair of sleeves and a pair of springs. One or more springs can be located axially along the axis 210 between a pair of springs. Additionally, one or more of the other springs can be located axially along the axis 210 between a hard stop and a sleeve. There can be at least one more spring than the total number of wedge sets. For example, if there are three sets of wedges, there can be four springs.

[0073] Each set of keys can be arranged axially between a set of sleeves. Each set of sleeves comprises at least one pair of sleeves. In other words, each set of sliding sleeves comprises a first sliding sleeve and a second sliding sleeve, which can be arranged on opposite sides of a set of keys. The sleeves can be displaced and spread apart along axis 210. The sleeves can be displaced by sliding sleeves and are also referred to here as sliding sleeves. One sleeve and another sleeve of the pair of sleeves can bear against each key of the key set on opposite sides in the axial direction with respect to axis 210. The sleeve and the other sleeve can be supported on the shaft. A spring can be arranged between the sleeve and a surface. Likewise, another spring can be arranged between the other sleeve and another surface.The spring and the other spring exert spring forces on the opposite sides of the keys via contact with the sleeve and the other sleeve, respectively. Or, put another way: The spring can press the sleeve and the other spring can press the other sleeve against the intervening set of keys. The spring force of the spring and the other spring can force the set of keys to retract into the shaft 212. Each set of sliding sleeves can reduce the radial displacement of one or more keys of a set of keys arranged between the sliding sleeves when there is no contact between the rod 246 and the keys. Each of the sliding sleeves of the jaw coupling assembly 202 is part of a set of sliding sleeves belonging to a set of intervening sliding keys.

[0074] For example, the shaft 212 can have a first set of first through holes 252, a second set of second through holes 254, and a third set of third through holes 256. A set of multiple first keys 258 can be fitted into and accommodated in the first through holes 252. A set of multiple second keys 260 can be fitted into and accommodated in the second through holes 254. Multiple third keys 262 can be fitted into and accommodated in the third through holes 256. The first keys 258, the second keys 260, and the third keys 262 can be displaced radially outward from the shaft 210 through the first through holes 252, the second through holes 254, and the third through holes 256, respectively. The first wedges 258, the second wedges 260 and the third wedges 262 can be translated by sliding and are therefore also called sliding wedges (e.g.the first sliding wedges 258, the second sliding wedges 260 and the third sliding wedges 262). The first through holes 252, the second through holes 254 and the third through holes 256 may be cut out of the shaft 212 by a machining technique, e.g. by milling.

[0075] The first gear 214 can have a plurality of first recesses 264, wherein the first recesses 264 extend radially outward into the material of the first gear 214. The second gear 216 can have a plurality of second recesses 266, wherein the second recesses 266 extend radially outward into the material of the second gear 216. The third gear 218 can have a plurality of third recesses 268, wherein the third recesses 268 extend radially outward into the material of the third gear 218. The recesses 264, 266, 268 can be pressed radially outward from an inner diameter of the first gear 214, the second gear 216, and the third gear 218, respectively. The recesses 264, 266, 268 can be cut out of the first gear 214, the second gear 216 or the third gear 218 by a machining technique, e.g. by profile drilling.The first gear 214 can be arranged around the shaft 212 such that the first recesses 264 are arranged radially around the first through holes 252. The second gear 216 can be arranged around the shaft 212 such that the second recesses 266 are arranged radially around the second through holes 254. The third gear 218 can be arranged around the shaft 212 such that the third recesses 268 are arranged radially around the third through holes 256.

[0076] The first wedges 258, the second wedges 260, and the third wedges 262 can be symmetrical. Likewise, the number of recesses in the first recesses 264, the second recesses 266, and the third recesses 268 can be symmetrical. Furthermore, the number of first recesses 264, second recesses 266, and / or third recesses 268 can be a multiple of the number of first wedges 258, second wedges 260, and / or third wedges 262, respectively.

[0077] The first wedges 258 can be arranged axially to the axis 210 between a first sleeve 274a and a second sleeve 276a. The first sleeve 274a and the second sleeve 276a constitute a first set of sliding sleeves. The second wedges 260 can be arranged with respect to the axis 210 between a third sleeve 274b and a fourth sleeve 276b. The third sleeve 274b and the fourth sleeve 276b constitute a second set of sliding sleeves. The third wedges 262 can be arranged with respect to the axis 210 between a fifth sleeve 274c and a sixth sleeve 276c. The fifth sleeve 274c and the sixth sleeve 276c constitute a third set of sliding sleeves. The first hard stop 270 can be located closer to the second side 206 of the arrangement than the second hard stop 272, and the first hard stop 270 can abut the frame 248. The second hard stop 272 can abut the lock nut 238.A first spring 280 can be arranged axially between the first hard stop 270 and the first sleeve 274a and be in contact with them. A second spring 282 can be arranged axially between the second sleeve 276a and the third sleeve 274b and be in contact with them. A third spring 284 can be arranged axially between the fourth sleeve 276b and the fifth sleeve 274c and be in contact with them. A fourth spring 286 can be arranged axially between the sixth sleeve 276c and the second hard stop 272 and be in contact with them. The first sleeve 274a, the third sleeve 274b, and the fifth sleeve 274c can be symmetrical. Likewise, the second sleeve 276a, the fourth sleeve 276b, and the sixth sleeve 276c can be symmetrical. The first sleeve 274a can be symmetrical with respect to the second sleeve 276a and be a mirror image of it. The third sleeve 274b can be symmetrical to the fourth sleeve 276b and mirror it. The fifth sleeve 274c can be symmetrical to the sixth sleeve 276c and mirror it.

[0078] The rod 246 comprises a cam-shaped section 294, a piston section, and a shaft 296. The shaft 296 connects and couples the piston-shaped section at a first end to the cam-shaped section 294 at a second end of the rod 246, with the first end of the rod 246 facing the second end. The piston section comprises or is a piston, here referred to as piston 292. The piston 292 may have a larger diameter than the maximum diameter of the cam-shaped section 294. The cam-shaped section 294 also comprises or is a cam. The piston 292 includes a cylindrical web that extends radially outward from the shaft 296. The cam-shaped section 294 may have an elliptical shape, e.g., an oval cam shape. The cam-shaped section 294 may press against one or more keys of a wedge set to be translated and radially spread. B.on the first keys 258, the second keys 260 or the third keys 262. The frame 248 can seal against the shaft 296.

[0079] The first keys 258, the second keys 260, or the third keys 262 can be displaced radially outward or radially inward from the axis 210 through the first through holes 252, the second through holes 254, or the third through holes 256. Contact with the rod 246 can force the first keys 258, the second keys 260, or the third keys 262 to move radially outward and withdraw from the shaft 212. More precisely, contact with the cam-shaped section 294 can force the first keys 258, the second keys 260, or the third keys 262 to be displaced radially outward and withdrawn from the shaft 212. When being pulled out, the first wedges 258 can engage in the first recesses 264, so that they rest against the first recesses 264 and are rigidly coupled to them, thereby optionally coupling the first gear 214 to the shaft 212.When pulled out, the second wedges 260 can engage in the second recesses 266, so that they bear against the second recesses 266 and are rigidly coupled to them, thereby selectively connecting the second gear 216 to the shaft 212. When pulled out, the third wedges 262 can engage in the third recesses 268, so that they bear against the third recesses 268 and are rigidly coupled to them, thereby selectively coupling the third gear 218 to the shaft 212.

[0080] A lack of contact with the cam-shaped section 294 can cause the first keys 258, the second keys 260, or the third keys 262 to be displaced radially inwards and retracted towards the shaft 212. Contact between the first sleeve 274a and the second sleeve 276a, as well as the spring force of the first spring 280 and the second spring 282, can cause the first keys 258 to be retracted towards the shaft 212. Contact between the third sleeve 274b and the fourth sleeve 276b, as well as the spring force of the second spring 282 and the third spring 284, can cause the second keys 260 to be retracted towards the shaft 212. The contact between the fifth sleeve 274c and the sixth sleeve 276c, as well as the spring forces of the third spring 284 and the fourth spring 286, can cause the third wedges 262 to be retracted to the shaft 212.

[0081] It is understood that the keys, such as the first key 258, the second key 260, and the third key 262, cannot be retracted during the transmission of torque to the shaft 212 and the rotation of the shaft 212. If the transmission of torque to the shaft 212 and the rotation of the shaft 212 continue, a set of sliding keys, which selectively engages a gear with the shaft 212, can remain engaged with their respective recesses even after the cam-shaped section 294 has been removed from a meshing position with the keys. This mechanically locks an adjacent set of keys, thereby reducing the cam-shaped section 294 from clamping adjacent keys to the locked keys, which move radially outward upon contact, and preventing the rod 246 from engaging the next gear or any other gear.In such cases, a locked sleeve, between which the locked wedges are arranged, restricts the movement of the rod 246 along the axis 210. The locked wedges can be contacted by the rod 246 and prevented from moving by the locked sleeve, and the locked wedges can reduce the further axial movement of the rod 246 when pressed against them. The relationship between a withdrawn set of wedges preventing the withdrawal of other sets of wedges via the sliding sleeves can be related to a locking function of the jaw coupling arrangement 202.

[0082] In other words, the first wedges 258, the second wedges 260, and the third wedges 262 can achieve a locking action with the first sleeve 274a and the second sleeve 276a, the third sleeve 274b and the fourth sleeve 276b, and the fifth sleeve 274c and the sixth sleeve 276c, respectively. The locking action can allow either the first wedges 258, the second wedges 260, or the third wedges 262 to extend and be withdrawn, while the distance over which other wedges extend can be reduced below a threshold distance. Additionally or alternatively, the locking action can prevent the other sets of wedges in the jaw coupling assembly 202 from withdrawing further wedges from sets of wedges that have been withdrawn or are being withdrawn. The threshold for the distance is smaller than the radial distance for the wedges of the other sets of wedges of the claw coupling arrangement 202, which can be pulled out into their respective recesses.For example, the first wedges 258, the second wedges 260, or the third wedges 262 are pulled out of the first recesses 264, the second recesses 266, or the third recesses 268, respectively, when they are displaced in a radial direction smaller than the threshold for the distance. In other words, the first wedges 258, the second wedges 260, or the third wedges 262 remain in place when they are displaced in a radial direction smaller than the threshold for the distance.

[0083] The hydraulic cylinder can actuate the cam of the cam-shaped section 294 by changing the hydraulic pressure on an actuating chamber between the piston 292 and the opening 240. The actuating chamber can be enclosed by the frame 248 and formed between the piston 292 and a surface of the frame 248.

[0084] The hydraulic cylinder can be a double-sided hydraulic cylinder in which the pressure on both sides of the piston 292 can be increased, thereby displacing the rod 246 in directions opposite to the side of the pressure increase. For example, an increase in hydraulic pressure in the chamber on the side of the piston 292 facing the second side 206 can force the rod 246 to move towards the first side 204. Likewise, an increase in hydraulic pressure in the chamber on the side of the piston 292 facing the first side 204 can force the rod 246 to move towards the second side 206. The hydraulic cylinder can thereby bring the cam-shaped section 294 into and out of contact with either the first wedges 258, the second wedges 260, or the third wedges 262.

[0085] Fig. Figure 3 shows a second view 300 of the claw coupling arrangement 202. The second view 300 is a side view and a section of the claw coupling arrangement 202.

[0086] The second view 300 shows that the frame 248 has an opening 332. The opening 332 can be radially centered around the axis 210 and be concentric with the frame 248. Through the opening 332, the third passage 298 can connect with the first passage 232.

[0087] A fastening element 334 can rigidly couple the frame 248 to the shaft 212. The fastening element 334 can be a snap ring having a tongue and groove arrangement with an inner surface of the shaft 212. More precisely, the fastener 334 can have a tongue and groove arrangement with a surface of the shaft 212 bent radially around the second section 236.

[0088] The first bearing arrangement 222, the second bearing arrangement 224, and the third bearing arrangement 226 can each contain a plurality of first bearing elements 342. The fourth bearing arrangement 228 can comprise a plurality of second bearing elements 344. And the fifth bearing arrangement 230 can comprise a plurality of third bearing elements 346. The first and second bearing elements 342 and 344 can be roller bearing elements. The third bearing elements 346 can be ball bearing elements.

[0089] Fig. Figure 4 shows a third view 400 of the claw coupling assembly 202. The third view 400 is a side view and a section of the claw coupling assembly 202. The third view 400 includes an area 410. The area 410 is enclosed by a rectangle of dashed lines. Another section, such as the fourth view 500 in Fig. 5A-5D can be recorded from area 410.

[0090] The claw coupling arrangement 202 comprises a plurality of wedge axes over which each wedge of the sets of wedges 258, 260, 262 can slide axially. Each set of wedge axes can accommodate the axes 816 of Fig. 8. For example, each wedge of the first wedges 258 can slide radially outward or inward in the direction of the axis 210 along a first wedge axis of a plurality of first wedge axes 442. Each wedge of the second wedges 260 can slide radially outward or inward in the direction of the axis 210 along a second wedge axis from a plurality of second wedge axes 444. Each wedge of the third wedges 262 can slide radially outward or inward in the direction of the axis 210 along a third wedge axis 446 from a plurality of third wedge axes 446. The first wedge axis 442, the second wedge axis 444 and the third wedge axis 446 extend in a radial direction from the axis 210. The center lines of the first wedges 258, the second wedges 260 and the third wedges 262 can run coaxially to the first wedge axes 442, the second wedge axes 444 and the third wedge axes 446.Likewise, each of the first through holes 252 and the first recesses 264 can be centered about a first axis of the first wedge axes 442. Each of the second through holes 254 and the second recesses 266 can be centered about a second axis of the second wedge axes 444. Each of the third through holes 256 and the third recesses 268 can be centered about a third axis of the third wedge axes 446. The first wedges 258 can move by sliding through the first through holes 252 and into the first recesses 264 along the first wedge axes 442. The second wedges 260 can move by sliding through the second through holes 254 and into the second recesses 266 along the second wedge axes 444. The third wedges 262 can be moved by sliding through the third through holes 256 and into the third recesses 268 along the third wedge axes 446.In the example of the claw coupling arrangement 202 shown in the third view 400, the first wedges 258 extend along the first wedge axes 442 in order to be pulled off the shaft 212 and engage with the first gear 214.

[0091] Each of the sleeves 274a, 276a, 274b, 276b, 274c, and 276c can have openings through which the rod 246, and in particular the cam-shaped section 294, can pass. For example, the first sleeve 274a has a first opening 452a. The second sleeve 276a has a second opening 454a. The third sleeve 274b has a third opening 452b. The fourth sleeve 276b has a fourth opening 454b. The fifth sleeve 274c has a fifth opening 452c. The sixth sleeve 276c includes a sixth opening 454c. In addition, the first hard stop 270 has a seventh opening 458 and the second hard stop 272 has an eighth opening 460 through which the rod 246, in particular the cam-shaped section 294, can be passed.

[0092] Each of the sleeves 274a, 276a, 274b, 276b, 274c, and 276c has at least one projection extending radially around the respective openings of the sleeves. For example, the first sleeve 274a includes a first projection 462a that bulges radially around the first opening 452a. The second sleeve 276a includes a second projection 464a that bulges radially around the second opening 454a. The third sleeve 274b includes a third projection 462b that bulges radially around the third opening 452b. The fourth sleeve 276b includes a fourth projection 464b that bulges radially around the fourth opening 454b. The fifth sleeve 274c includes a fifth projection 462c that bulges radially around the fifth opening 452c. The sixth sleeve 276c includes a sixth projection 464c that curves radially around the sixth opening 454c.

[0093] Each of the first wedges 258 can be contacted by and positioned between the first projection 462a and the second projection 464a, thus preventing the first wedges 258 from sliding or being pulled out along the first wedge axes 442. The contact of the cam-shaped section 294 with the first wedges 258 allows the first projection 462a and the second projection 464a to be axially spread, enabling displacement of the first wedges 258. The first and second projections 462a, 464a can be adapted to the volume of the first wedges 258 and enclosed by them. Each of the second wedges 260 can be contacted by and positioned between the third projection 462b and the fourth projection 464b, thus preventing the second wedges 260 from sliding or being pulled out along the second wedge axes 444.The contact of the cam-shaped section 294 with the second wedges 260 allows the third projection 462b and the fourth projection 464b to spread, thus enabling displacement of the second wedges 260. The third and fourth projections 462b, 464b can be adapted to the volumes of the second wedges 260 and enclosed by them. Each of the third wedges 262 can be contacted by and positioned between the fifth projection 462c and the sixth projection 464c, thereby preventing the third wedges 262 from sliding along the third wedge axes 446 or being pulled out. The contact of the cam-shaped section 294 with the third wedges 262 allows the fifth projection 462c and the sixth projection 464c to spread, thus enabling displacement of the third wedges 262.

[0094] When the first projection 462a and the second projection 464a are attached to the first keys 258, they can reduce the self-locking of the first keys 258 on the first gear 214 or the first through holes 252. The third projection 462b and the fourth projection 464b can reduce the self-locking of the second keys 260 on the second gear 216 or on the second through holes 254, if they are adapted to the features of the second keys 260. The fifth projection 462c and the sixth projection 464c, if adapted to features of the third keys 262, can reduce the self-locking of the third keys 262 on the third gear 218 or the third through holes 256.

[0095] Each set of adjacent gears arranged along shaft 212 has an axial clearance of less than 10% of the end face width of the adjacent gears, specifically the gear with the smallest diameter. The axial clearance between adjacent gears is parallel to axis 210.

[0096] For example, there is a first axial clearance 472 between the first gear 214 and the second gear 216. Likewise, there is a second axial clearance 474 between the second gear 216 and the third gear 218. The first gear 214 has a first face width 482. The second gear 216 has a second face width 484. The third gear 218 has a third face width 486. The distance of the first axial clearance 472 can be less than 10% of the first face width 482 and the second face width 484. The distance of the second axial clearance 474 can be less than 10% of the second face width 484 and the third face width 486.

[0097] The dimensions of the distances between the gears 214, 216, 218, including the first axial play 472 and the second axial play 474, can be arranged with the keys and sleeves of the jaw coupling assembly 202 such that the keys are not simultaneously blocked by more than one gear of the gears 214, 216, 218 and / or other gears of the jaw coupling assembly 202. Furthermore, the dimensions of the distances between the keys, such as the distances between the first keys 258, the second keys 260 and the third keys 262, and the dimensions of the distances between the sleeves and the lengths of the sleeves, such as...The distances between the sleeves and the lengths of the first sleeve 274a, the second sleeve 276a, the third sleeve 274b, the fourth sleeve 276b, the fifth sleeve 274c, and the sixth sleeve 276c must be arranged such that the keys are not attached to more than one gear of the jaw coupling assembly 202 at the same time. The arrangement of the gears 214, 216, 218, the keys 258, 260, 262, and the sleeves 274a, 276a, 274b, 276b, 274c, 276c can prevent more than one gear from being coupled to the shaft 212 at the same time.

[0098] Fig. Figure 12 shows a twelfth view 1200 of the first gear 214. However, it is to be understood that the features of the arrangement with the second gear 216 and the third gear 218 have similar features that may be proportional to the features of the first gear 214.

[0099] The first gear 214 can have a first surface, which is an outer surface and is referred to here as outer surface 1222. The outer surface 1222 curves radially around the first gear 214. The outer surface is a pitch surface of the first gear 214.

[0100] The first gear 214 comprises an opening 932 and a second surface, which is an inner surface, here referred to as inner surface 934. The inner surface 934 curves radially around the opening 932. The first recesses 264 extend radially outward from the inner surface 934 into the material of the first gear 214. The inner surface 934 and the first recesses 264 define the shape and volume of the opening 932. The opening 932 and the inner surface 934 can be radially centered about the axis 210. The inner surface 934 has a partially cylindrical shape, with the plurality of first recesses 264 interrupting the cylindrical curvature of the inner surface 934.

[0101] The first gear 214 can also have a third surface 1224 and a fourth surface 1226, which are annular and perpendicular to the axis 210. The third surface 1224 can be flat and extend radially inwards from the outer surface 1222. The third surface 1224 can be adjacent to the outer surface 1222. The fourth surface 1226 can be flat and annular, with portions of the annular shape extending beyond the first recesses 264. The fourth surface 1226 can extend radially from the inner surface 934 and the first recesses 264. A groove 1232 is arranged radially between the third surface 1224 and the fourth surface 1226. The groove 1232 can curve radially around the fourth surface 1226 and the opening 932.

[0102] Fig. Figure 5A shows a fourth view 500 of the claw coupling arrangement 202. The fourth view 500 is a side and section view of the claw coupling arrangement 202. Fig. Figure 5A shows an area 504 enclosed by numerous dashed lines. Area 504 can also be viewed from a different perspective. The fourth view, 500, refers to area 410 of Fig. 4. Fig. Figure 5A shows the claw coupling arrangement 202, which is configured such that the rod 246 is in a first position. In the first position of Fig. 5A the cam-shaped section 294 is brought to a first point 506.

[0103] The fourth view 500 shows a plurality of points along the axis 210, including the first point 506, a second point 508, and a third point 510, to which the cam-shaped section 294 can be displaced. The first set of wedges 258 can be arranged radially around the first point 506, and the second set of wedges 260 can be arranged radially around the second point 508. The third point 510 is a neutral point located axially between the first point 506 and the second point 508, and approximately equidistant from them. The third point 510 can also be located axially between the first wedges 258 and the second wedges 260, and at approximately the same distance from them.

[0104] The cam-shaped section 294 can have sections with a first diameter 520 and a second diameter 522. The first diameter 520 is a minimum diameter and the second diameter 522 is a maximum diameter of the cam-shaped section 294. The first diameter 520 is below a first clearance threshold, so that the cam-shaped section 294 can be positioned radially inward from the first set of first keys 258, the second set of second keys 260, or the third set of third keys 262 without contact. The second diameter 522 is above a second clearance threshold, so that the cam-shaped section 294 contacts the first set of first keys 258, the second set of second keys 260, or the third set of third keys 262 and forces them to extend out of their respective through-holes on the shaft 212.The first set of first wedges 258, the second set of second wedges 260 or the third set of third wedges 262 are inserted into the recesses of the first gear 214, the second gear 216 or the third gear 218 respectively.

[0105] The first sleeve 274a and the second sleeve 276a can be separated by a first gap 512. The first wedges 258 can be arranged axially between the first sleeve 274a and the second sleeve 276a in the first gap 512. Likewise, the third sleeve 274b and the fourth sleeve 276b are separated by a second gap 514. The second wedges 260 can be arranged axially between the third sleeve 274b and the fourth sleeve 276b in the second gap 514. The fourth sleeve 276b and the fifth sleeve 274c can be separated by a third gap 516. Additionally, a fourth gap 518 can be present between the second gear 216 and each wedge of the second keys 260. More precisely, the fourth gap 518 is located between the second wedges 260 and the contact surfaces of the second recess 266. The first axial clearance 512, the second axial clearance 514 and the third axial clearance run parallel to the axis 210.The fourth clearance 518 is an axial clearance in a radial direction between the second splines 260 and the second gear 216. If the second splines 260 are moved radially inwards, the distance of the fourth clearance 518 increases.

[0106] The third sleeve 274b and the fourth sleeve 276b abut, bear against, and press upon the second wedges 260, thus locking the second wedges 260 toward the second recesses 266 and reducing the distance between them, without requiring any intentional force greater than a threshold for spreading the third sleeve 274b and the fourth sleeve 276b. Contact between the sliding wedges and the cam-shaped section 294 can generate a force greater than the first threshold to spread the sliding sleeves apart. For example, the contact between the cam-shaped section 294 and the first wedges 258 can spread apart the first sleeve 274a and the second sleeve 276a, or the contact between the cam-shaped section 294 and the second wedges 260 can spread apart the third sleeve 274b and the fourth sleeve 276b.

[0107] In the first position, the cam-shaped section 294 contacts the first wedges 258 and has spread apart the first sleeve 274a and the second sleeve 276a. By spreading apart the first sleeve 274a and the second sleeve 276a, the first gap 512 is enlarged.

[0108] In the first position, the cam-shaped section 294 is positioned such that a first part with the second diameter 522 is located at the first point 506 and is in contact with the first keys 258, thereby pushing the first keys 258 radially outward. Increasing the diameter of the cam-shaped section 294 at the first point 506 forces the first keys 258 to slide a further radially outward. Furthermore, increasing the diameter of the cam-shaped section 294 at the first point 506 forces the first sleeve 274a and the third sleeve 274b to slide further apart under the pressure of the first keys 258, thus enlarging the first gap 512. The second diameter 522 is the maximum diameter, and within it the first keys 258 can slide radially outward to be pulled out at a maximum radial distance from the shaft 212.The first wedges 258 are pressed into contact with the first recesses 264 and engage to selectively couple and lock the first gear 214 with the shaft 212. The contact surfaces of the first wedges 258 with the first recesses 264 engage the first gear 214, thereby selectively coupling the first gear 214 with the shaft 212. Due to the contact, there is no or negligible play between the first wedges 258 and the first gear 214. Furthermore, the first gap 512 is expanded to a maximum distance because the second diameter 522 intersects the first point 506, and the first wedges 258 are pulled out to a maximum distance from the axis 210 while pressing against the first sleeve 274a and the second sleeve 276a.

[0109] An axial clearance between two sliding sleeves of a set is a distance dimensioned such that, when one set of sliding wedges is extended between the two sliding sleeves, the axial clearance and at least one sliding sleeve of the same set prevent the extension of other sets of sliding wedges between other sets of sliding sleeves. The axial clearance between two sliding sleeves can thus constitute a locking mechanism for the jaw coupling arrangement 202, preventing more than one set of wedges from being withdrawn from the shaft 212. The contact between the sleeves prevents the wedges from moving radially outward beyond a certain value at a minimum axial clearance.

[0110] In the first position of Fig. For example, in 5A the first gap 512 is enlarged so that the second sleeve 276a rests against the third sleeve 274b. The second sleeve 276a and the second spring 282, which rest against and press against the third sleeve 274b, reduce the axial displacement of the third sleeve 274b away from the second wedges 260. The third spring 284, which rests against and presses against the fourth sleeve 276b, and the lack of contact between the cam-shaped section 294 and the second wedges 260, reduce the axial displacement of the fourth sleeve 276b away from the second wedges 260. The second gap 514 can be located at a minimum distance within it, and the third sleeve 274b and the fourth sleeve 276b can prevent radial outward displacement and self-extension of the second wedges 260. Likewise, the third distance 516 can be a maximum, so that the fifth sleeve 274c rests against the third wedges 262.By applying and pressing the third spring 284 against the fifth sleeve 274c and the lack of contact between the cam-shaped section 294 and the third wedges 262, the displacement of the fifth sleeve 274c in an axial direction away from the third wedges 262 is reduced.

[0111] It is understood that the rod 246 can be configured to be positioned in various axial positions, in which the cam-shaped section 294 can be radially inward from another gear and in contact with other sets of keys. In a first alternative position, for example, the cam-shaped section 294 can be positioned radially inward from and in contact with the second keys 260, thereby pushing the second keys 260 radially outward. The second keys 260 can be pressed into contact with the second recesses 266 to selectively engage and lock the second gear 216 with the shaft 212. In such arrangements, the third sleeve 274b and the second spring 282 bear against the second sleeve 276a, thereby reducing the axial displacement of the second sleeve 276a away from the first keys 258.The first sleeve 274a and the second sleeve 276a can prevent radial outward displacement and self-removal of the first wedges 258. Likewise, the third sleeve 274b and the fourth sleeve 276b, as well as the third spring 284, can bear against the fifth sleeve 274c and reduce the axial displacement of the fifth sleeve 274c away from the third wedges 262. The fifth sleeve 274c and the sixth sleeve 276c can prevent radial outward displacement and self-removal of the third wedges 262.

[0112] In a second alternative position, the cam-shaped section 294 can be positioned radially inward and in contact with the third keys 262, thereby pressing the third keys 262 radially outward. The third keys 262 can be pressed into contact with the third recesses 268 to selectively engage and lock the third gear 218 with the shaft 212. In such arrangements, the fifth sleeve 274c and the third spring 284 can bear against the fourth sleeve 276b and reduce the axial displacement of the fourth sleeve 276b away from the second keys 260. The third sleeve 274b and the fourth sleeve 276b can prevent radial outward displacement and self-disengagement of the second keys 260.

[0113] Fig. Figure 5B shows the fourth view 500 of the claw coupling arrangement 202. Fig. Figure 5B shows that the claw coupling arrangement 202 can be configured such that the rod 246 is in a second position. In the second position, the cam-shaped section 294 is, compared to the first position, Fig. 5A is shifted away from the first point 506. In the second position, the first part of the cam-shaped section 294 with the second diameter 522 is located at a point along the axis 210 between the first point 506 and the third point 510.

[0114] In the second position, a second part of the cam-shaped section 294 remains radially inward of and in contact with the first wedges 258. This second part has a diameter corresponding to an intermediate diameter 546. The intermediate diameter 546 is smaller than the second diameter 522 and larger than the first diameter 520. The reduced diameter of the cam-shaped section 294 and the compression of the first sleeve 274a and the second sleeve 276a can force the first wedges 258 to move radially inward toward the axis 210. In the second position, the first wedges 258 are, compared to the first position, Fig. 5A radially shifted inwards.

[0115] Reducing the diameter of a portion of the cam-shaped section 294 that contacts the first wedges 258 allows the first sleeve 274a to be displaced axially away from the first hard stop 270. Similarly, the second sleeve 276a can be displaced axially away from the third sleeve 274b. Displacing the first sleeve 274a and the second sleeve 276a toward the first point 506 reduces the distance of the first gap 512.

[0116] A fifth clearance 534 can be created between the first sleeve 274a and the first hard stop 270. The fifth clearance 534 increases the further the first sleeve 274a is from the first hard stop 270. A sixth clearance 536 can be created between the second sleeve 276a and the third sleeve 274b. The sixth clearance 536 increases the further the second sleeve 276a is from the third sleeve 274b. The fifth clearance 534 and the sixth clearance 536 are axial clearances that can run parallel to the axis 210.

[0117] By displacing the first wedges 258 radially inwards, a seventh clearance 538 can be created between the first gear 214 and each wedge of the first wedges 258. More precisely, the seventh clearance 538 is located radially between the first wedges 258 and one or more contact surfaces of the first recess 264. The seventh clearance 538 is an axial clearance in a radial direction between the first wedges 258 and the first gear 214. When the first wedges 258 are displaced radially inwards, the seventh clearance 538 increases. In the second position, the seventh clearance 538 is smaller than the fourth clearance 518.

[0118] It is understood that the keys, such as the first key 258, the second key 260, and the third key 262, cannot be retracted during the transmission of torque to the shaft 212 and the rotation of the shaft 212. As the transmission of torque to the shaft 212 and the rotation of the shaft 212 continue, a set of sliding keys, which selectively couple a gear to the shaft 212, remains engaged with their respective gear recesses even after the cam-shaped section 294 has been removed from a meshing position with the keys. Likewise, each of the locked sleeves abuts adjacent sleeves of other sets, thus reducing the formation of a gap between them. For example, if the shaft 212 were rotating and the rod 246 were in the second position, the first keys 258 would remain extended, and no seventh gap 538 would form.Likewise, the first sleeve 274a can abut the first hard stop 270, thereby reducing the formation of the fifth gap 534. Furthermore, the second sleeve 276a can abut the third sleeve 274b, thereby reducing the formation of the sixth gap 536.

[0119] This interlock mechanically locks an adjacent set of keys, preventing the cam-shaped section 294, which forces the adjacent keys to the locked keys, from moving radially outward upon contact. The interlock also prevents the rod 246 from engaging the next gear or any other gear. In such cases, an interlocked sleeve, between which the interlocked keys are arranged, restricts the movement of the rod 246 along the axis 210 and prevents contact with the adjacent set of keys.

[0120] Fig. 5C shows the fourth view 500 of arrangement 202. Fig. Figure 5C shows that the arrangement 202 can be configured such that the rod 246 is in a third position. In the third position, the cam-shaped section 294 is, compared to the second position, Fig. 5B is displaced further away from the first point 506 in the axial direction. In the third position, the first part of the cam-shaped section 294 with the second diameter 522 is located at the third point 510, and the cam-shaped section 294 is in a neutral position without contact with the first wedges 258, the second wedges 260, and the third wedges 262.

[0121] The first wedges 258 and the second wedges 260 can be separated by a distance 542. The distance 542 is an axial distance parallel to the axis 210. Furthermore, the cam-shaped section 294 has a length of 552. If the rod 246 is parallel or coaxial to the axis 210, the length 552 can run parallel to the axis 210. The length 552 is dimensioned such that the cam-shaped section 294 has no common surface contact with the first wedges 258 or the second wedges 260. In a first example, the distance 542 is greater than the length 552.

[0122] In the third position, the cam-shaped section 294 is completely out of contact with the first wedges 258, allowing the first wedges 258 to be retracted. The first sleeve 274a and the second sleeve 276a can press against the first wedges 258 and reduce their radial outward displacement. The first sleeve 274a and the second sleeve 276a bear against and press against the first wedges 258, thereby blocking and reducing the expansion of the first wedges 258 toward the first recesses 264 without requiring any intentional force greater than the threshold for the expansion of the first sleeve 274a and the second sleeve 276a. The first wedges 258 prevent the first sleeve 274a and the second sleeve 276a from approaching the first point 506 in the axial direction. The initial distance of 512 can be reduced to a minimum distance at the third position.The first distance 512 and the second distance 514 can be approximately the same distance apart at the third position.

[0123] The first sleeve 274a can be located further axially from the first hard stop 270 compared to the second position, e.g., at a maximum distance from the first hard stop 270. The fifth distance 534 can be increased compared to the second position, e.g., to a maximum distance. Likewise, the second sleeve 276a can be located axially further from the third sleeve 274b than when the rod is in the second position, for example, by a first maximum distance from the fourth sleeve 276b. The sixth distance 536 can be increased, e.g., to a second maximum distance. The fifth distance 534 and the sixth distance 536 can be approximately equidistant from each other.

[0124] It is understood that the cam-shaped section 294 can also be in neutral positions other than the third position of Fig. 5C can be positioned. The other neutral positions are located between other sets of wedge sets, e.g., a neutral position between the second wedges 260 and the third wedges 262. The other neutral positions have a point along the axis 210 that is equidistant from two sets of wedge sets on opposite sides of the neutral position. The first section of the cam-shaped section 294 with the second diameter 522 can be moved to this point, so that the cam-shaped section 294 is located in the other neutral position between the wedge sets. When moved to the other neutral position, the cam-shaped section 294 does not come into contact with either set.

[0125] Fig. 5D shows the fourth view 500 of the claw coupling arrangement 202. Fig. Figure 5D shows that the claw coupling arrangement 202 can be configured such that the rod 246 is in a fourth position. In the fourth position, the cam-shaped section 294 is displaced further axially away from the first point 506 and towards the second point 508 than if the rod 246 were in the third position. Fig. 5C is located. In the fourth position, the first section of the cam-shaped section 294 with the second diameter 522 is located axially between the second point 508 and the third point 510, and the cam-shaped section 294 touches the second wedges 260. Fig. 5D shows an area 562 enclosed by numerous dashed lines. Another view of area 562 is also possible.

[0126] In the fourth position, the cam-shaped section 294 is positioned such that a third part of the cam-shaped section 294, forming the first diameter 520, is located at the second point 508. This third part of the cam-shaped section 294 is radially inside the second wedges 260 but does not touch them. A fourth part of the cam-shaped section 294 may touch the second wedges 260 at a point axially between the second point 508 and the third point 510. This fourth part has a second intermediate diameter 572, which is smaller than the second diameter 522 and larger than the first diameter 520.

[0127] The contact between the cam-shaped section 294 and the second wedges 260 exerts pressure, forcing the second wedges 260 to move radially outward. As the diameter of the cam-shaped section 294, which is in contact with the second wedges 260, increases, the second wedges 260 can be forced by the cam-shaped section 294 to move further in a radially outward direction. The second wedges 260 can then press against the third sleeve 274b and the fourth sleeve 276b, spreading them apart. By expanding the third sleeve 274b and the fourth sleeve 276b, the second gap 514 increases compared to the third position of the rod 246. The second gap 514 can be larger than the first gap 512. The third sleeve 274b can be displaced axially towards the second sleeve 276a, thereby reducing the size of the sixth gap 536 compared to the third position of the rod 246.The fourth sleeve 276b can be displaced axially towards the fifth sleeve 274c, thereby reducing the size of the third gap 516 compared to the third position of the rod 246. The second wedges 260 can be displaced radially outwards, thereby making the fourth gap 518 smaller than the seventh gap 538.

[0128] In the fourth position, the first space 512 and the fifth space 534 can remain unchanged in size if the rod 246 is in the third position.

[0129] It is understood that the keys, such as the first key 258, the second key 260, and the third key 262, cannot be retracted during the transmission of torque to the shaft 212 and the rotation of the shaft 212. When the transmission of torque to the shaft 212 and the rotation of the shaft 212 continue, a set of sliding keys, which selectively couple a gear to the shaft 212, remains engaged with their respective gear recesses even after the cam-shaped section 294 has been removed from a meshing position with the keys. Likewise, each of the locked sleeves abuts adjacent sleeves of other sets, thus reducing the formation of a gap between them. Furthermore, the lack of gaps prevents the adjacent sleeves from being forced apart by compression.The lack of clearance between adjacent sleeves and the sleeves of the splines locked to the gear reduces the radial outward movement of the adjacent splines toward the locked splines upon contact with the cam-shaped section. Furthermore, the forward movement of the rod is hindered by the sleeve that is locked by another sleeve of the locked splines and by the adjacent splines. For example, if the shaft 212 were to rotate and the rod 246 were to contact the second splines 260, the first splines 258 would remain extended, and no seventh gap 538 would form. Similarly, the first sleeve 274a can rest against the first hard stop 270, thus reducing the formation of the fifth gap 534. Additionally, the second sleeve 276a can rest against the third sleeve 274b, thus reducing the formation of the sixth gap 536.The contact of the second sleeve 276a with the third sleeve 274b can reduce the axial expansion of the third sleeve 274b away from the second wedges 260, thereby blocking the third sleeve 274b. By reducing the displacement of the third sleeve 274b, the radial outward sliding of the second wedges 260 within it is reduced. Upon contact with the second wedges 260, the second wedges 260 and the third sleeve 274b within them can impede the axial movement of the rod 246 along the axis 210. In this example, the second wedges 260 and the third sleeve 274b can impede the forward movement of the rod 246 in the axial direction toward the first side 204. The rod 246 can be prevented from moving into the fourth position by contact with the second wedges 260. Fig. to move in 5D.

[0130] Of course, the rod 246 can also be moved into a fifth position. In the fifth position, the cam-shaped section 294 is positioned such that the first part with the second diameter 522 is located at the second point 508 and is in contact with the first keys 258, thereby pushing the second keys 260 radially outward. The increase in the diameter of the cam-shaped section 294 at the second point 508 forces the second keys 260 to slide a little further radially outward. Furthermore, the increase in the diameter of the cam-shaped section 294 at the second point 508 forces the third sleeve 274b and the fourth sleeve 276b to slide further apart due to the pressure of the second keys 260, thus increasing the second gap 514. The second keys 260 can slide radially outward to be pulled out at a maximum radial distance from the shaft 212.The second wedges 260 are pressed into contact with the second recesses 266. The contact of the second wedges 260 with the contact surfaces of the second recesses 266 causes engagement with the second gear 216, thereby selectively coupling the second gear 216 with the shaft 212. Due to the contact, the fourth clearance 518 between the second wedges 260 and the second gear 216 is either non-existent or negligibly small. Furthermore, the second clearance 514 is increased to a maximum distance because the second wedges 260 are pulled out to a maximum distance from the axis 210 while pressing against the third sleeve 274b and the fourth sleeve 276b.

[0131] Fig. Figure 6 shows a fifth view 600 of the jaw coupling assembly 202. The fifth view 600 is a side view and a section of the jaw coupling assembly 202. The fifth view 600 shows the jaw coupling assembly 202 configured such that the rod 246 is in the first position of Fig. 5A is located where the cam-shaped section 294 contacts the first wedges 258 via the second part of the cam-shaped section 294 with the second diameter 522. The fifth view 600 refers to the area 504 in Fig. 5A.

[0132] Each of the wedges 258, 260, 262 can have a head and a base. The heads of the wedges 258, 260, 262 can have a prismatic shape. The bases of the wedges 258, 260, 262 can be smooth and rounded, with a frustoconical section and a cylindrical section. The frustoconical section is a portion of a structure with a frustoconical volume and outer surface. The cylindrical section is a slice of a structure with a cylindrical volume and outer surface area. For example, each of the bases closer to the head of the respective wedge that encompasses the base can be frustoconical. The base and head of a wedge are connected and physically coupled. Each of the wedges can have recesses, such as... B. notches for the cam-shaped component of the cam-shaped section 294 and features of one or more of the sleeves 274a, 276a, 274b, 276b, 274c and 276c to fit and conform to it.Furthermore, the bases of the wedges can be dovetail-shaped roots.

[0133] For example, each of the first wedges 258 can have a first head 632a and a first base 634a. Likewise, each of the second wedges 260 can have a second head 632b and a second base 634b. The first head 632a and the second head 632b can be symmetrical. Likewise, the first base 634a and the second base 634b can be symmetrical. For example, the first head 632a of each of the first wedges 258 can be moved into a recess of the first recesses 264 to engage with the first gear 214.

[0134] Each of the first wedges 258 can have a first notch 642a and each of the second wedges 260 can have a second notch 642b. The first and second notches 642a, 642b can penetrate into the first base 634a and the second base 634b, respectively, and curve towards the first head 632a and the second head 632b, respectively.

[0135] Each of the first wedges 258 can have a third notch 644a and a fourth notch 646a. The third and fourth notches 644a and 646a can be pressed into the first base 634a and toward the first head 632a. The third notch 644a and the fourth notch 646a are located between the first head 632a and the first base 634a of each of the first wedges 258. Sleeves such as the first sleeve 274a and the second sleeve 276a can be fitted into the third notch 644a and the fourth notch 646a, respectively, so that the surfaces of the sleeves 274a and 276a are enclosed and contacted by the surfaces of the first head 632a and the first base 634a around the third notch 644a and the fourth notch 646a. More precisely, the first projection 462a can be fitted into the third notch 644a and the second projection 464a into the fourth notch 646a, so that the second head 632b and the second base 634b enclose and touch the third projection 462b and the fourth projection 464b.When the first sleeve 274a and the second sleeve 276a interlock and touch, they can lock each of the first wedges 258 and reduce the displacement along the first wedge axes 442. The third notch 644a and the fourth notch 646a give the first base 634a a dovetail shape, with two symmetrical inclined planes on opposite sides of the first base 634a, each inclined plane accommodating the volume of the third notch 644a or the fourth notch 646a.

[0136] Each of the first wedges 258 can have a fifth notch 644b and a sixth notch 646b. The fifth notch 644b and the sixth notch 646b are located between the second head 632b and the second base 634b of each of the second wedges 260. The fifth and sixth notches 644b, 646b can press into the second base 634b and toward the second head 632b. Sleeves such as the third sleeve 274b and the fourth sleeve 276b can be fitted into the fifth notch 644b and the sixth notch 646b, respectively, so that the surfaces of the sleeves 274b, 276b are enclosed and contacted by the surfaces of the second head 632b and the second base 634b around the fifth notch 644b and the sixth notch 646b. More precisely, the third lead 462b can be fitted into the fifth notch 644b and the fourth lead 464b into the sixth notch 646b, so that the second head 632b and the second base 634b enclose and touch the third lead 462b and the fourth lead 464b.When the first sleeve 274a and the second sleeve 276a interlock and touch, they can lock each of the second wedges 260 and reduce the displacement along the second wedge axes 444. The fifth notch 644b and the sixth notch 646b give the second base 634b a dovetail shape, with two symmetrical inclined planes on opposite sides of the second base 634b, each inclined plane enclosing the volume of the fifth notch 644b or the sixth notch 646b.

[0137] The notches of the individual wedges, including notches 644a, 646a, 644b, and 646b, may each have inclined surfaces extending at an angle 662. A projection, such as projections 462a, 464a, 462b, and / or 464b, may slide into or out of the notches 644a, 646a, 644b, and / or 646b along the surfaces extending at an angle 662. The notches of the individual wedges, including notches 644a, 646a, 644b, and 646b, may extend axially into the respective wedges over a distance 664. The distance 664 may be approximately the same length as the sixth gap 536 in the fully expanded state or any other distance between two adjacent sleeves of separate pairs that are not crimped.

[0138] Fig. Figure 7A shows a sixth view 700 of the claw coupling assembly 202. The sixth view 700 is a side view and a section of the claw coupling assembly 202. The sixth view 700 shows the claw coupling assembly 202 configured such that the rod 246 is in the fourth position of Fig. 5D is located in which the cam-shaped section 294 contacts the second wedges 260 via the second part of the cam-shaped section 294 of the second diameter 522. The fifth view 600 is applied to the area 562 of Fig. Shot in 5D.

[0139] The third sleeve 274b comprises a first surface 730, which is perpendicular to the axis 210. The first surface 730 can be annular in shape and area and extends radially from the third opening 452b. The first surface 730 adjoins a surface of the third opening 452b, which curves radially around the axis 210. The third projection 462b can have a first rounded surface 732. The first rounded surface 732 can be connected to and merge into a second, partially frustoconical surface 734 and a third, partially cylindrical surface 735. The second surface 734 can be located radially around the axis 210 and point radially inward from the third projection 462b. The second surface 734 can adjoin the surface of the third opening 452b. The third surface 735 can curve radially around the axis 210 and point radially outwards from the third projection 462b.The third surface 735 can be connected to and adjacent to a fourth surface 736 via a first rounded section 737. The fourth surface 736 can have an annular shape and area extending radially outwards from the first groove 737. The fourth surface 736 can be connected to and adjacent to a fifth surface 738 via a first chamfered edge 739. The fifth surface 738 can have a cylindrical shape and area that curves radially around the axis 210 and points radially outwards from the third sleeve 274b.

[0140] The fourth sleeve 276b comprises a sixth surface 740, which is perpendicular to the axis 210. The sixth surface 740 can be annular in shape and area and extends radially from the fourth opening 454b. The sixth surface 740 adjoins a surface of the fourth opening 454b, which curves radially around the axis 210. The fourth projection 464b can have a second rounded surface 742. The second rounded surface 742 can be connected to and merge into a seventh, partially frustoconical surface 744 and an eighth, partially cylindrical surface 745. The seventh surface 744 can extend radially around the axis 210 and point radially inward from the fourth projection 464b. The seventh surface 744 can adjoin the surface of the fourth opening 454b. The eighth surface 745 can curve radially around the axis 210 and point radially outwards from the fourth projection 464b.The eighth surface 745 can be connected to and adjacent to a ninth surface 746 via a second fillet 747. The ninth surface 746 can have an annular shape and surface extending radially outwards from the second fillet 747. The ninth surface 746 can be connected to and adjacent to a tenth surface 748 via a second chamfered edge 749. The tenth surface 748 can have a cylindrical shape and surface that curves radially around the axis 210 and points radially outwards from the fourth sleeve 276b.

[0141] The fifth surface 738 and the tenth surface 748 can be smooth and have a low coefficient of friction. The fifth surface 738 and the tenth surface 748 can share a common surface that is in contact with an inner surface of the shaft 212, wherein the fifth surface 738 and the tenth surface 748 can slide in axial directions while in contact with the inner surface.

[0142] Fig. Figure 11 shows an eleventh view 1100 of a wedge 1102. In the eleventh view 1100, the wedge 1102 is separated from other components and features of the jaw coupling arrangement 202. Fig. 2-5D representation.

[0143] The wedge 1102 can comprise a head 632, a base 634, a first notch 642, a second notch 644, and a third notch 646. The wedge 1102 can be a wedge of the first wedges 258, the second wedges 260, the third wedges 262, and / or another set of wedges of the present disclosure. The head 632 can be the first head 632a and / or the second head 632b of Fig. 6. Likewise, base 634 can replace the first base 634a and / or the second base 634b of Fig. 6. The first notch 642 can be the first notch 642a or the second notch 642b of Fig. 6. The second notch 644 can be the third notch 644a or the fifth notch 644b of Fig. 6. The third notch 646 can be the fourth notch 646a or the sixth notch 646b of Fig. 6.

[0144] The base 634 has a first wedge surface 1116 and a second wedge surface 1118. The first wedge surface 1116 and the second wedge surface 1118 can be connected to and merge into a third wedge surface 1119 that encloses the first notch 642. The first wedge surface 1116 and the second wedge surface 1118 can have a convex shape, curving both outwards away from the first notch 642 and inwards towards it. Likewise, the first wedge surface 1116 and the second wedge surface 1118 can be curved radially inwards, e.g., radially inwards in the direction of the axis 210. Fig. 2-6 and Fig. 9-10. The first wedge surface 1116, the second wedge surface 1118 and / or the third wedge surface 1119 can be connected to the cam-shaped section 294 of the Fig. 2-7A have a common surface.

[0145] The base 634 can include a fourth wedge surface 1120 and a fifth wedge surface 1122, each inclined at an angle 662 from the second notch 644 and the third notch 646, respectively. The fourth wedge surface 1120 and the fifth wedge surface 1122 can form the first and second inclined planes of the base 634. The fourth wedge surface 1120 can be a first inclined surface against which a sleeve rests and slides, and the fifth wedge surface 1122 can be a second inclined surface against which another sleeve rests and slides. The fourth wedge surface 1120 and the fifth wedge surface 1122 extend from the base 634 to the head 632. The fourth wedge surface 1120 and the fifth wedge surface 1122 can be connected to and adjacent to the head 632. The fourth wedge face 1120 and the fifth wedge face 1122 can be located on opposite sides of the base 634.The fourth wedge surface 1120 and the fifth wedge surface 1122 can be arranged symmetrically and as mirror images on opposite sides of the base 634. The fourth wedge surface 1120 can be located around and enclosing the second notch 644. The fifth wedge surface 1122 can be located around and enclosing the third notch 646.

[0146] The head 632 can have a sixth wedge surface 1124 and a seventh wedge surface 1126, which can be located on opposite sides of the head 632. The sixth and seventh wedge surfaces 1124 and 1126 can be flat. The head 632 can have an eighth wedge surface 1128. The eighth wedge surface 1128 is an upper surface of the head 632, which is connected to surfaces of a recess, such as the first recesses 264, the second recesses 266, and the third recesses 268 of the Fig. 2-5D, can come into contact, lie against and lock.

[0147] The fourth wedge surface 1120 and the fifth wedge surface 1122 can have curvatures with multiple inflection points. For example, the fourth wedge surface 1120 can be connected to and adjacent with the sixth wedge surface 1124 via a first chamfered edge 1142. The fourth wedge surface 1120 can curve upwards towards the first chamfered edge 1142 via a first curve 1132 and adjacent with it. Similarly, the fifth wedge surface 1122 can be connected to and adjacent with the seventh wedge surface 1126 via a second chamfered edge 1144. The fifth wedge surface 1122 can curve upwards towards the second chamfered edge 1144 and adjacent with it via a second curve 1134.

[0148] The eighth wedge surface 1128 can be connected to and adjacent to a third chamfered edge 1146. The third chamfered edge 1146 can extend at an angle from and be connected to a side surface, as in the case of the Fig. 9 shown side surface 972 in the direction of the eighth wedge surface 1128.

[0149] Back to Fig. 7A: The third projection 462b can slide in and out of the fifth notch 644b while touching the fourth wedge face 1120. More precisely, the second face 734 can touch the fourth wedge face 1120. The first curve 1132 can enclose and abut the third projection 462b. The third face 735 can touch and abut the first curve 1132. The fourth face 736 and the first fillet 737 can touch and abut the sixth wedge face 1124 and the first chamfered edge 1142, respectively. Likewise, the fourth projection 464b can slide in and out of the sixth notch 646b while touching the fourth wedge face 1120. More precisely, the seventh face 744 can touch the fifth wedge face 1122. The second curve 1134 can enclose and abut the fourth projection 464b. The eighth surface 745 can touch and abut the second curve 1134.The ninth surface 746 and the second rounding 747 can touch and abut the seventh wedge surface 1126 and the second chamfered edge 1144, respectively.

[0150] Fig. Figure 7B shows the sixth view 700 of the claw coupling arrangement 202 with a multitude of force vectors, which are schematically represented as arrows.

[0151] A hydraulic force of 760 can be applied to the rod of 246. Fig. 2-6 are exerted and move these forward, thereby bringing the cam-shaped section 294 into contact with one or more surfaces of the second wedges 260. For example, the cam-shaped section 294 can contact the first wedge surface 1116. The hydraulic force 760 is an axial force. The hydraulic force 760 can be transmitted to and exert a pressure on other components or features that come into contact with the rod 246. The hydraulic force exerted on the rod results in a force that is perpendicular to the surfaces of the wedges of the jaw coupling assembly 202. When the cam-shaped section 294 is in contact with one or more wedges of a set of wedges, the hydraulic force 760 can be transmitted to the wedges of the jaw coupling assembly 202. The hydraulic force 760 can, for example, be transmitted via the cam-shaped section 294 to the second wedges 260.Due to the geometry of the surfaces involved, the hydraulic force 760 can be decomposed into an axial and a radial component, which are represented as the axial force component 762 and the radial force component 764 of the cams, respectively. Additionally, each set of sleeves and their respective springs can exert an axial force component and a radial force component on the wedges arranged between them. For example, the second spring 282 can exert a first axial force component 766 and a first radial force component 768 on one or more of the second wedges 260 via the contact between the second wedges 260 and the third sleeve 274b. In this or another example, the third spring 284 can exert a second axial force component 770 and a second sleeve radial force component 772 on one or more of the second wedges 260 via the contact between the second wedges 260 and the fourth sleeve 276b.Additionally, forces act on the wedges of the jaw coupling assembly 202, e.g., an axial force component 774 and a radial force component 776 of the wedge. The axial force component 774 of the wedge can arise from the contact of one or more wedges of the jaw coupling assembly 202 with the shaft 212, e.g., through frictional force. Likewise, the radial force component 776 of the wedge can originate from external forces such as gravity and the contact of one or more wedges of the jaw coupling assembly 202 and the shaft 212. The wedges of the jaw coupling assembly 202 can contact the shaft 212 at their respective through-holes. For example, the second set of wedges 260 can contact the shaft 212 at the second set of through-holes 254.

[0152] The axial force component of the cam 762 is sufficiently strong to overcome the axial component of the spring forces and move the sleeves. As the distance between the sleeves on both sides of the gear increases, the intervening keys are unlocked, allowing radial displacement of the unlocked keys. Likewise, the cam radial force component 764 is sufficiently robust to overcome the radial force components acting on the keys, such as the spring forces, gravity, and the force from contact between the keys and the shaft 212. The cam-shaped section 294 within it displaces the keys radially outward upon contact. For example, the axial force component of the cam 762 can be greater than the axial force component of the first sleeve 766 and the axial force component of the second sleeve 770, thereby spreading the third sleeve 274b from the fourth sleeve 276b, the first gap 512 of the Fig. 5A-5D is increased and the second spring 282 and the third spring 284 are compressed. Likewise, the cam radial force component 764 can be greater than the first sleeve radial force component 768, the second sleeve radial force component 772 and the wedge radial force component 776, thereby moving the second wedges 260 in a radially outward direction.

[0153] Each of the wedges, e.g., the second wedge 260, can be freely rotatable, as indicated by a curved arrow 778. In other words, each of the wedges can rotate or pivot about a center point or axis concentric to the curved arrow 778, e.g., when it is touched. The rotation can be in a range of one or several tens of degrees of a full 360 degrees. The rotation or other free movement of the wedges from contact with the cam-shaped section 294 can cause one or more wedges to bear against and engage surfaces surrounding the slot or other through-hole of the shaft 212, such as the second through-holes 254. The rotation of the wedges can concentrate the contact and force on specific areas and surfaces of the shaft's through-holes, e.g., on the surfaces of the second through-holes 254. The contact and forces, such asThe axial wedge force component 774 and a radial wedge force component 776 between the surfaces of the through holes and one or more wedges can cause self-locking, in which one or more wedges remain stuck in their slots. To prevent self-locking of the wedges by rotation, the wedges of the jaw coupling assembly 202 can have a width 782 that is no more than three times the thickness 784 of the shaft 212. For example, each of the second wedges 260 has a width 782 or a smaller width at intervals. The first wedges 258 and the third wedges 262 also each have a width 782 or a smaller width at intervals. In addition, a lever arm 786 of the cam-shaped section 294 can be less than three times the thickness of the shaft 784.

[0154] Fig. Figure 9 shows an eighth view 900 of a section of the jaw coupling assembly 202, more precisely the shaft 212, the first gear 214 and the first splines 258. The eighth view 900 is a perspective and section view of the jaw coupling assembly 202.

[0155] Each gear of the jaw coupling assembly 202 has an opening, and an inner surface of the gear can rotate radially. The shaft 212 can be concentric with the opening. Likewise, the recesses of the gear can extend radially outward from the inner surface into the gear material.

[0156] The shaft 212 can be concentric with the opening 932. The inner surface 934 curves radially around the opening 932 and defines its shape. The first recesses 264 extend radially outward from the inner surface 934 into the material of the first gear 214. The first recesses 264 can have rectangular areas that accommodate the first keys 258.

[0157] The shaft 212 can have an outer surface 936 and an inner surface 938. The inner surface 938 can have a cylindrical shape and area. The through holes of the shaft 212 can extend radially from the inner surface 938 to the outer surface 936. For example, the first through holes 252 can extend from the inner surface 938 to the outer surface 936.

[0158] Each of the first wedges 258 has a side surface 972. The side surface 972 can slide and contact the surfaces of the shaft 212, which form the shape of the first through holes 252. The first wedges 258 are partially inserted into the first recesses 264, but are not connected to the first recesses 264.

[0159] Fig. Figure 10 shows the ninth view 1000 of a section of the jaw coupling assembly 202, specifically the shaft 212, the first gear 214, the rod 246, and the first key 258. The eighth view 900 is a front and sectional view of the jaw coupling assembly 202, perpendicular to the axis 210. The first keys 258 are partially inserted into and connected to the first recesses 264. In the ninth view, the first gear 214 can be selectively coupled to the shaft 212 via the first keys 258.

[0160] The jaw coupling arrangement 202 can have eight keys per set of keys, eight through holes per set of holes, and eight recesses per gear. For example, the shaft 212 can have eight of the first keys 258 and eight of the first through holes 252, and the first gear 214 can have eight of the first recesses 264.

[0161] In this way, a jaw coupling arrangement within the meaning of the present disclosure is presented. The jaw coupling arrangement can selectively couple several gears to a shaft, whereby the selective coupling of two or more of the three gears to the shaft is reduced. There can be three gears that can be selectively coupled to the shaft. The shaft accommodates several sets of multiple splines over several sets of multiple slots. There can be three sets of splines and three sets of slots. A rod with a cam-shaped section is also located in the shaft. The cam-shaped section can contact a set of splines and displace radially outward to engage with a specific gear of the three gears. The cam-shaped section is configured to reduce contact with more than one set of splines simultaneously.

[0162] A first method for shifting gears via a jaw coupling arrangement of the present disclosure, e.g. the jaw coupling arrangement 202, can be described by reference to the Fig. 5A-5D will be illustrated.

[0163] The first method may involve increasing the hydraulic pressure on a hydraulic cylinder driven by a shaft, such as shaft 212 of the Fig. 2-5D, is formed. The hydraulic pressure can be increased on one side of a piston of the hydraulic cylinder, which is rigidly coupled to a rod, to a value above the first pressure threshold, the rod being rigidly coupled or comprising a cam or cam-shaped section. The rod could be, for example, rod 246 and the piston could be piston 292 of Fig. Act 2-5D. The hydraulic pressure can be increased between the piston 292 and the second side 206, thereby moving the piston towards the first side 204.

[0164] After the hydraulic pressure has been increased above a first pressure threshold, the process continues the displacement of a cam-shaped section of a rod toward a first point along a central axis, with a plurality of wedges arranged radially around the first point. During the displacement, the rod is moved in a direction away from the hydraulic cylinder. The wedges are arranged axially between a first and a second sleeve.

[0165] It goes without saying that in the first method, a different type of actuation system than a hydraulic actuator can be used to move the rod. In other examples, the rod can be moved by a purely electric or electrohydraulic actuation. In other words, instead of a hydraulic pressure cylinder or other hydraulic actuation system, the rod can be moved by a purely electric or electrohydraulic actuation system, where the actuation system includes an electric machine to actuate the rod. In these examples, the electric machine can be an electric motor.

[0166] For example, the rod can be the rod 246, the cam-shaped section can be the cam-shaped section 294, the multitude of wedges can be the first wedges 258, and the first point can be the second point 508 of the Fig. 5A-5B. Likewise, the first sleeve and the second sleeve can be the third sleeve 274b or the fourth sleeve 276b of the Fig. 5A-5B. The gear to be switched via the claw coupling arrangement can be the second gear 216.

[0167] The steps of the first procedure can differ depending on whether the cam-shaped section is driven from a neutral position or from a position in which the cam-shaped section has optionally coupled another gear, referred to here as the other gear, to the shaft. In the neutral position, the cam-shaped section can be retracted so that it does not contact any of the keys of any set of the jaw coupling assembly. Starting from a neutral position, the rod can be located at a third point between the first and a second point. The second point is a point along the axis where another set of keys, referred to here as the other keys, is radially arranged. For example, when starting from the neutral position, the rod can be located at the third point of Fig. 5C. If the other gear is optionally coupled to the shaft, the rod comes into contact with the other keys, so that the locking with the other gear occurs via the other keys. Another example is that the rod is in the first position of Fig. 5A is located when it is locked to the other gear via the other wedges. In these and other examples, the second point can be the first point 506 and the third point the third point 510 of Fig. 5A-5D. The other wedges can be the first wedges 258, and the other gear can be the first gear 214.

[0168] Assuming that the other gear is locked with the other splines, the other gear is selectively decoupled from the shaft by displacing the third part, the cam-shaped section, away from the second point. This further reduces the force exerted by the cam-shaped section on the other splines. The reduction in force on the cam-shaped section allows a third and a fourth sleeve to push the other splines radially inward. The other splines can be pushed radially inward when no torque is transmitted between the other gear and the shaft or any of the multiple gears of the jaw coupling assembly. The third and fourth sleeves can, for example, be the first sleeve 274a and the second sleeve 276a of the Fig. 5A-5D.

[0169] The procedure continues by determining whether a torque is transmitted to the other gear and / or whether the shaft rotates above a first speed threshold. Furthermore, the procedure determines, more broadly, whether gears of the jaw coupling assembly transmit a torque to the shaft.

[0170] The torque transmitted between a gear of the jaw coupling assembly, which may optionally be coupled to the shaft, and the shaft itself, can engage the keys in an extended position (e.g., the other keys, which remain in place). When the other keys are engaged and torque is transmitted between the other gears, the torque prevents the other keys from retracting. Further centrifugal forces at a sufficiently high shaft rotational speed lock the other keys in an extended position, preventing their retraction. If it is detected that the other gear is transmitting torque to the shaft, the other gear is synchronized with the shaft by the procedure so that the differential speed between the shaft and the other gear is less than a threshold value.If it is determined that a gear in the jaw coupling assembly, which can be selectively coupled to the shaft, is transmitting torque to the shaft, the selectively coupled gear transmitting torque is synchronized with the shaft of the jaw coupling assembly so that the differential speed between the shaft and the selectively coupled gear is within the differential speed threshold. At differential speeds below the differential speed threshold, virtually no torque is transmitted between the other gear and the shaft, allowing the other teeth to engage. Similarly, if the differential speed falls below the threshold, virtually no torque is transmitted between the selectively coupled gear and the shaft.Furthermore, the other gear and the shaft can rotate at approximately the same speed if the differential speed is less than or equal to the differential speed.

[0171] The springs are dimensioned to overcome the centrifugal force at the rotor's maximum rotational speed. In other words, the springs have sufficient spring force to push a set of keys radially inward over sliding sleeves when the centripetal force on the shaft is at its maximum and when a cam-shaped section, such as cam-shaped section 294, is not in contact with the keys. The first rotational speed threshold can be the maximum speed at which the shaft can be rotated and, if exceeded, centripetal forces are generated that are large enough to overcome the spring force. In other words, the shaft can be throttled at rotational speeds above the first rotational speed threshold. If the shaft is found to be rotating above the first rotational speed threshold, the drive units, such as...Internal combustion engines or electric machines that drive the shaft reduce the rotational energy, e.g., the torque, until the shaft is detected rotating below the threshold.

[0172] In practice, the shaft can be rotated at or below a second speed threshold. This second speed threshold is a second maximum speed and the maximum speed at which the shaft can be driven by the assemblies of a vehicle, such as the engine 120, the first electric motor 124, and the second electric motor 126. Fig. 1. can be rotated. If the shaft is rotated at speeds exceeding the second speed threshold, undesirable effects on the drive may occur. The second speed threshold is significantly lower than the first speed threshold. For example, the second speed threshold is at least less than the first speed threshold minus 5% of the first speed threshold.

[0173] The dimensions and spring force of the springs, the geometries of the sleeves, and the locking function they provide to the jaw coupling assembly can prevent double engagement of the jaw coupling assembly. In double engagement, two sets of splines, e.g., one spline and another, engage with two idler gears, e.g., one gear and another, on the same shaft. Double engagement causes the shaft to lock, reducing its rotation and abruptly stopping the vehicle axle to which the transmission is connected. The arrangement of the springs and sleeves creates a locking mechanism, allowing only one set of splines from the multitude of splines to extend radially beyond the gap threshold. Furthermore, the spring forces are large enough to prevent disengagement and radial outward displacement of the splines by centripetal forces at maximum rotational speed (e.g., at high speed).to reduce the first threshold of rotational speed). In other words, if the keys are not in contact with a cam-shaped section, a set of pulled-out keys will be reduced or completely prevented from pulling out or extending radially outward when the shaft and keys are subjected to centripetal forces less than or equal to a maximum centripetal force acting on the shaft at the first rotational speed threshold.

[0174] If the shaft receives no torque from any gear in the jaw coupling assembly, such as the other gear, and experiences a rotation below the first threshold of rotational speed, the process continues by retracting the other keys from a plurality of other recesses in the other gear. The process continues by retracting the other keys toward a plurality of other through-holes. Once the cam-shaped section is no longer in contact with the other keys, the first process continues, in which the cam-shaped section is moved to the neutral position. The third sleeve or the fourth sleeve can then be axially displaced within it from the first or the second sleeve, creating a gap.

[0175] After the start of the displacement from the neutral position or the movement of the cam-shaped section into a neutral position, the first procedure is continued by moving a first section of the cam-shaped section to the first point, the first section having a first diameter that is so far from the wedges that it lies radially inward.

[0176] The procedure for contacting the keys can vary depending on whether the torque is transmitted to the first shaft and / or the shaft via the selected gear (e.g., the gear to which the keys are pulled out and into which they engage). If the shaft is subjected to torque by the selected gear, the pulled-out set of keys may only be retracted once the selected gear is no longer transmitting torque. The procedure further reduces the pull-out of the keys by the centripetal force. The radially outward centripetal force at maximum shaft speed is less than the radially inward force of the first or second sleeve bearing against the third or fourth sleeve.By reducing the distance between the wedges and reducing the amount of wedges being pulled out, the axial movement of the rod after contact between the cam-shaped section and the wedges can be reduced.

[0177] If the shaft receives no torque from the selected gear during rotation, or if the shaft and selected gear are not rotating, the procedure continues by allowing the keys to be pulled off through contact with the cam-shaped section. The first procedure continues by moving a first sleeve and a second sleeve away from the keys by the force of contact with the cam-shaped section. The first procedure continues by displacing the keys radially outward from contact with the cam-shaped section through a plurality of through-holes by means of a radial force.

[0178] In the first method, a first rotational speed of the shaft can be synchronized with a second rotational speed of the gear. Synchronization between the shaft and gear prevents the transmission of torque from the gear to the shaft during key movement. A prerequisite for engagement is that the differential speed between the shaft and the gear being engaged does not exceed a threshold value. During synchronization, the differential speed between the first and second rotational speeds is reduced below this threshold. The rotational speed of the shaft can be increased or decreased using an electric motor or other electrical machine.For example, the initial rotational speed of the shaft can be reduced by the electric machine so that it is below the threshold of the rotational speed difference to the gear by reducing the torque exerted on the shaft by the electric machine. To synchronize the shafts, a pair of electric machines can be used to synchronize the gear with the shaft. For example, a first electric machine in the pair can drive the gear, and a second electric machine in the pair can drive the drive shaft. The pair of electric machines can be electric motors. For example, the pair of electric machines in a P2 position of vehicle 100 can be... Fig. The gears can be arranged in position 1, with position P2 being separate from positions P1 and P3. Additionally or alternatively, synchronization can be achieved by disconnecting the shaft and / or gear from a torque source, reducing the differential speed of the shaft and gear to zero or less than the differential speed threshold, and reducing the torque to zero. Once the shaft and gear are successfully synchronized, the first procedure can be continued, and the engagement proceeds. The first electric machine can be configured to selectively couple and drive any gear that may be coupled to the jaw coupling arrangement.

[0179] The first method consists of transferring the keys into a plurality of recesses in the gear. The first method is continued by bringing the keys into contact with a surface of the recesses and selectively coupling the gear to the shaft. The first method is continued by moving a third section of the cam-shaped portion to the first point, the third section having a third diameter. The third diameter is a maximum diameter of the cam-shaped portion. The third diameter can be the second diameter 522 of Fig. 5A-5D. In the first method, the third part of the cam-shaped section is held at the first point, with the wedges locking against the gear. After holding the third part of the cam-shaped section, the first method can be completed.

[0180] In an example of the first method, the rod 246 can selectively couple the second gear 216 to the shaft 212. The rod 246 can be in the third position of Fig. 5C begins. The first procedure continues by moving the rod 246 into a first intermediate position between the third and fourth positions of Fig. The first method shifts the rod 246 by 5D. In the first intermediate position, the first part of the cam-shaped section 294 of the first diameter 520 is radially inside the second keys 260. The first method continues the displacement of the rod 246 into a second intermediate position, in which a part of the cam-shaped section with a third diameter contacts the second keys 260, the third diameter being at a distance between the first diameter 520 and the second diameter 522. If the differential speed between the shaft 212 and the second gear 216 is greater than or equal to the threshold value of the differential speed, the cam-shaped section 294 can be prevented from further displacement.The first procedure can be continued by synchronizing the rotational speed of the shaft 212 with the second gear 216 via an electric machine, so that the speed difference between the shaft 212 and the second gear 216 is below the threshold of the differential speed.

[0181] If the differential speed between shaft 212 and the second gear 216 is below the differential speed threshold, and shaft 212 experiences no rotation or rotation below the speed threshold, the cam-shaped section 294 can displace the second splines 260 radially. The differential speed threshold and the rotational speed threshold can be different values. By displacing the second splines 260 radially outward, the third sleeve 274b can be spread apart from the fourth sleeve 276b. The first procedure continues the displacement of the rod 246 into the fifth position, which is described below. Fig. 5D describes where the second wedges 260 engage in the second recesses 266.

[0182] In another example of the first method, the rod 246 can decouple the first gear 214 from the shaft 212 and selectively couple the second gear 216 to the shaft 212. The rod 246 can be in the first position of Fig. 5A begins. The first procedure continues when the rod 246 is moved into the second position. If the shaft 212 rotates at a speed above the rotational speed threshold and / or receives torque from the first gear 214, the distance over which the first keys 258 move radially inward can be reduced. The first keys 258 can remain engaged with the first gear 214. Likewise, the second keys 260 can remain locked and reduce the displacement of the cam-shaped section 294, for example, when the cam-shaped section 294 is in contact with the second keys 260. If the shaft 212 receives no torque from the first gear 214 and the shaft 212 is not rotating or is rotating below the rotational speed threshold, the first keys 258 can move radially inward, and the first sleeve 274a and the second sleeve 276a can move axially closer to each other.From the second position, rod 246 can be moved to the third position. The other example of the first procedure can then proceed with the steps of the above example of the first procedure.

[0183] A second method for shifting gears via a jaw coupling arrangement of the present disclosure, e.g. the jaw coupling arrangement 202, can be described by means of the Fig. 5A-5D will be illustrated.

[0184] The second method may include the same steps as the first method; however, the second method involves reducing the hydraulic pressure on a hydraulic cylinder driven by a shaft, such as shaft 212 of the Fig. 2-5D, is formed. The hydraulic pressure can be increased to more than a second pressure threshold on the side of the piston opposite the side described in the first method. The rod is, for example, rod 246 and the piston is piston 292 of Fig. 2-5D. The hydraulic pressure can be increased between the piston 292 and the first side 204, thereby moving the piston towards the second side 206.

[0185] Additionally or alternatively, the hydraulic pressure on the side of the piston described in the first method can drop below a third pressure threshold, so that the camshaft is moved by the spring force of a spring into a position to lock a gear. For example, a spring can be arranged to press on the piston, e.g., piston 292, of the hydraulic cylinder and displace the piston by spring force. The spring can be housed above a hydraulic pressure body, e.g., frame 248, to push the piston. During displacement, the rod is retracted toward the hydraulic cylinder. After the hydraulic pressure drops below the second pressure threshold, the method continues to displace a cam-shaped section of a rod toward the first point along a central axis, with the majority of the keys arranged radially around the first point.

[0186] It goes without saying that in the second method, other types of actuation systems besides a hydraulic actuator can be used to move the rod. In the second method, these other types of actuation systems can move the rod in a direction opposite to that in the first method. In other examples, the rod can be moved by a purely electric or electrohydraulic actuation system. In other words, instead of a hydraulic pressure cylinder or other hydraulic actuation system, the rod can be moved by a purely electric or electrohydraulic actuation system, where the actuation system includes an electric machine to actuate the rod. In these examples, the electric machine can be an electric motor.

[0187] The second method can follow the steps of the first method in reverse, so that a gear of the jaw coupling arrangement that is coupled via the first method can be uncoupled via the second method, and another gear that can be uncoupled via the first method can be coupled via the second method.The rod can be the rod 246, the cam-shaped section can be the cam-shaped section 294, the first point can be the first point 506, the second point can be the second point 508, the plurality of keys can be the first keys 258, the plurality of other keys can be the second keys 260, the plurality of the through holes for the wedges can be the first through holes 252, the plurality of the other through holes for the other wedges can be the second through holes 254, the gear can be the first gear 214, and the other gear can be the second gear 216.

[0188] In an example of the second method, the rod 246 can selectively couple the first gear 214 to the shaft 212. The rod 246 can be in the third position of Fig. 5C begins. The second procedure continues by moving the rod 246 into a first intermediate position between the third position and the second position of Fig. 5B is displaced. In the first intermediate position, the first part of the cam-shaped section 294 of the first diameter 520 is radially located within the first keys 258. The second method continues the displacement of the rod 246 into a second intermediate position, in which a portion of the cam-shaped section with a third diameter contacts the second keys, the third diameter being a distance between the first diameter 520 and the second diameter 522. If the differential speed between the shaft 212 and the first gear 214 is greater than or equal to the threshold for the differential speed and / or the shaft 212 receives a torque from a gear of the jaw coupling assembly 202, the cam-shaped section 294 can be locked against further displacement.The process can be continued by synchronizing the rotational speed of the shaft 212 with the first gear 214 via an electric machine, so that the speed difference between the shaft 212 and the first gear 214 is below the threshold for the differential speed and / or preventing a torque from being transmitted between a gear of the jaw coupling arrangement 202 and the shaft 212.

[0189] If the differential speed between shaft 212 and the first gear 214 is below the differential speed threshold, no torque is transmitted between any gear of the jaw coupling assembly 202, and shaft 212 experiences no rotation or rotation below the differential speed threshold, the cam-shaped section 294 can displace the second splines 260 radially. The differential speed threshold and the rotational speed threshold can be different values. The cam-shaped section 294 can displace the first splines 258 radially outward and spread the first sleeve 274a away from the second sleeve 276a. The first method involves displacing the rod 246 into the first position of Fig. 5A continues, in which the first wedges 258 engage in the first recesses 264.

[0190] In another example of the second method, the rod 246 can decouple the second gear 216 from the shaft 212 and selectively couple the first gear 214 to the shaft 212. The rod 246 can start at the fifth position, which is specified by Fig. 5D is described. The second procedure continues by moving the rod 246 to the fourth position of Fig. 5D is displaced. If the shaft 212 rotates at a speed above the rotational speed threshold and / or receives torque from the second gear 216, the radial inward displacement of the second splines 260 can be reduced. The first splines 258 can remain locked and reduce the displacement of the cam-shaped section 294, for example, when the cam-shaped section 294 is in contact with the first splines 258. If the shaft 212 receives no torque from the first gear 214 and the shaft 212 is not rotating or is rotating below the rotational speed threshold, the second splines 260 can move radially inward, and the third sleeve 274b and the fourth sleeve 276b can move axially closer to each other. From the fourth position, the rod 246 can be moved to the third position. The other example of the second procedure can then proceed with the steps of the above example of the second procedure.

[0191] A third method can use two or more jaw coupling assemblies of the present disclosure to selectively couple with a gear and shift into different gears of a transmission. The third method can use the first method and / or the second method to move rods, select and engage a gear, and deselect and disengage another gear. In the third method, a first gear can be selected and engaged to selectively couple a first jaw coupling assembly, while a second gear, which can selectively couple a second jaw coupling assembly, is deselected and disengaged. With reference to Fig. 1. The third method can, for example, shift the transmission 108 upshift, thus moving the transmission 108 from third to fourth gear. The third speed can be selected by choosing the second gear set 156 from Fig. 1 can be selected to transfer the torque from one or more movers to the wheels 114 of Fig. 1 to transmit. The fourth speed can be achieved by selecting the sixth gear set 164 of Fig. 1 can be selected to transmit the torque from one or more movers to the wheels 114. The third method can begin with the vehicle 100 being started in third speed, with the sixth gear set 164 selected. When third speed is selected, the odd-numbered clutch (e.g., the clutch inside drum 147 of Fig. 1, which can optionally be combined with the fourth wave 148 of Fig. 1 can be coupled) closed, thereby closing the second claw coupling arrangement 145 of Fig. 1 is optionally coupled to the drum 147. Furthermore, a uniform coupling (e.g., the coupling within the drum 147, which is optionally coupled to the third shaft 146 of Fig. 1 can be coupled) opened, so that the first claw coupling arrangement 143 of Fig. 1 is optionally decoupled from drum 147. The odd-numbered coupling and the even-numbered coupling can be wet couplings in this example.

[0192] The third procedure can be continued by determining whether both the third speed on the odd-numbered shaft and the fourth speed on the even-numbered shaft are engaged. In other words, the third procedure determines whether the sixth gear set 164 of Fig. 1 via the second claw coupling arrangement 145 and the second gear set 156 of Fig. 1 is selected via the first claw coupling arrangement 143, wherein the selection of the sixth gear set 164 selects the third gear and the selection of the second gear set 156 selects the fourth gear. In an arrangement in which the sixth gear set 164 is selected, the second cam of the second rod 194 is located Fig. 1 under the eleventh gear 181 of Fig. 1 and touches a second set of the second wedges 198 of Fig. 1, to engage the eleventh gear 181. In this arrangement, or any other arrangement in which the second gear set 156 is selected, the first cam of the first rod 192 is located Fig. 1 under the third gear 173 of Fig. 1 and touches a first set of the first wedges 196 of Fig. 1, to engage the third gear 173. The sixth gear set 164, and thus the third gear, is selected at the beginning of the third process in this example.

[0193] If the third gear 173 is not engaged (e.g., if fourth gear and the second gear set 156 are not engaged by the first dog clutch assembly 143), the third method can advance the first rod 192 to a position where the first cam of the first rod 192 is located under the third gear 173 and contacts the first set of the first splines 196. By positioning the first cam of the first rod 192 under the third gear 173, the third shaft 146 is selectively coupled to the third gear 173, and the second gear set 156 is engaged.

[0194] When the third gear 173 is engaged (e.g., when fourth gear and the second gear set 156 are selected by the first claw coupling assembly 143), the third method can hold the first rod 192 so that the first cam remains positioned under the third gear 173, thereby keeping the third gear 173 engaged and optionally coupled to the third shaft 146.

[0195] The third method and the locking arrangement of the first jaw coupling assembly 143 prevent or reduce the engagement of the other gears, which may be optionally coupled to the third shaft 146, such as the first gear 171, the fifth gear 175, and the seventh gear 177, when the third gear 173 is engaged. Likewise, the third method and the locking arrangement of the second jaw coupling assembly 145 prevent or reduce the engagement of the other gears, which may be optionally coupled to the fourth shaft 148, such as the ninth gear 179, the thirteenth gear 183, and the fifteenth gear 185, when the eleventh gear 181 is engaged.

[0196] In the third method, the torque is transferred from the second jaw coupling assembly 145 to the first jaw coupling assembly 143. During the torque transfer, the odd-numbered coupling opens and the even-numbered coupling closes. When the odd-numbered coupling opens, the second jaw coupling assembly 145 is disengaged from the drum 147. When the even-numbered coupling is closed, the first jaw coupling assembly 143 is selectively coupled to the drum 147. The torque transfer from the second jaw coupling assembly 145 to the first jaw coupling assembly 143 can occur within a time span of a few hundred milliseconds. The first cam of the first rod 192 and the second cam of the second rod 194 remain in their positions.

[0197] After shifting from 3rd to 4th gear, the process opens the odd-numbered clutch, reducing the torque of the eleventh gear 181 almost to zero. The differential speed between the eleventh gear 181 and the fourth shaft 148 can be below the threshold of the differential speed. The third process can optionally be continued by shifting the second cam of the second rod 194 under another gear, which can selectively engage the fourth shaft 148. When the second cam is shifted under the other gear, it contacts another set of second splines 198 of the second dog clutch assembly 145, which selectively engage and engage the other gear. In other words, the third process preselects the other gear to selectively engage the fourth shaft 148, so that the other gear is selected when the torque is transferred from the first dog clutch assembly 143 to the second dog clutch assembly 145.For example, the second rod 194 is moved so that the second cam advances under the thirteenth gear 183 and preselects it. Another example: The second rod 194 is moved so that the second cam advances under the ninth gear 179 and preselects it.

[0198] This discloses a plurality of methods for a method of shifting gears via a jaw coupling arrangement, wherein the hydraulic pressure on a hydraulic cylinder is increased or decreased to actuate a rod and bring a cam-shaped section of the rod into and out of contact with a plurality of keys. Contacting the keys with the cam-shaped section engages the keys with a gear to create engagement between the keys and a plurality of recesses in the gear, the gear being optionally coupled to a shaft that accommodates the hydraulic cylinder and the rod. By moving the keys out of contact with the cam-shaped section, the gear is optionally decoupled from the shaft, and the coupling between the keys and the plurality of recesses is released.

[0199] In another interpretation, the disclosure provides a mounting for a jaw coupling arrangement, comprising: a hollow shaft with a plurality of first through holes and a plurality of second through holes arranged radially about a central axis and extending from an outer surface to an inner surface of the hollow shaft; a first rod, wherein the first rod is received by the hollow shaft; a first gear, wherein the first gear is arranged radially around the first through holes; a second gear, wherein the second gear is arranged radially around the second through holes; a plurality of first sliding keys, wherein the first sliding keys are housed in the first through holes and are arranged to extend through the first through holes and into a plurality of first recesses of the first gear;a plurality of second sliding wedges, wherein the second sliding wedges are accommodated in the second through-holes and arranged to extend through the second through-holes of the shaft and into a plurality of second recesses of the second gear; a first set of first sleeves, wherein the first sliding wedges are arranged axially between the first sleeves; a second set of second sleeves, wherein the second sliding wedges are arranged axially between the second sleeves;and a rod which is received by the shaft and arranged to move coaxially along the central axis, the rod contacting the first sliding wedges and moving into the first recesses to selectively engage the first gear with the shaft, and the rod contacting the second sliding wedges and moving into the second recesses to selectively engage the second gear with the shaft. In a first example of the system, the rod comprises a cam-shaped section, the cam-shaped section contacting the first sliding wedges when moved to a first point along the central axis, and contacting the second sliding wedges when moved to a second point along the central axis.

[0200] Although various embodiments have been described above, it should be clear that these serve only as examples and do not constitute limitations. Those skilled in the art will recognize that the disclosed subject matter can be implemented in other specific forms without departing from the spirit of the subject matter. The embodiments described above are therefore to be regarded in every respect as illustrative and not as limiting. Thus, the configurations and routines disclosed here are exemplary in nature, and the specific examples are not to be considered limiting, as numerous variations are possible. The technology described above can, for example, be applied to powertrains that include various types of power sources, including different types of propulsion motors, internal combustion engines, and / or transmissions.The subject matter of the present disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, as well as other features, functions and / or properties disclosed herein.

[0201] It is understood that the configurations and routines disclosed herein are exemplary and that these specific embodiments are not to be considered limiting, as numerous variations are possible. Unless expressly stated otherwise, the terms "first," "second," "third," etc., do not denote any order, position, quantity, or significance, but serve only to distinguish the individual elements. The subject matter of this disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, as well as other features, functions, and / or properties disclosed herein.

[0202] The following claims highlight in particular certain combinations and subcombinations that are to be considered novel and not obvious. These claims may refer to "one" element or "a first" element, or the equivalent thereof. Such claims are to be understood as including one or more such elements, with two or more such elements neither required nor excluded. Other combinations and subcombinations of the disclosed features, functions, elements, and / or properties may be claimed by amending the present claims or by filing new claims in this or a related application. Such claims, whether they have a broader, narrower, the same, or different scope than the original claims, are also to be considered as included in the subject matter of the present disclosure.

Claims

[1] Gearbox, comprising: a hollow shaft with at least two sets of radial through holes, including a first set and a second set of radial through holes; a multitude of gears arranged around the hollow shaft; a plurality of sliding wedges arranged to extend through the radial through-holes of the hollow shaft and engage in a plurality of recesses of a selected gear to engage and couple the selected gear; a plurality of sliding sleeves, each of the plurality of sliding wedges being arranged between two sliding sleeves, the two sliding sleeves being spring-loaded and bearing against the plurality of sliding wedges in such a way that only one gear is selected, thereby realizing a locking mechanism for the plurality of sliding wedges; and a rod configured to move coaxially to and along the hollow shaft, the rod having a cam-shaped section configured to actuate the plurality of sliding keys of the selected gear. [2] Gearbox according to claim 1, wherein the cam-shaped section is actuated via a hydraulic cylinder located in the hollow shaft, the hydraulic cylinder changing a pressure to bring the cam-shaped section into and out of contact with the plurality of sliding wedges, and the rod containing a piston on which the hydraulic pressure acts to move the rod coaxially along the axis. [3] Gearbox according to claim 2, wherein the hydraulic cylinder has a first passage, a second passage and a frame, wherein the first passage provides hydraulic pressure for actuating the piston, wherein the frame is received by the second passage, wherein the frame is arranged around the rod and supports it, wherein the frame prevents the rod from moving along the axis beyond a first point and a second point along the axis. [4] Gearbox according to any of the preceding claims, wherein each set of radial through-holes has geometries that reduce the self-locking of a respective set of the plurality of sliding wedges. [5] Transmission according to any of the preceding claims, wherein the plurality of gears arranged along the hollow shaft are idle gears. [6] Gearbox according to any of the preceding claims, wherein each set of adjacent gears of the plurality of gears arranged along the hollow shaft has an axial clearance of less than 10% of the end face width of the adjacent gears. [7] Gearbox according to one of the preceding claims, wherein each axial play between two sliding sleeves of the same set is a distance dimensioned such that the axial play and at least one sliding sleeve of the same set hinders the withdrawal of other sets of wedges between other sets of other sliding sleeves. [8] Gearbox according to one of the preceding claims, wherein there is a distance between a pair of sets of the plurality of sliding wedges and the cam-shaped section has a length which is less than the distance, so that the cam-shaped section is displaced into a neutral position between the pair of sets in which the contact of the cam-shaped section with each set of the plurality of sliding wedges from the pair is reduced. [9] Gearbox according to any of the preceding claims, wherein each of the plurality of sliding wedges has a base and a head, the base having a first inclined surface and a second inclined surface which are symmetrical and mirror images and extend in the direction of the head, wherein a first sliding sleeve abuts and rests against the first inclined surface of a sliding wedge and a second sliding sleeve abuts and rests against the second inclined surface of the sliding wedge, thereby blocking and reducing the extension of the sliding wedge in the direction of a recess of a gear. [10] Gearbox according to claim 9, wherein the first sliding sleeve slides away from the sliding wedge along the first inclined surface and the second sliding sleeve slides away from the sliding wedge along the second inclined surface when a radial force greater than a force threshold extends the sliding wedge radially outwards. [11] The transmission according to one of the preceding claims, wherein the hollow shaft has a plurality of other sets of radial through holes and the plurality of sliding wedges is arranged to extend radially outwards from each of the other sets of radial through holes and into recesses of another gear. [12] Vehicle, comprising: a first drive device; a second drive device; a first shaft, wherein the first shaft is hollow and is driven by the first drive device, the first shaft comprising a plurality of first sliding wedges and a first rod, wherein the plurality of first sliding wedges is arranged to extend through a plurality of first slots of the first shaft, and the first rod is arranged to move coaxially along the first shaft and to contact the plurality of first sliding wedges, such that the latter extend through the plurality of first slots; a second shaft, wherein the second shaft is driven by the second drive device; a transmission, wherein the transmission comprises a gear selection arrangement, the gear selection arrangement comprising a plurality of first gear sets with different gear ratios; and a drive axle, wherein the drive axle is driven by the second shaft; wherein each of the plurality of first gear sets of the gear selection arrangement has at least one first gear and one second gear, wherein each first gear is arranged around the first shaft such that a set of the plurality of first sliding keys extends through the plurality of first slots into a plurality of recesses of a selected first gear, engages in the selected first gear and selectively couples the selected first gear to the first shaft, and each second gear is rigidly coupled to the second shaft, the first gear drives the second gear, and wherein the first shaft drives the second shaft via a selected gear set of the plurality of first gear sets which includes the selected first gear. [13] Vehicle according to claim 12, wherein the gear selection arrangement comprises a plurality of second gear sets with different gear ratios; wherein each of the plurality of second gear sets has at least a third gear and a fourth gear, wherein the third gear selectively couples a rotating element driven by the first drive device and the fourth gear is rigidly coupled to the second shaft, and the third gear drives the fourth gear. [14] Vehicle according to claim 13, wherein the rotating element is a third shaft, the third shaft being hollow and comprising a plurality of second sliding wedges and a second rod, wherein the plurality of second sliding wedges is arranged to extend through a plurality of second slots of the third shaft, and the second rod is arranged to displace coaxially along the third shaft and to contact the plurality of second sliding wedges so that they extend through the plurality of second slots, and wherein the third gear is arranged around the first shaft such that another set of the plurality of second sliding wedges extends through the plurality of second slots into a plurality of other recesses of a selected third gear, engages in the selected third gear and selectively couples the selected third gear to the third shaft,wherein the third shaft drives the second shaft via another gear set of the plurality of second gear sets, which includes the selected third gear. [15] Vehicle according to any one of claims 12 to 14, wherein the first drive device and the second drive device are electric machines that are part of an electrified powertrain.

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