Freewheel clutch for use in a power transmission device

Abstract

Freewheel clutch (630, 630A, 630B) for use in a power transmission device with hydraulic fluid, wherein the freewheel clutch (630, 630A, 630B) comprises the following: a coupling arrangement (20, 120, 220, 420, 520, 600, 600A, 600B) with an inner ring (36) and an outer ring (22) rotatable with respect to the inner ring (36), wherein the outer ring (22) has several locking structures consisting of inner ratchet teeth (34) and outer ratchet teeth (44); and a ratchet finger arrangement (48, 448, 548, 632) with an active ratchet finger (50) which is for movement between a first position displaced from engagement with the inner ratchet teeth (34) and outer ratchet teeth (44), which defines a free-running mode, and a second position engaged with the inner ratchet teeth (34) and outer ratchet teeth (44), which defines a locked mode by which the inner ring (36) is supported, wherein the inner ring (36) and / or the active locking finger (50) has / have an anti-disengagement feature configured to assist in holding the actuator element in its first position during a rotation of the outer ring (22) relative to the inner ring (36) by counteracting hydraulic forces applied by the hydraulic fluid to the active locking finger (50), characterized in that the anti-disengagement feature counteracts the hydraulic forces applied to the active locking finger (50) by diverting the fluid to flow in a path configured to push the active locking finger (50) into its first position.

Description

AREA OF INVENTION

[0001] The present disclosure relates generally to overrunning clutch devices, such as freewheel clutches or brakes, and in particular to selectable one-way coupling devices (SOWC devices, SOWC - Selectable One-Way Coupling) and / or electronically controlled one-way coupling devices (EOWC devices, EOWC - Electronically-Controlled One-Way Coupling) with a deployable locking finger and an arrangement to prevent unintentional deployment of the locking finger. BACKGROUND OF THE INVENTION

[0002] This section provides background information relating to the present disclosure, which is not necessarily the state of the art.

[0003] Automatic transmissions provide multiple forward and reverse gear ratios or stages by selectively actuating one or more clutches and / or brakes to establish a torque-transmitting drive connection between a transmission input and a transmission output to supply driving force (i.e., drive torque) from a drivetrain to a transmission in a motor vehicle. A common type of brake or clutch in automatic transmissions is an overrunning clutch device, commonly referred to as a one-way clutch (OWC), which freewheels when one of its rings (in a radial clutch configuration) or one of its drive pulleys (in axial clutch configurations) rotates in a first (i.e., freewheeling) direction relative to the other ring or drive pulley, and engages or locks in a second (i.e., locking) direction.Typically, a locking element, such as a detent finger, associated with the freewheel clutch, is movable between a disengaged position for creating a freewheel mode and an engaged position for creating a locked mode. The detent finger is generally biased in one of its two positions. Such conventional freewheel clutches do not provide independent control over their operating modes—that is, whether they lock or freewheel in both directions—and are commonly referred to as passive freewheel clutches. Thus, simple freewheel clutches provide the "locked" mode in one direction of rotation and the "freewheel" mode in the opposite direction, depending on the direction in which the drive torque is applied to the input ring or drive pulley.

[0004] However, modern automatic transmissions have requirements that necessitate a "controllable" overrunning clutch device, commonly referred to as either a selectable one-way clutch (SOWC) or an electrically controlled one-way clutch (EOWC), to provide additional operating modes. Specifically, a controllable one-way clutch can be capable of generating a freewheel mode in both directions of rotation until a command signal (i.e., from the transmission control unit) causes an externally driven actuator to engage the clutch device in its locked mode. Thus, a controllable one-way clutch can provide a drive connection between an input and output element in one or both directions of rotation and can be operated to freewheel in one or both directions.Furthermore, it is known in modern automatic transmissions to integrate a passive freewheel clutch and a controllable freewheel clutch into a combined clutch device, which is commonly referred to as a bidirectional clutch.

[0005] During development tests of controllable freewheel clutches, at least one problem was identified that required addressing. Specifically, under certain operating conditions of the automatic transmission, excessive oil levels are generated in the controllable freewheel clutches near the deployable detent fingers, potentially leading to unintended "hydraulic deployment" of the detent finger. Unintended hydraulic deployment is a condition in which the detent finger, independent of the actuation of the externally driven actuator, is moved from its disengaged position to its deployed position due to a pressure gradient acting upon it. This pressure gradient, together with fluid dynamics associated with the fluid flow around the clutch components, results in a force vector acting on one end of the detent finger.As the hydraulic force acting on the end part of the locking finger increases, it eventually overcomes the preload force exerted on the locking finger by the locking finger return spring, leading to an unintentional partial or complete deployment of the locking finger.

[0006] Such an unintentional hydraulic extension can cause the locking finger to "ratchet" against the inner ring / drive pulley, leading to premature failure of the locking finger system and / or the armature connected to the externally driven actuator due to fatigue. Furthermore, the impact can deform the armature / locking finger configuration, resulting in a loss of primary locking function, as the locking finger may only have partial extension capability.

[0007] US 2018 / 0094677A1 discloses a freewheel clutch comprising a clutch assembly, an inner ring, and an outer ring rotatable with respect to the inner ring, wherein the second member has multiple locking structures; and a detent finger assembly comprising an active detent finger that provides movement between a first position disengaged from the engagement of the inner and outer ratchet teeth, defining a freewheel mode, and a second position engaged with the inner and outer ratchet teeth, defining a locked mode, thereby supporting the first member. The inner member and / or the active detent finger includes an anti-disengagement feature configured to assist in holding the actuator member in its first position during rotation of the outer ring with respect to the inner ring by counteracting hydraulic forces applied to the active detent finger by the hydraulic fluid.

[0008] There is a need for the further development of new and improved overtaking clutch devices that advance the technology and offer improved functionality. SUMMARY OF THE INVENTION

[0009] This section provides a general summary of the revelation and should not be interpreted as a complete and comprehensive listing of all its aspects, features, and benefits.

[0010] According to one aspect of the present disclosure, a freewheel clutch arrangement is provided which is designed for use in a power transmission device.

[0011] Another aspect of the present disclosure is to configure the freewheel clutch arrangement to include a clutch module with a first component and a second component arranged to rotate with respect to the first component, and a detent finger module with at least one detent finger pivotably mounted for movement with respect to ratchet teeth formed on the second component between a disengaged / unlocked position and an engaged / locked position.

[0012] As a related aspect, the freewheel clutch is configured to include an anti-disengagement feature in conjunction with the first component and / or the detent finger, which can prevent unintentional movement of the detent finger into its disengaged / locked position in response to hydraulic fluid forces and / or fluid dynamics acting on the freewheel clutch assembly within the power transmission device.

[0013] According to one embodiment, a first anti-release feature shall provide an elongated flow channel in the first component, which serves to direct fluid away from the locking finger in response to a rotation of the second component relative to the first component within the power transmission device.

[0014] According to another embodiment, a second anti-extension feature shall provide a cam-equipped surface on the first component configured to guide fluid to assist in holding the locking finger in its non-extensioned / unlocked position in response to a rotation of the second component relative to the first component within the power transmission device.

[0015] According to yet another embodiment, a third anti-disengagement feature shall provide one or more flow lines or “spoilers” in the locking finger configured to direct fluid to assist in holding the locking finger in its non-disengaged / unlocked position in response to a rotation of the second component relative to the first component within the power transmission device.

[0016] According to a further embodiment, a fourth anti-disengagement feature provides one or more elongated flow channels on the cam-equipped surface of the first component, which are directed toward one or more corresponding flow channels or "spoilers" provided in the locking finger. These flow channels or "spoilers" work together to guide fluid and assist in holding the locking finger in its disengaged / unlocked position in response to a rotation of the second component relative to the first component within the power transmission device. The flow channel(s) associated with the cam-equipped surface of the first component are configured to direct fluid flow into the corresponding flow channel(s) formed in the locking finger, thereby applying a fluid-generated preload force to the locking finger to press it into its disengaged / locked position.

[0017] One or more of these anti-deployment features can be applied to a passively controlled freewheel clutch assembly, an actively controlled freewheel clutch assembly, or a combination thereof configured as a bidirectional freewheel clutch assembly.

[0018] Further areas of application of the concepts according to the invention will become apparent from the detailed description provided here. The aspects and embodiments mentioned in this summary are not intended to limit the scope of protection of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The drawings described here serve only to illustrate selected embodiments and are not intended to limit the scope of protection of this disclosure. The inventive concepts associated with this disclosure become clearer when referring to the following description in conjunction with the accompanying drawings; the drawings show: Fig. 1 an expanded isometric view of a bidirectional coupling arrangement configured to include a passive freewheel coupling and a controllable freewheel coupling with an electromechanical actuator and a punch grid and an integrated safety switch according to one aspect of the disclosure; Fig. 2 a front view of the punch grid and the integrated safety switch of Fig. 1; Fig. 3 an isometric partial view of the in Fig. 1 coupling arrangement shown in an assembled state; Fig. 3A and Fig. 3B Sectional views of the electromagnetic actuator of Fig. 3, wherein a latching finger of an active latching finger arrangement is shown in a locked (i.e. deployed) or unlocked (i.e., not deployed) position in response to a respective excited or unexcited state of the electromagnetic actuator; Fig. 4A and Fig. 4B similar views to the Fig. 3A and Fig. 3B, wherein they show an alternative embodiment of an electromagnetic actuator carried out in accordance with another aspect of the present disclosure; Fig. 5 a coupling arrangement with a switchable freewheel coupling comprising an electromagnetic actuator fitted by press fit and associated with an active locking finger arrangement, according to another aspect of the present disclosure; Fig. 5A an enlarged partial section view of Fig. 5, which represents a radially pressed electromagnetic actuator according to one aspect of the present disclosure; Fig. 5B a similar view to Fig. 5A, which shows another version of a radially pressed electromagnetic actuator designed according to another aspect of the present disclosure; Fig. 6 an expanded isometric view of a bidirectional clutch arrangement configured to include a modular active detent finger arrangement for a switchable freewheel clutch according to another aspect of the present disclosure; Fig. 7 a sectional view of the in Fig. 6 bidirectional coupling arrangement shown; Fig. 8 An enlarged partial side view of an active locking finger arrangement designed for use with the switchable freewheel clutch, which corresponds to the bidirectional clutch arrangements of Fig. 1 is assigned and configured to provide a high inertia load resistance arrangement according to the present disclosure, and which represents the active latching finger in an unlocked position when an electromagnetic actuator is not energized; Fig. 9 a similar view to Fig. 8, which represents the active latching finger, which is in a locked position in response to an excitation of the electromagnetic actuator; Fig. 10 a similar view to Fig. 8, which represents the inertial load resistance arrangement that necessarily holds the active locking finger in its unlocked position when a radially directed high inertial load is applied; Fig. 11 an enlarged partial view of an active locking finger arrangement designed for use with any of the controllable freewheel clutches associated with any of the previously disclosed bidirectional clutch arrangements of the present disclosure, and configured to provide one or more features to prevent hydraulic ejection; Fig. 12 an enlarged partial view of Fig. 11, which further describes a first and a second feature for preventing hydraulic discharge; Fig. 13 an isometric view of the active latching finger arrangement of the Fig. 11 and Fig. 12 associated locking fingers, which further illustrate a third feature to prevent hydraulic ejection; Fig. 14 an isometric view of the active latching finger arrangement of Fig. 13, which further describes the combination of all three features to prevent hydraulic discharge; Fig. 15 Another isometric view of the active latching finger arrangement of Fig. 13, which are the three features for preventing hydraulic discharge of Fig. 14, which are now combined with a fourth feature to prevent hydraulic discharge, shows; and Fig. 16 another isometric view of the active latching finger arrangement of Fig. 13, which is an alternative configuration for the in Fig. The fourth feature shown in 15 is designed to prevent hydraulic discharge. DESCRIPTION OF IMPLEMENTATION METHODS

[0020] Exemplary embodiments are now described in more detail with reference to the accompanying drawings. Each embodiment generally relates to an overrunning clutch device (that is, a brake and / or a clutch) that has at least one controllable freewheel locking device, which includes a movable locking component (for example, a clamping element, a detent finger, etc.) that is controlled at least partially by an electromagnetic actuator. Thus, the freewheel locking device transmits torque mechanically but is actuated by an electrical actuation system. However, the exemplary embodiments are provided only to the extent that the present disclosure is comprehensive and conveys its full scope to a person skilled in the art.Numerous specific details are provided, such as examples of specific components, devices, and methods, to ensure a comprehensive understanding of the embodiments of the present disclosure. It is obvious to the person skilled in the art that specific details are not necessary, that embodiments can be designed in many different ways, and that none of these should be considered a limitation of the scope of protection of the disclosure. In some embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.

[0021] On the Fig. Referring to Figures 1-3, in which the same numbers in all of the several views indicate corresponding parts, a bidirectional coupling arrangement 20 is shown in general terms. As detailed below, the bidirectional coupling arrangement 20 generally comprises a coupling module with a stationary outer ring and a rotatable inner ring, a passive freewheel coupling with several passive detent fingers, and a controllable freewheel coupling with at least one active detent finger arrangement and an electromagnetic actuator. The coupling module of the coupling arrangement 20 comprises an outer ring 22 extending circularly around an axis A. The outer ring 22 comprises an outer rim segment 24 and an inner rim segment 26, which are radially spaced apart and connected to each other via a radial web segment 27.The outer ring segment 24 has several outer projections 28 extending radially outward from the outer surface 29 for assembly with a first component. The first component can be a stationary component (for example, a gearbox housing) or a rotating component (such as a shaft). The outer ring segment 24 also has at least one projection 30 extending radially outward from the outer surface 29. Each projection 30 defines a radially extending actuator pocket 32 ​​and a ratchet finger pocket 33. It should be obvious that more or fewer projections 30 could be used. The inner ring segment 26 has several inner ramp surfaces, referred to below as inner ratchet teeth 34, extending radially inward and evenly spaced around axis A.

[0022] The coupling module of the coupling assembly 20 further comprises an inner ring 36, which also extends circularly around the axis A. The inner ring 36 has an outer rim 38 and an inner rim 40, which are radially spaced apart from each other by a radial web segment 41. The outer rim 38 is arranged radially between the outer and inner rim segments 24, 26 of the outer ring 22, and the inner rim 40 is arranged radially inward from the inner rim segment 26 of the outer ring 22. The inner rim 40 of the inner ring 36 has several internal projections 42 that extend radially inward for assembly with a second component (generally a rotating component). The projections 42 commonly connect a shaft or coupling plates to the inner ring 36 for rotation.Furthermore, the outer edge 38 of the inner ring 36 has several outer ramp surfaces, which are referred to below as outer ratchet teeth 44, which extend radially outwards and are evenly distributed around the axis A.

[0023] The passive freewheel clutch contains several locking elements, also referred to as passive detent fingers 46, which are pivotably supported in detent finger openings formed in the inner ring 36 for pivoting between a locked and an unlocked position. In the locked position, the passive detent fingers 46 engage the inner ratchet teeth 34 of the outer ring 22 to connect the outer and inner rings 22, 36 during counterclockwise rotation of the inner ring 36 relative to the outer ring 22. Therefore, engagement by one or more passive detent fingers 46 prevents relative counterclockwise displacement of the outer and inner rings 22, 36. However, the passive detent fingers 46 allow relative displacement, i.e., freewheeling, in a clockwise direction when they are in the locked position, as they ratchet over the ramped profile of the inner ratchet teeth 34.In the unlocked position, the passive locking fingers 46 are radially spaced from the inner ratchet teeth 34 of the outer ring 22, which is why they also allow a counterclockwise rotation of the inner ring 36 relative to the outer ring 22.

[0024] In conjunction with the controllable freewheel clutch, an active detent finger assembly 48 is received by each of the detent finger pockets 33 of the outer ring segment 24. Each of the active detent finger assemblies 48 contains an active detent finger 50, which is selectively pivotable between a locked (extended) and an unlocked (disengaged) position. In the locked position, the active detent finger 50 engages the outer ratchet teeth 44 of the inner ring 36 in a locking manner, thereby locking the outer and inner rings 22, 36 together during a clockwise movement of the inner ring 36 relative to the outer ring 22. However, the active detent finger 50 still allows relative displacement, i.e., freewheeling, in a counterclockwise direction. In the unlocked position, the active locking finger 50 is radially spaced from the outer ratchet teeth 44, allowing the inner and outer rings 22, 36 to rotate relative to each other.Furthermore, each of the active locking finger arrangements 48 contains an anchor 60, which is arranged next to the active locking finger 50 and in operative relation to it to provide the pivoting movement of the active locking finger 50.

[0025] The switchable freewheel clutch further comprises electromagnetic actuators 51, each containing a coil assembly 52, which is mounted in the actuator pocket 32 ​​and radially spaced from the active locking finger 50 and armature 60. The coil assembly 52 includes a core 54 made of a magnetically permeable material, a coil former 56 arranged around the core 54, and a coil 58 wound around the coil former 56. Furthermore, the armature 60 is arranged between the active locking finger 50 and the coil 58 to pivot towards the core 54 and thus provide the pivoting movement of the active locking finger 50 in response to excitation of the coil 58. The armature 60 can be made of a magnetic material so that it is magnetically attracted to the core when the coil 58 is excited, or, in alternative actuators 51, it can be made of a non-magnetic material for mechanical coupling with a moving component (a solenoid).

[0026] In a preferred, but not limiting, arrangement, when a voltage and / or current is applied to the coil 58, it becomes an electromagnet that generates an electric field (or an electric flux). The flux flows outwards in all directions and is transmitted through the small air gap between the armature 60 and the core 54 in the center of the coil arrangement 52. The core 54 is magnetized, causing the armature 60 to be attracted to the core 54. The resulting movement pushes the active locking finger 50 into its mechanical ejection position due to the linkage between the active locking finger 50 and the armature 60. During ejection, the active locking finger 50 moves from its unlocked position ( Fig. 3B) into its locked position ( Fig. 3A), where it positions itself against one of the outer ratchet teeth 44 of the inner ring 36 and effectively locks the inner ring 36 against rotation in that direction. Disengagement occurs when voltage and / or current are removed from the coil assembly 52, whereby the armature 60 is demagnetized and no longer exerts a magnetic attraction on the core 54 of the coil assembly 52. ​​A preload element, such as a return spring 61, is positioned between the active detent finger 50 and the outer ring 22 in the detent finger pocket 33, causing the active detent finger 50 to return to its unlocked position when the coil assembly 52 is de-energized and the core 54 is demagnetized.

[0027] It should be obvious that the arrangement consisting of the armature 60, the active locking finger 50, and the coil arrangement 52 can exert a locking force in a radial direction (as shown in the diagram), depending on the design and / or requirements of the coupling arrangement 20. Fig. (1 shown) or in an axial direction. Radially stacked versions of the coupling arrangement 20 offer packaging advantages over their axial counterparts in situations where axial space is limited, for example in automatic transmissions. Furthermore, radially actuated couplings transmit drive torque directly outwards for anchoring against the transmission housing without the risk of forces being transmitted directly axially, which could cause problems for the dimensioning of other system components for compensating axial forces.

[0028] A punched grid 62 is attached to each of the electromagnetic actuators 51 for electrically connecting the coils 58 to excite them. It should be obvious that the punched grid 62 could connect any number of coils 58. A printed circuit board (PCB) 64 is attached to the punched grid 62 for selectively controlling the excitation of the coils 58. The PCB 64 is arranged radially and axially adjacent to one of the coils 58. The punched grid 62 also includes at least one power output contact 66, which is arranged radially and axially adjacent to each of the coils 58 to electrically connect the coils 58 and thus supply power to them. Any number of power output contacts 66 could be used to control any number of coils 58.A resistance-welded connection is used to connect the power output contact 66 and the coils 58; however, other connections could be used as an alternative. Furthermore, at least one wire (not shown) extends between the circuit board 64 and each of the power output contacts 66 for the electrical connection of the circuit board 64 and the power output contacts 66. The stamped grid 62 also contains a wiring harness 68 that extends from the circuit board 64 to connect to a transmission control module (TCM) or a powertrain control module (PCM) for transmitting data to the circuit board 64 and for supplying power to the circuit board 64.

[0029] Furthermore, the die-cut grid 62 includes a plastic encapsulation or housing 70, which is arranged around the circuit board 64 and the wires, to protect the circuit board 64 and the wires, to allow immersion of the die-cut grid 62 in automatic transmission fluid, and to allow operation at temperatures between -40°C and +140°C. It should be obvious that the above-mentioned configuration of the die-cut grid 62 and the associated components offers a cost-effective, modular solution that provides a simplified manufacturing process.

[0030] The voltage applied to the coils 58 consists of a high side and a low side and is supplied by the vehicle's TCM or PCM. The high side (HS) is typically a power supply shared with other loads, and the low side is typically a discrete line (LSD) that controls the discrete / individual circuitry. The LSD can control the current flowing through the coils 58. Since the LSD is usually located within the TCM / PCM, a wiring harness is required between the electromagnetic actuators 51 and the TCM / PCM. If the wiring harness sustains mechanical damage and the discrete LSD line of the electromagnetic actuators 51 is shorted to chassis ground, the coils can be energized. Accordingly, an integrated high-side failsafe switch (HSFSS) is provided to add another layer of logic and thus control the shared high-side supply.The HSFSS consists of the printed circuit board 64 (PCB), a high-side switch (not shown), a transistor (not shown), and passive components (not shown). These are electrically connected to the die-cut grid 62. It should be obvious that the configuration of the die-cut grid 62 protects the integrated electronic components (including the HSFSS) and provides improved packaging and reduced wiring. Furthermore, it should be obvious that the modular configuration of the die-cut grid 62 and associated components could be used in other coupling arrangement configurations, for example, axially inset coupling arrangements. The HSFSS is controlled by OWCC_HS_ENABLE, which allows the HSFSS to conduct current to the coils 58. Fig. Figure 3 represents an embodiment of a circuit which could be used with the printed circuit board 64 according to one aspect of the disclosure.

[0031] On the Fig. 3, Fig. 3A and Fig. Referring to Figure 3B, in one embodiment of the projections 30, the open side surface 35 defines the actuator pocket 32 ​​for the axial reception of the coil assembly 52. ​​Furthermore, a radially outwardly projecting outer wall 72 of the projection 30 provides a through-channel, also simply referred to as the passage 74, which extends radially inward into the actuator pocket 32. In this embodiment, the coil 58 and the coil former 56 are axially arranged and press-fitted through the open side surface 35 into the actuator pocket 32. After positioning in the actuator pocket 32, which extends radially inward from the outer wall 72, the core 54 is pressed radially inward through the passage 74 and through a central through-channel of the coil former 56 until it reaches a predetermined, preset position that establishes the magnetic gap G between an armature 60 and the free end of the core 54.The core 54 achieves an interference fit against an inner surface 75, which defines and limits the through-channel of the coil former 56, thereby fixing it against movement within it. The core 54 can also be fitted into the through-channel of the coil former 56 by interference fit or configured in a clearance fit within it. Fig. Figure 3A shows an active locking finger 50 in the locked position as a result of the excitation of the coil assembly 52, and Fig. 3B shows the active locking finger 50 in the unlocked position as a result of the de-excitation of the coil assembly 52.

[0032] On the Fig. Referring to 4A-4B, another embodiment of a part of a coupling arrangement 120, similar to that referred to in the Fig. 3, Fig. 3A and Fig. As discussed in Figure 3B, the same reference numbers plus 100 are used to identify identical features. The coil assembly 152 is axially arranged and press-fitted into the respective actuator pockets 132, as discussed above; however, instead of being directly fixed and press-fitted in a passage 174 in an outer wall 172 of the projection 130, the core 154 is operatively fixed in the passage 174 in the outer wall 172 via a hollow adapter plug, also referred to as a nut 76. The nut 76 is first fixed in the passage 174 of the projection, and then the core 154 is positioned through the nut 76 and fixed thereto, whereupon the core 154 is slightly adjusted to provide the desired gap G between the free end of the core 154 and the armature 160.The nut 76 is provided with an outer surface 77 configured for fixation in the passage 174, for example by an interference fit and / or an adhesive and / or a welded joint and / or a threaded engagement and / or another suitable mechanical and / or adhesive fixing mechanism. Furthermore, the nut 76 includes a threaded through-channel 78 configured for threaded engagement with an externally threaded portion 80 of the core 154, such as the threaded fastener end portion 80 shown. To facilitate screwing the core 154 into the nut 76, the fastener end portion 80 may be provided with a tool receptacle 81, the pocket 81 being configured to engage with any standard tool drive feature known in fastener technology.When screwing the core 154 into engagement with the nut 76, the gap G between the free end of the core 154 and the armature 160 can be adjusted precisely as desired, for example, by screwing the free end of the core 154 in against the armature 160 and then unscrewing and radially pulling the core 154 away from the armature 160 by a predetermined distance, which can be easily derived from knowing the helix angle of the thread on the nut 76 and the core 154. When the core 154 is fixed in its position, it can remain without direct attachment to the coil 158 and the coil former 156 and is thus arranged in a clearance fit, which in turn allows for easy adjustment and replacement of the core 154 as desired, without affecting the coil 158 or the coil former 156.

[0033] On the Fig. 5 and Fig. Referring to Figure 5A, another embodiment of a coupling arrangement 220 is shown, using the same reference numerals plus 200 to identify identical features. In this embodiment, a passage 274 extends directly through the outer wall 272 of the projection 230 to the actuator pocket 232, the passage 274 being configured to radially receive the core 254 of the coil assembly 252. The core 254 of the coil assembly 252 is pressed radially inward into the passage 274 and fixed therein. As a result of the core 254 being fixed in the passage 274, the entire coil assembly 252 is secured in position without providing access to any inner part of the projection 230.In the embodiment shown, the core 254 is dimensioned for a tight fit in the passage 274, although it should be apparent that other mechanisms for fixing the core 254 in the passage 274 in a manner other than an interference fit are conceivable, as discussed above with reference to adhesives, welded joints, mechanical fasteners, and the like. As in . Fig. As shown in 5B, another embodiment similar to the one above is further illustrated with reference to the Fig. 4A and Fig. As discussed in Figure 4B, the same reference numerals plus 300 are used to identify identical features. Instead of fixing the core 354 in direct contact with the opening 374 in the outer wall 372, a nut 376 can be used to facilitate fixing the core 354 of the coil assembly 352 in a precise position relative to the armature 360, thereby creating a precise gap G between them, as desired. The nut 376 is provided with an outer surface 377 configured for fixing in the opening 374, for example, by means of an interference fit and / or an adhesive and / or a welded connection and / or a threaded engagement and / or another suitable mechanical and / or adhesive fixing mechanism.Furthermore, the nut 376 includes a threaded through-channel 378 configured for threaded engagement with an externally threaded portion 380 of the core 354, as shown, for example, as a portion immediately adjacent to the radially outwardly extending coil former 356 and the coil 358. When the core 354 is screwed into engagement with the nut 376, the gap G between the free end of the core 354 and the armature 360 ​​can be formed as described above with reference to the figure. Fig. 4A and Fig. 4B discussed and precisely adjusted. When fixing the core 354 in the nut 376, it should be evident that, unlike the core 354, the remaining part of the coil assembly 352 remains outside the projection 312 and is therefore freely accessible if desired, thus facilitating maintenance of the coil assembly 352.

[0034] On the Fig. 6 and Fig. With reference to Figure 7, in which the same reference numerals plus 400 indicate identical parts in all of the multiple views, a coupling arrangement 420 is shown in general terms. The coupling arrangement 420 includes an outer ring 422 extending circularly around an axis A. The outer ring 422 includes an outer rim 424 having several outer projections 428 extending radially outward for assembly with a first component. The first component can be a stationary component (such as a gearbox housing) or a rotating component (such as a shaft). The outer ring 422 further includes an axially oriented web or surface 427 having a circular shape extending radially inward from the outer rim 424. Several passive locking fingers 446 are pivotably connected to the axial surface 427.A preload spring (not shown) engages each of the passive locking fingers 446 to preload the passive locking fingers 446 into a locked position against an inner ring 436.

[0035] The inner ring 436 extends circularly around the axis A. The inner ring 436 has an outer rim or band 438 and an inner rim or band 440, which are radially spaced apart from each other on opposite sides of the passive locking fingers 446. The inner band 440 of the inner ring 436 has several internal projections 442, which extend radially inward from them for engagement with a second component (generally a rotating component). The inner band 440 of the inner ring 436 also has several passive ratchet teeth 434, which extend radially outward from them for engagement by the passive locking fingers 446 to lock the inner and outer rings 436, 422 together in response to a counterclockwise rotation of the inner ring 436 relative to the outer ring 422. The outer band 438 of the inner ring 436 has several active ratchet teeth 444 extending radially outwards from it and being evenly distributed around the axis A.

[0036] Several active locking finger assemblies 448 are axially connected to the outer ring 422. Each of the active locking finger assemblies 448 includes a generally arcuate projection 430, the projection 430 being a separate piece of material from the outer ring 422. Each projection 430 includes a base 82 and a pair of circumferential flanges 84 extending from the base 82 on opposite sides. A fastening element 85, for example a bolt, extends axially through a through-hole in each of the flanges 84 and is attached to the outer ring 422 to secure the active locking finger assemblies 448 to the outer ring 422. The active locking finger assemblies 448 are arranged one another circumferentially about axis A, as desired.

[0037] The actuator pocket 432 extends axially into the base 82 of each of the active latching finger assemblies 448. A coil assembly 452 is arranged in each of the actuator pockets 432. The coil assembly 452 comprises a core 454 made of magnetically permeable material, a coil former 456 configured to receive the core 454, and a coil 458 wound around the coil former 456. It should be evident that the coil formers 456 and the coils 458 of the coil assemblies 452 can advantageously be easily inserted into their respective actuator pockets 432 for ease of installation.

[0038] Each of the active detent finger arrangements 448 contains an active detent finger 450, which is selectively pivotable between a locked and an unlocked position, as discussed above. In the locked position, the active detent fingers 450 engage the active ratchet teeth 444 of the inner ring 436 and therefore lock the outer and inner rings 422, 436 together when the inner ring 436 moves clockwise relative to the outer ring 422. However, the active detent fingers 450 allow relative displacement, i.e., free rotation, in a counterclockwise direction. In the unlocked position, the active detent fingers 450 are radially spaced from the active ratchet teeth 444, thus allowing the outer and inner rings 422, 436 to rotate relative to each other.

[0039] The multiple passive locking fingers 446 are pivotable between a locked position and an unlocked position. In the locked position, the passive locking fingers 446 engage the active ratchet teeth 434 of the outer ring 422 to connect the outer and inner rings 422, 436 during a counterclockwise rotation of the inner ring 436 relative to the outer ring 422. Therefore, engagement by the passive locking fingers 446 prevents a counterclockwise relative displacement of the outer and inner rings 422, 436; however, the passive locking fingers 446 allow a clockwise relative displacement, i.e., free rotation. In the unlocked position, the passive locking fingers 446 are radially spaced from the passive ratchet teeth 434 of the outer ring 422, thus allowing the inner ring 436 to rotate counterclockwise relative to the outer ring 422.

[0040] Each of the active locking finger assemblies 448 further includes an armature 460, which is arranged between the active locking finger 450 and the core 454 to provide the pivoting movement of the active locking finger 450 in response to an excitation of the coil 458. A punch grid 462, as described above with reference to the Fig. 1 and Fig. As discussed in section 2, the coils 458 are electrically connected to each other in order to excite the coils 458 to actuate and pivot the active locking fingers 450 into their engaged, locked position.

[0041] Accordingly, it should be obvious that the modular configuration of the active locking finger assemblies / coil assemblies 448, 452 allows for the separate manufacture of the active locking finger assemblies / coil assemblies 448, 452 from the rest of the coupling assembly 420. Furthermore, it should be obvious that any number of the active locking finger assemblies / coil assemblies 448, 452 could be installed on any given coupling assembly 420 to provide the required torque level as needed.

[0042] Furthermore, it should be obvious that the modular active latching finger arrangements, as described herein, could be used in various other coupling arrangement configurations.

[0043] It should be obvious that the ability to subject the coil assemblies 52, 152, 252, 352, 452 discussed above to axial or radial loads ensures a simple assembly step during manufacturing and allows the coil assembly 52, 152, 252, 352, 452 to be mounted in the respective actuator pocket 32, 132, 232, 432 before installation. Furthermore, it should be obvious that the aforementioned axially and radially load-bearing pockets / projections could also be used on other coupling assembly configurations.

[0044] On the Fig. Referring to Figures 8-10, in which identical reference numerals plus 500 indicate identical parts in all of the multiple views, an active locking finger arrangement 548, which, as is readily apparent to a person skilled in the art, can be installed in any of the coupling arrangement embodiments discussed herein as well as in others, is received in a locking finger pocket 533 of the outer ring 522. Each of the active locking finger arrangements 548 can be actuated by means of an electromagnetic actuator 551, which comprises a coil arrangement 552, an armature 560, a preload spring 561 and an active locking finger 550.

[0045] The active locking finger 550 comprises a base segment 86 and a locking arm 87. The locking arm 87 extends from the base segment 86 to a locking end or edge 88. The base segment 86 is designed for pivoting movement between a locked position ( Fig. 9) and an unlocked position ( Fig. 8 and Fig. 10) pivotably arranged in the detent finger pocket 533. In the locked position, the locking edge 88 engages the outer ratchet teeth 544 of the inner ring 536, and in the unlocked position, the locking edges 88 are radially spaced from the outer ratchet teeth 544 of the inner ring 536. The preload spring 561 is arranged in the detent finger pocket 533 and extends between the base segment 86 and a base or bottom of the detent finger pocket 533 to preload the detent finger 550 into the unlocked position.

[0046] The coil arrangement 552 includes a core 554 made of a magnetically permeable material, which is arranged through a central channel of a coil body 556, wherein at least one coil 558 is wound directly onto the coil body 556 and thus around the core 554 in order to focus the magnetic flux generated by the coil 558 onto the core 554.

[0047] The armature 560 extends between a first end 90, which is seated in an armature section 91 of the actuator pocket 532 for pivoting movement, and a second end 92, which extends into the detent finger pocket 533 in engagement with the base segment 86 of the detent finger 550. The armature 560 has forked legs 93, which form a channel between them. This channel is dimensioned to receive a reduced-width section of the detent finger 550 with a clearance fit, each leg 93 extending along opposite sides of the detent finger 550. The first end 90 of the armature 560 is pivotably arranged about a pivoting carrier 94 in the armature section 91 of the actuator pocket 532 to pivot radially to and away from the core 554 between an actuated position and an unactuated position in response to excitation of the coil 558.In the actuated position, the armature 560 is drawn towards the core 554, whereupon the legs 93 drive the locking finger 550 into the locked position by engaging the base segment 86. In the unactuated position, the armature 560 is spaced from the core 554, allowing the preload spring 561 to bias the locking finger 550 into the unlocked position. The armature 560 has an upper curvature 95 in each leg 93 and a lower curvature 96 adjacent to a mounting area of ​​the legs 93, such that the upper and lower curvatures 95, 96 are located between the first end 90 and the second end 92.

[0048] Particularly when the clutch assembly 520 is used on motor vehicle components, it is important that the detent fingers 550 engage the outer ratchet teeth 544 of the inner ring 536 only when the coil assembly 552 is energized to deliberately move the detent fingers 550 into the locked position. Therefore, resistance to inertial loading (high acceleration forces in certain directions in addition to simple gravity) is important for the operation of the clutch assembly 520. The most common method to counteract high inertial loading is to use a preload spring 561 with a higher force. While this method is a short-term solution, it has disadvantages.One of the disadvantages is the increased resistance exerted by the preload spring 561 during normal operation. This necessitates larger dimensions and a greater thickness of the armature 560 and / or the coil assembly 552 to generate the required increased magnetic forces to overcome the increased spring force exerted by the larger preload spring 561. To accommodate such larger components, the pockets 532 and 533 may also need to be larger, thereby increasing the overall size and weight of the clutch assembly 520.

[0049] As an alternative solution for increasing the dimensions of the aforementioned components / arrangements, the generally central part of the locking finger 550, which extends between the legs 93 of the anchor 560, includes projections 97 having a generally triangular cross-section extending longitudinally along a portion of the locking arm 87. The projections 97 extend outward from the central part of the locking arm 87, overlapping each other and extending from one leg 93 to the other. Each projection 97 converges and terminates at a generally sharp edge 98. Furthermore, the upper curvature 95 in the legs 93 of the anchor 560 defines or provides a shoulder 99.The shoulders 99 are configured to engage with the edges 98 of the projections 97 of the locking finger 550, restricting the locking finger 550 from movement in the locked direction unless otherwise actuated by excitation of the coil assembly 552. Thus, the deliberate engagement of the projections 97 with the shoulders 99 during the application of inertial forces causes the upward rotation of the locking finger 550 to be stopped, thereby preventing engagement of the outer ratchet teeth 544 of the inner ring 536 with the locking edge 88 of the locking finger 550 (as best described in ). Fig. 10 shown).

[0050] Fig. Figure 8 represents a non-excited position of the coil 558, with the locking finger 550 in the unlocked position. Furthermore, Fig. 9 represents an excited position of the coil 558, which causes the locking finger 550 to pivot into the locked position, as intended. Fig. Figure 10 shows the situation in which a high inertial load is applied to the coupling assembly 520 in a radially inward direction (as indicated by the arrow). In this situation, the armature 560 rotates slightly clockwise under the inertial load, but the locking finger 550 is intentionally blocked and prevented from rotating further counterclockwise due to the tight fit formed between the adjacent shoulder 99 of the armature 560 and the locking edges 98 of the projections 97. Therefore, the tight fit between the edges 88 of the projections 97 and the shoulders 99 of the armature 560 greatly increases the force required to move the locking finger 550 against the outer ratchet teeth 544 of the inner ring 536, but does not increase the load height required by the armature 560 / coil assembly 552 to pivot the locking finger 550 as controlled and intended.

[0051] It should be obvious that the projections 97 of the locking fingers 550 and the shoulders 99 of the anchor 560 could also be used on other active locking finger arrangement configurations to counteract a high inertial load.

[0052] Now to the Fig. Referring to 11-14, a coupling arrangement 600 is generally shown to be a modified version applicable to any bidirectional coupling arrangement 20 ( Fig. 1-3), 120 ( Fig. 4), 220 ( Fig. 5A), 420 ( Fig. 6-7) and 520 ( Fig. 8-10) and, in particular, can be applied to the controllable freewheel clutch associated with each alternative embodiment. Specifically, the clutch assembly 600 includes a controllable freewheel clutch in which several disengagement prevention features are integrated. These features are designed to counteract and minimize / prevent the unintentional disengagement of the active detent finger due to hydraulic effects acting upon it as a result of fluid in the transmission and / or in the clutch assembly 600. The features for preventing hydraulic disengagement, to be described below, are also applicable to passive freewheel clutches for the same purpose, and it is readily apparent to those skilled in the art that these features can be easily integrated into any detent finger freewheel clutch or freewheel clutch rocker.Although each of the above coupling arrangements includes an active detent finger arrangement configured to use an armature for extending the active detent fingers upon actuation of the electromagnetic actuator, the features for preventing hydraulic extension of the present disclosure are equally applicable to controllable freewheel couplings having configurations for a “direct” detent finger actuation, as well as to other types of movable locking elements used in place of detent fingers.

[0053] The coupling assembly 600 includes an outer ring 602 extending around an axis A. The outer ring 602 comprises an outer rim segment 604, an inner rim segment 606, and a plate segment 608 between them. Projections 610 formed on the outer rim segment 604 are provided for assembly with a first component. As mentioned, the first component can be a stationary gearbox housing or a rotating component, such as a shaft. Furthermore, the outer rim segment 604 includes one or more actuator projections 612, which define an actuator pocket 614, an anchor pocket 616, and a detent finger pocket 618. Finally, the inner rim segment 606 includes several ramped inner ratchet teeth 620 that extend inwards and are evenly distributed around the axis A.

[0054] Although the coupling assembly 600 is shown only schematically, it also includes an inner ring 624 that extends around axis A. The inner ring of the coupling assembly 600 is to be understood as being generally similar in structure and function to the inner ring 36 of the coupling assembly 20. Thus, the inner ring 624 has an outer rim segment arranged radially between the outer and inner rim segments 604, 606 of the outer ring 602, and an inner rim segment arranged radially inward from the inner rim segment 606 of the outer ring 602. The inner rim segment of the inner ring 624 has internal torque transmission structures (i.e., projections or splined teeth) for meshing with the second component. Finally, the outer rim segment of the inner ring 624 includes several ramped outer ratchet teeth that extend radially outward and are evenly distributed around axis A.

[0055] A passive freewheel clutch (not shown) is associated with the clutch assembly 600 and again contains several passive locking fingers, which are pivotably supported by the inner ring 624. The passive locking fingers are movable to engage the inner ratchet teeth 620 on the inner ring segment 606 of the outer ring 602. As before, the passive locking fingers are configured to engage the inner ratchet teeth 620 to prevent relative rotation between the outer ring 602 and the inner ring 624 in a first (locking) direction, while allowing relative rotation between them in a second (freewheeling) direction.

[0056] The controllable freewheel clutch 630 associated with the bidirectional clutch assembly 600 includes an active detent finger assembly 632, which is received in each actuator projection 612 of the outer ring 602. Each active detent finger assembly 632 comprises an active detent finger 634, an armature 636, and an electromagnetic actuator 638. Each active detent finger 634 is pivotably supported in the detent finger pocket 618 for movement between a locked (disengaged) and an unlocked (disengaged) position with respect to the ramped outer ratchet teeth formed on the outer edge segment of the inner ring 624. In the locked position, an engagement end 634a of the active detent fingers 634 is pivoted into a position with respect to the outer ring 602 such that it engages the outer ratchet teeth on the inner ring 624 to establish the locked clutch mode.The engagement end 634a of the active locking fingers 634, however, is radially displaced and disengaged from the outer ratchet teeth on the inner ring 624 when they are in their unlocked position in order to establish the unlocked clutch mode.

[0057] Each armature 636 is pivotably supported in the armature pocket 616 of the actuator cantilever 612 and is mechanically connected to a corresponding active locking finger 634. When the armature 636 is in a taut position relative to the actuator 638, the active locking finger 634 is in its extended position. Conversely, positioning the armature 636 in a non-tightened position relative to the actuator 638 results in the active locking fingers 634 being positioned in their disengaged positions. A return spring 640 is held by the outer ring 602 and acts on a rear end 634b of each active locking finger 634, biasing the active locking finger 634 in its disengaged position, thereby biasing the armature 636 in a non-tightened position. Alternatively, the return spring 640 could act directly on the armature 636.The electromagnetic actuator 638 is supported in the actuator pocket 614 of the actuator cantilever 612 and has a coil assembly that is radially spaced from the armature 636 and the detent finger 634. As before, the coil assembly comprises a core made of magnetically permeable material, a coil former surrounding the core, and a coil wound around the coil former. As is known, excitation of the coil assembly creates a magnetic attraction between the core and the armature 636, which causes the armature 636 to pivot into its engaged position and the detent finger 634 to move against the bias of the return spring 640 into its extended position.

[0058] According to aspects of the present invention, several differentiated features for preventing ejection are assigned to the outer ring 602 and / or the active locking finger 634 and / or the armature 636. These features are configured to prevent unintentional (i.e., non-excitation-induced) ejection of the active locking fingers 634 by overcoming and counteracting the fluid dynamics and flow characteristics of the fluid acting on and around the active locking finger assemblies 632, cumulatively referred to as "hydraulic ejection." Unintentional hydraulic ejection is a condition in which the locking finger is moved from its non-ejected position to its ejected position by a pressure gradient acting upon it.This pressure gradient, together with the fluid dynamics associated with the rotation of the inner ring 624 relative to the outer ring 602, results in a force vector acting on the engagement end 634a of the active locking fingers 634. As the hydraulically induced force acting on the end 634a of the active locking fingers 634 increases, it eventually overcomes the preload force exerted by the return spring 640. This leads to an unintended pivoting movement of the active locking fingers 634 into their extended position, while the electromagnetic actuator 638 remains in the unenergized state. Thus, the coupling arrangement 600 acts as an inefficient fluid pump.

[0059] One solution to this undesirable pumping behavior is to add anti-discharge features that divert or redirect fluid flow from sensitive areas of the switchable freewheel clutch 630, or reduce the fluid pressure in other areas, thereby reducing the hydraulic discharge force exerted on the active locking fingers 634 by the fluid movement associated with the freewheeling of the inner ring 624 relative to the outer ring 602. To this end, several modifications and / or features have been added to the various components of the switchable freewheel clutch 630. The following description of each feature is given in no particular order, relevance, or functionality.

[0060] According to a first anti-deployment feature, an elongated flow channel 650 formed in a plate segment 608 of the outer ring 602 is shown. Although the flow channel 650 is aligned along axis A in the illustration and generally runs symmetrically with respect to a center line of the electromagnetic actuator 638, these are merely non-limiting examples used to illustrate a suitable embodiment. Possible alternatives include, without limitation, modifying the length of the flow channel 650, its symmetry, its depth (constant or variable), and its width. Such variations are all intended to prevent pressure build-up or to release pressure from the high-pressure area to the low-pressure area of ​​the coupling 630.Furthermore, this flow line 650 acts on fluid flowing radially outwards towards the active locking finger arrangement 632, in particular on fluid located between the outer ring segment 604 and the inner ring segment 606 of the outer ring 602.

[0061] According to a second anti-deployment feature, a ramp-shaped flow cam structure 660 is formed on an inner wall surface 662 of an outer ring segment 604 of the outer ring 602. This flow cam structure 660 is best used in Fig. Figure 14 shows a raised surface segment 664 connected to the inner wall surface 662 via a ramped surface segment 666. The length and surface configuration (i.e., arcuate, planar, constant radius, or variable) of the raised surface segment 664 and / or the cam surface segment 666 connected to the flow cam structure 660 can be varied. This feature is configured to eliminate a squish point between the inner ring 624 and the outer ring 602, which resulted from a fluid damping effect associated with fluid in and around the coil pocket 614 and caused localized fluid pressure near and around the active detent finger 634.

[0062] According to a third anti-ejection feature, one or more flow guides, also referred to as spoilers 670, are formed in the edge surface 634c at the engagement end 634a of the active locking fingers 634. The active locking finger 634 is best installed in the Fig. 13 and Fig. Figure 14 shows a pair of leg sections 634d, 634e, which are connected via a crossbeam section 634f at the engagement end 634a and via a pivot beam section 634g at the pivot end 634b. Fig. 13 and Fig. Figure 14 shows a pair of ramp-shaped spoilers 670 with greatest depth at the edge surface 634c, converging towards the leg sections 634d, 634e. The length, width, taper, position, number, and / or profile of these flow spoilers 670 can be varied to meet any suitable requirements. In particular, the spoilers 670 act to force oil over the engagement end 634a of the active locking fingers 634 to assist in holding the active locking fingers 634 in their retracted, disengaged position. These flow channels in the active locking fingers 634 act as spoilers insofar as they assist a radial fluid force to assist the return spring 640 in holding the active locking fingers 634 in the disengaged position. Fig. 12 contains an elongated arrow 680, which shows that the combination of these three (3) anti-ejection features is configured to redirect the oil flow over the tips of the active locking fingers 634 and thereby push them towards the coil pocket.

[0063] Those with the Fig. 11-14 associated concepts according to the invention are of crucial importance for the optimization of the main performance of these freewheel clutches or clutch rockers and are aimed at minimizing the susceptibility to unintentional hydraulic detent finger deployment.

[0064] Now on Fig. 15 With reference to this, a coupling arrangement 600A is shown, which is a slightly modified version of the one described in the Fig. The coupling assembly 600 shown in Figures 11-14 is included. The coupling assembly 600A incorporates a controlled freewheel coupling 630A, which integrates several disengagement prevention features. These features, as mentioned above, are designed to minimize / prevent the unintentional disengagement of the active detent finger 634 resulting from the hydraulic effects of the fluid acting upon it due to fluid flow in the transmission and / or the coupling assembly 600A. In general terms, the coupling assembly 600A is configured to incorporate one or more of the features associated with the coupling assembly 600. Fig. References 11-13 disclose three (3) features for preventing hydraulic discharge, combined with an additional (hereinafter referred to as the “fourth”) anti-discharge feature. Due to the similarity of most components of the coupling assembly 600A to the components previously listed in detail in connection with the coupling assembly 600, common reference numerals are used below to identify the same components.

[0065] The controllable freewheel clutch 630A associated with the bidirectional clutch assembly 600A includes an active locking finger assembly 632, which is received in each actuator projection 612 formed in the outer ring 602. As before, each active locking finger assembly 632 includes an active locking finger 634, an armature 636, and an electromagnetic actuator 638. Each active locking finger 634 is pivotably supported in the locking finger pocket 618 for movement between a locked (extended) and an unlocked (disengaged) position with respect to the ramped outer ratchet teeth formed on the outer edge segment of the inner ring 624.As can be seen, in this non-restrictive embodiment, the controllable freewheel clutch 630A includes the following: (a) the first anti-disengagement feature mentioned above, configured as an elongated flow channel 650 formed in the plate segment 608 of the outer ring 602; (b) the second anti-disengagement feature mentioned above, configured as a ramped cam structure 660 formed on the outer rim segment 604 of the outer ring 602; and (c) the third anti-disengagement feature mentioned above, configured as a pair of flow channels or “spoilers” 670 formed in the edge surface 634c at the engagement end 634a of the active locking fingers 634. As mentioned previously, the specific dimensions of each of these anti-disengagement features can be modified to meet specific fluid flow and disengagement requirements associated with the clutch assembly 600A.

[0066] According to the fourth anti-dispersal feature, Fig. Figure 15 shows a pair of elongated flow channels 650 formed in the cam structure 660, which are directed towards spoilers 670 formed in the active locking fingers 634. The flow channels 650 are designed to optimize the fluid flow directed into the spoilers 670 and thus increase the force exerted on the engagement end 634a of the active locking fingers 634, which in turn presses the active locking fingers 634 into their disengaged position. The length, width, and depth of the flow channels 650 can be varied, as can their profile (i.e., rectangular or cylindrical) to provide an optimized fluid flow directed into the spoilers 670. Although both flow channels 650 have an identical configuration in the illustration, the present embodiment provides alternative arrangements that employ non-identical configurations for the flow channels 650.

[0067] Fig. 16 represents another version of a bidirectional coupling arrangement 600B, which has a controllable freewheel coupling 630B, which is the freewheel coupling 630A of the bidirectional coupling arrangement 600A of Fig.15 is generally similar, except that a single flow channel 650' is formed in the ramped cam structure 660, which is directed towards a single spoiler 670' formed in the active locking finger 634. As before, the use of this fourth anti-disengagement feature, together with the second anti-disengagement feature (the ramped cam structure 660) and the third anti-disengagement feature (the spoiler 670'), promotes an improved / enhanced fluid flow, directed in particular towards the engagement end 634a of the active locking fingers 634, to assist in holding the active locking fingers 634 in their unlocked / non-disengaged position. It should be noted that the coupling arrangement 600B is also configured to include the first anti-disengagement feature comprising the flow channel 650. Reference symbol list 20, 120, 220, 420, 520, 600, 600A, 600B coupling arrangement 22, 422, 522, 602 Outer ring 24, 424, 604 outer wreath segment 26, 606 inner wreath segment 27, 427 radial web segment, radial surface 28, 428, 610 external approaches 29, 77, 377 outdoor area 30, 130, 230, 312, 430, 97 lead 32, 132, 232, 432, 532, 614 Actuator pocket 33, 533, 618 Rastfinger pocket 34, 434, 620 inner ratchet teeth 35 open side surface 36, 436, 536, 624 inner ring 38, 438 outer edge, outer band 40, 440 inner edge 41 radial bridge segment 42, 442 internal approaches 44, 444, 544 outer ratchet teeth 46, 446 passive locking fingers 48, 448, 548, 632 Latching finger arrangement 50, 450, 550, 634 active detent fingers 51, 551, 638 Actuator 52, 152, 252, 352, 452, 552 coil arrangement 54, 154, 254, 354, 454, 554 core 56, 156, 456, 556 coil formers 58, 158, 458, 558 coil 60, 160, 360, 560, 636 anchors 61, 640 Return spring 62,462 punch grids 64 Printed circuit board (PCB) 66 Power output contact 68 Wiring harness 70 plastic housings 72, 172, 272, 372 Exterior wall 74, 174, 274, 374 Through channel, passage 75 mm interior surface 76, 376 hollow adapter plug, nut 78, 378 threaded through channel 80, 380 externally threaded part, fastening element end part 81 Tool storage bag 82 base 84 flange 85 Fastening element 86 Base segment 87 Locking arm 88 Blocking edge, blocking margin 90 first end 91 Anchor section 92 second end 93 thighs 94 swivel brackets 95° upper curvature 96 lower curvature 98 sharp edge 99 Shoulder 561 Preload spring 608 plate segment 612 Actuator cantilever 614 Spool bag 616 Anchor Bag 630, 630A, 630B Freewheel clutch 634a End of intervention 634b rear end 634c Edge area 634d, 634e thigh sections 634f Crossbeam section 634g swivel bracket section 650, 650' Flow line 660 Flow cam structure 662 interior wall area 664 raised surface segment 666 ramp-shaped surface segment, cam surface segment 670, 670' Spoiler 680 Oil flow direction Axis G gap

Claims

[1] Freewheel clutch (630, 630A, 630B) for use in a power transmission device with hydraulic fluid, wherein the freewheel clutch (630, 630A, 630B) comprises: a coupling arrangement (20, 120, 220, 420, 520, 600, 600A, 600B) with an inner ring (36) and an outer ring (22) rotatable with respect to the inner ring (36), wherein the outer ring (22) has several locking structures consisting of inner ratchet teeth (34) and outer ratchet teeth (44); and a ratchet finger arrangement (48, 448, 548, 632) with an active ratchet finger (50) which allows movement between a first position displaced from engagement with the inner ratchet teeth (34) and outer ratchet teeth (44), defining a free-running mode, and a second position engaged with the inner ratchet teeth (34) and outer ratchet teeth (44), defining a locked mode by which the inner ring (36) is supported, wherein the inner ring (36) and / or the active locking finger (50) has / have an anti-ejection feature configured to assist in holding the actuator element in its first position during a rotation of the outer ring (22) relative to the inner ring (36) by counteracting hydraulic forces applied by the hydraulic fluid to the active locking finger (50), characterized by , that the anti-ejection feature counteracts the hydraulic forces applied to the active locking finger (50) by diverting the fluid to flow in a path configured to push the active locking finger (50) into its first position. [2] Freewheel clutch (630, 630A, 630B) according to claim 1, wherein the anti-disengagement feature is a flow guide (650, 650') formed at a location between the inner ratchet teeth (34) and outer ratchet teeth (44) on the outer ring (22) and the active locking finger (50) in the inner ring (36). [3] Freewheel clutch (630, 630A, 630B) according to claim 1, wherein the anti-disengagement feature is at least one flow line (650, 650') formed in the active locking finger (50). [4] Freewheel clutch (630, 630A, 630B) according to claim 1, wherein the anti-disengagement feature is a ramp-shaped surface (666) formed on the inner ring (36) and configured to direct the hydraulic fluid to act on the active detent finger (50) to force the active detent finger (50) into its first position. [5] Freewheel clutch (630, 630A, 630B) according to claim 1, wherein the anti-disengagement feature is a flow line (650, 650') formed in the inner ring (36) which is configured to direct the hydraulic fluid to act on the active locking finger (50) in order to force the active locking finger (50) into its first position. [6] Freewheel clutch (630, 630A, 630B) according to claim 1, wherein the anti-disengagement feature comprises a first anti-disengagement feature and a second anti-disengagement feature which cooperate to direct the hydraulic fluid to flow over the active locking finger (50) and to push the active locking finger (50) into its first position. [7] Freewheel clutch (630, 630A, 630B) according to claim 6, wherein the first anti-disengagement feature is a flow guide (650, 650') formed at a location between the inner ratchet teeth (34) and outer ratchet teeth (44) on the outer ring (22) and the active locking finger (50) in the inner ring (36), and wherein the second anti-disengagement feature is a ramp-shaped surface (666) formed on the inner ring (36) and configured to direct the hydraulic fluid to act on an end part of the active locking finger (50). [8] Freewheel clutch (630, 630A, 630B) according to claim 7, wherein the anti-disengagement feature further comprises a third anti-disengagement feature which interacts with the second anti-disengagement feature to direct fluid to act on the end part of the active locking finger (50). [9] Freewheel clutch (630, 630A, 630B) according to claim 8, wherein the third anti-release feature is configured to include at least one flow line (650, 650') formed in the end part of the active locking finger (50). [10] Freewheel clutch (630, 630A, 630B) according to claim 9, wherein the anti-release feature includes a fourth anti-release feature which interacts with the third anti-release feature. [11] Freewheel clutch (630, 630A, 630B) according to claim 10, wherein the fourth anti-release feature is configured to include at least one flow line (650, 650') formed in the ramp-shaped surface (666) on the inner ring (36), and which is arranged to direct fluid to the at least one flow line (650, 650') formed in the end part of the active locking finger (50). [12] Freewheel clutch (630, 630A, 630B) according to claim 11, wherein a pair of the flow lines (650, 650') is formed in the inner ring (36) and is aligned with a pair of the flow lines (650, 650') formed in the end part of the active locking finger (50).

Images