Clutch assembly and free-running clutch and control assembly
Patent Information
- Authority / Receiving Office
- DE · DE
- Patent Type
- Patents
- Current Assignee / Owner
- MEANS IND INC
- Filing Date
- 2019-10-23
- Publication Date
- 2026-07-09
AI Technical Summary
Existing high-speed clutches experience significant frictional forces at high rotational speeds, leading to strut instability and premature wear, which affects durability and efficiency.
Incorporation of bearings, such as thrust or roller bearings, between the locking member and the pocket wall to reduce the coefficient of friction, allowing for pivotal movement with reduced frictional forces.
The implementation of bearings significantly reduces friction, enhancing the durability and efficiency of high-speed clutches by minimizing strut instability and wear, even at high rotational speeds.
Abstract
Description
CROSS-REFERENCE TO RELATED REGISTRATIONS
[0001] This application claims the benefit of the preliminary US application filed on October 23, 2018, under serial number 62 / 749,165, the disclosure of which is hereby incorporated herein in its entirety by reference. TECHNICAL AREA
[0002] This invention relates generally to high-speed, free-running coupling and control assemblies, coupling assemblies and locking parts that pivot with significantly reduced friction. Overview
[0003] As described in U.S. Patent No. 6,571,926, entitled “One-Way Clutch Assembly Featuring Improved Strut Stability,” which has been assigned to the assignee of the present application, clutches are used in a wide range of applications to selectively couple energy from a first rotatable “driving” part, such as a drive disk or plate, to a second, independently rotatable “driven” part, such as a driven plate or disk. In a known range of clutches, commonly referred to as “one-way” or “freewheeling” clutches, the clutch engages to connect the driving part to the driven part only when the driving part tends to move in a first direction with respect to the driven part.Once engaged, the clutch will only disengage or decouple the driven part from the driving part if the driving part rotates in a second, opposite direction relative to the driven part. Otherwise, the clutch allows the driving part to rotate freely in the second direction relative to the driven part. This "free-running" of the driving part in the second direction relative to the driven part is also known as a "free-running" state.
[0004] Such a known one-way coupling employs adjacent, nominally coaxial driving and driven parts, which generally have planar coupling surfaces in close axial proximity. Such "planar" one-way couplings typically include, as taught by Frank in U.S. Patent No. 5,449,057 and Ruth et al. in U.S. Patent No. 5,579,057, several recesses formed in the surface of the driving part and at least as many recesses formed in the surface of the driven part. A thin, flat strut is held in each of the recesses of the driving part such that a first longitudinal end of each strut can easily engage and rest against a shoulder defined by its respective recess in the driving part.The second, opposite longitudinal end of the strut is pressed towards and against the surface of the driven part, for example, by a spring located below the strut in the recess of the driving part.
[0005] When the driving part rotates in the first direction relative to the driven part, the second end of at least one strut engages and rests against a shoulder defined by a recess in the driven part, thereby compressing the strut and connecting the driven part to the driving part for rotation. When the driving part rotates in the second direction relative to the driven part, rising surfaces defined by other sections of the recesses in the driven part press the second end of each strut backward toward the driving part, allowing the driving part to rotate in the second direction relative to the driven part.
[0006] The clearance angle of the outer pocket wall can significantly affect the strut deposition rate. Angles greater than zero degrees tend to increase the deposition rate, while negative angles can be used to decrease it. However, this represents a trade-off in manufacturing complexity; higher clearance angles generally result in lower manufacturing costs because they can extend the service life of the press used to produce the pocket plate. Conversely, zero or negative clearance angles are more difficult to manufacture and usually require a secondary machining operation.
[0007] Published US application no. 2011 / 0297500 (which is also allocated to the assignee of the present application) provides a dynamic intervention analysis of a strut within its respective pocket, with various forces acting on the strut being represented and described as follows:
[0008] F R = the resulting strut force. The force available to push the strut out of its pocket (i.e., the force acting on the strut).
[0009] F S = Spring force. The force generated by a spring used to push the strut out of its pocket to engage with the notch plate.
[0010] F C = Centrifugal force. The effective weight of the strut due to rotation of the pocket plate during operation (strut force against pocket plate wall). This is a fictitious force that depends on the observer's frame of reference.
[0011] F F = Frictional force. This force is generated by the effective weight of the strut (centrifugal force) acting on the pocket plate. The higher the rotational speed, the greater the frictional force. This force prevents the strut from being forced out of its pocket.
[0012] F P = Strut push-out force. The angle of the pocket plate wall causes the strut to be pushed out of the pocket plate. This results from the centrifugal force generated by the rotation of the pocket plate.
[0013] F L = Fluid force. This force is generated by the action of the strut displacing the transmission fluid when engaging the notch plate.
[0014] As described in the aforementioned application, a "truly vertical" or "slightly negative" vertical wall improves the stability of a strut or rocker arm (collectively referred to as "locking parts") that experiences rotational centrifugal forces during freewheeling. Furthermore, the "slightly negative" angle reduces the rotational speed at which a strut "locks" due to such centrifugal forces.
[0015] In other words, performance is increased when a pocket plate wall is machined vertically or slightly negatively, as opposed to a cast, positively angled surface which may have a taper such as 1 to 2 degrees or 0.5 to 1 degree (i.e. the surface is angled 'slightly positively').
[0016] U.S. Patent No. 5,927,455 discloses a bidirectional free-running pawl clutch. U.S. Patent No. 6,244,965 discloses a planar free-running clutch for torque transmission. U.S. Patent No. 6,290,044 discloses a selectable one-way clutch assembly for use in an automatic transmission. U.S. Patents No. 7,258,214 and 7,484,605 disclose a free-running clutch assembly. U.S. Patent No. 7,344,010 discloses a free-running clutch assembly. U.S. Patent No. 7,484,605 discloses a free-running radial clutch assembly or clutch.
[0017] Other related US patent publications include: 2015 / 0014116; 2016 / 0377126; 2011 / 0183806; 2011 / 0233026; 2011 / 0214962; 2010 / 0252384; 2010 / 0230226; 2010 / 0063693; 2010 / 0200358; 2009 / 0098970; 2009 / 0194381; 2008 / 0223681; 2008 / 0110715; 2008 / 0169166; 2008 / 0185253; 2006 / 0185957; and the following US patents with the numbers 7,942,781; 8,079,453; 7,967,121; 7,992,695; 8,051,959; 8,011,464; 8,042,669; 8,061,496; 8,042,670; 8,056,690; 8,083,042; 8,087,502; 7,824,292; 7,743,678; 7,491,151; 7,464,801; 7,448,481; 7,455,156; 7,661,518; 7,349,010; 7,275,628; 7,256,510; 7,233,298; 7,198,587; 7,100,756; 7,093,512; 6,953,409; 6,896,111; 6,814,201; 6,503,167; 6,193,038; 6,116,394; 6,186,299; 6,571,926; 4,050,560; 5,638,929; 5,362,293; 5,678,668; 5,918,715; 5,070,978; 5,964,331 and 9,188,170.
[0018] For the purposes of this application, the term "coupling" should be interpreted as including clutches or brakes, wherein one of the plates is driveably connected to a torque-transmitting element of a transmission and the other plate is driveably connected or anchored to another torque-transmitting element and held stationary with respect to a transmission housing. The terms "coupling", "clutch", and "brake" may be used interchangeably.
[0019] A "moment of force" (often simply called moment) is the tendency of a force to twist or rotate an object. Mathematically, a moment is defined as the product of the force and the force arm. The force arm is the perpendicular distance from the point or axis of rotation to the line of action of the force. The moment can be understood as a measure of the tendency of a force to cause a rotation about an imaginary axis through a point.
[0020] In other words, a "moment of force" is the rotational effect of a force about a specific point or axis, measured by the product of the force and the perpendicular distance of that point from the line of action of the force. Generally, clockwise moments are called "positive" moments, and counterclockwise moments are called "negative" moments. If an object is balanced, then the sum of the clockwise moments about a pivot point is equal to the sum of the counterclockwise moments about the same pivot point or axis.
[0021] Metal injection molding (MIM) is a metalworking process in which finely powdered metal is mixed with a measured amount of a binder to create a raw material that can be processed by plastic processing equipment in a process known as injection molding. This molding process allows for the production of complex parts in a single operation and in high volumes. The end products are generally component parts used in various industries and applications. The properties of the MIM raw material stream are defined by a physics called rheology. Current equipment capabilities dictate that processing is limited to products that can be formed using typical volumes of 100 grams or less per shot.Rheology allows this "injection" to be distributed into multiple cavities, making it cost-effective for small, complex products in high volumes that would otherwise be quite expensive to manufacture using alternative or conventional methods. The variety of metals that can be used in a MIM raw material is referred to as powder metallurgy, and these contain the same alloying elements found in industry standards for common and exotic metal applications. Subsequent processing operations are carried out on the formed mold, removing the binder material and fusing the metal particles to the desired state for the metal alloy.
[0022] Fig. Figure 1 is a top view of a locking part or strut, which is designated by 10 and is in a pocket. 12 a coupling surface 14a coupling component generally designated as 16, such as a pocket plate, is received and nominally held. At high speeds, such as 2000 rpm and above, the strut locks. 10 on exterior walls 18 the bag 12 due to centrifugal friction effects as reaction forces F R1 and F R2 , which are located at a relatively large distance from an axis of engagement 20 the strut 10 are removed. Consequently, the total movement that must be overcome to move the strut is 10 with regard to a second coupling part (not shown in Fig. 1, but shown in many of the other figures), such as a notched plate, to bring in and out of engagement, quite large.
[0023] Fig. 2 represents a locking part or strut, generally designated 22, which transmits a moment between a first and second coupling part. As described in U.S. Patent No. 9,121,454, the first coupling part can 24 a pocket plate that can rotate either clockwise or counterclockwise (as indicated by 29) around the axis of rotation (not shown) of the assembly and has a generally flat, annular coupling surface 30 containing several pockets, generally specified as 32, each of which is dimensioned and shaped to include a locking part, such as the locking part 22 , to take in and hold nominally. The pockets 32 are around the axis of the assembly 28 spaced around. The surface is oriented so that it faces axially in a first direction along the axis of rotation of the assembly.
[0024] The second coupling part (not shown) can be a notched plate and has a generally flat, annular second coupling surface that corresponds to the first surface. 30 The second surface is oriented in the opposite direction and such that it faces axially in a second direction opposite to the first, along the axis of rotation of the assembly. The second surface has several locking configurations defined by the locking elements. 22 when jumping out of the pockets 32 Intervention is required to prevent a relative rotation of the first and second parts with respect to each other in at least one direction around the axis of the assembly.
[0025] The locking part 22 has a first end surface that engages a part 34 , a second end surface that engages a part 36 and an elongated main body section 38 between the end surface 34 and 36open. The locking part 22 also features a protruding inner or outer pivot pin 40 or 42 on, which extend laterally from the main body section 38 extend to allow a pivoting movement of the locking part 22 around a pivot axis 44 of the locking part 22 to enable which the pivot pins 40 and 42 cuts. The end surface 34 and 36 of the locking part 22 are movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thereby enabling a one-way torque transmission between the coupling parts in the engaged positions of the coupling parts. 22 can take place.
[0026] In general, the pivot pins 40 and 42 with regard to the main body section 38dimensioned, shaped and arranged in such a way that frictional engagement of an end surface 45 of the outer pivot pin 42 with an outer wall of the bag 32 near the pivot axis 44 during a rotation of the first clutch part 24 and the retained locking part 22 can take place above a predetermined rotational speed, thereby increasing the total torque at the locking part 22 around the pivot axis 44 around is significantly reduced, which must be overcome to access the locking part. 22 to move between its positions in engagement and out of engagement.
[0027] The assembly also includes an opening retaining element or an opening retaining plate, which is mounted between the first and second coupling parts. The retaining element has at least one element extending completely through it to connect it to the locking parts or struts.22 to allow it to extend through this and lock the first and second coupling parts together. The upper surfaces of the pivot pins 40 and 42 pivot against the underside of the mounting plate during such a movement.
[0028] The total or net torque at the locking part 22 is during the pivoting movement of the locking part 22 negative from the position outside of the intervention to the position in the intervention.
[0029] The total or net torque at the locking part 22 is during the pivoting movement of the locking part 22 positive change from the position in intervention to the position out of intervention.
[0030] The inner pivot pin 40 is notched, as indicated by 48, to allow frictional engagement of a side surface of the notched inner pivot pin 40with an interior wall 52 the bag 32 to allow and a rotation of the locking part 22 in the bag 32 to prevent the outer pivot pin 42 can be notched in the same way, so that the locking part 22 It can be used either as a forward locking part or as a backward locking part.
[0031] The center of gravity (i.e., CG) of the locking part 22 is located in the main body section 38 and from the pivot axis 44 removed.
[0032] Friction is the force that opposes the relative motion or tendency of such motion between two surfaces in contact. The coefficient of friction (also known as the friction coefficient) is a dimensionless numerical value that describes the ratio of the frictional force between two bodies to the force pressing them together.
[0033] As in the published US patent applications 2018 / 0010651 and 2018 / 00384245 As eCMDs (electrically controlled mechanical diodes) are increasingly accepted as a viable technology for advanced hybrid powertrains and electric vehicles, the technical guidelines and requirements for clutches are rapidly increasing. A characteristic of electric motors is their high torque at zero / low speed, with the ability to rotate three times faster than a conventional internal combustion engine (ICE) application. eCMDs must be able to engage and disengage at speeds of at least 15,000 rpm. The formula for the radial force generated by rotation is: F C =MV 2 / r
[0034] The radial force increases with the square of the speed. For example, a strut in a clutch, weighing 4.17 grams, rotates at 15,000 RPM, resulting in a radial force of 151 US pounds on the strut within its pocket. These are the new realities that eCMD designers now face. The eCMD's control system (the electromechanical section) must be able to rotate the strut in the presence of these enormous radial forces. The outer wall of the pocket plate does not react to these radial forces. A frictional force is generated, creating a torque opposing the desired rotation of the strut. The frictional force equation (formula) is: F f = μ N , worin N gleich F and μ der Reibungskoeffizient ist
[0035] The equation for the opposite moment is: M=F f r <?page 6=""?>
[0036] Where r is the force arm, which is the distance from the pivot point to the contact point of the strut with the pocket.
[0037] The lower the value of M, the easier it is for the electromechanical section of the eCMD to rotate the strut. Thus, for a given clutch speed, the parameters that can be influenced to reduce the torque are the strut mass, the value of µ, and the length of the lever arm. One objective of disclosures 2018 / 0010651 and 2018 / 0038425 is to reduce the lever arm.
[0038] "Strut instability" is an undesirable condition often characterized by a strut being extended when it should be seated in its pocket. Strut instability is a primary concern regarding durability, as it is directly correlated with premature spring, strut, and pocket wear, and eventual failure. During the free-running phase, it is advantageous for the struts to descend into their respective pockets to minimize parasitic losses resulting from various Newtonian interactions. The minimum angular velocity of the pocket plate that holds the strut in the pocket is often referred to as the strut's "deposit" velocity.
[0039] The mechanical processes that cause the strut to descend are numerous and can be correlated (among many other factors) with the rotational speed of the pocket plate, the angular acceleration of the pocket plate, the strut geometry, the spring coefficient, the fluid interactions, and the clearance angle of the pocket wall, as mentioned previously.
[0040] Published US patent application No. 2017 / 0343060 discloses a coupling part for an engaging coupling assembly, which has a coupling surface with at least one pocket. Each pocket is dimensioned and shaped to receive and nominally hold a locking part that rests within its pocket during a free-running condition of the assembly at a settling angular velocity of the coupling part about a rotational axis of the assembly. Each pocket has a pocket axis that is angled with respect to a normal to a centerline of the coupling part to improve the locking part dynamics with respect to the strut settling velocity during the free-running condition. SUMMARY OF EXAMPLE FORMS OF EXECUTION
[0041] An objective of at least one embodiment of the present invention is to provide a high-speed, free-running clutch and control assembly, a clutch assembly and a locking element for use therein, wherein friction between the locking element and a side surface of its pocket is substantially reduced to facilitate pivoting movement of the locking element.
[0042] An objective of at least one embodiment of the present invention is to provide a high-speed, free-running clutch and control assembly, a clutch assembly and a locking element for use therein, wherein friction between the locking element and an outer wall of a pocket, which is normally contacted by the locking element at high speeds, is greatly reduced by providing a bearing between the locking element and the wall, thereby reducing the coefficient of friction between them.
[0043] In carrying out the foregoing objectives and other objectives of at least one embodiment of the present invention, a locking element is provided to transmit a controllable torque between a first and second coupling element of a coupling assembly. The first coupling element rotates about an axis of rotation of the assembly and has a centerline through the axis and a coupling surface with a pocket that is at least partially defined by a pocket surface. The pocket is dimensioned and shaped to receive and nominally retain the locking element and at least one bearing. During a free-running state of the assembly, the locking element pivots downward into the pocket. The locking element has a partially engaging first end face, a partially engaging second end face, a main body section between the end faces, and at least one pivot pin projecting from the main body section.The at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement.
[0044] The at least one pivot pin can be a generally cylindrical end section for contacting the at least one bearing, wherein the at least one bearing can comprise an axial bearing that causes centrifugal forces to react, which are generated from the locking part at high speeds around the axis of rotation.
[0045] The end faces of the locking part can be movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thus enabling a one-way torque transmission between the coupling parts.
[0046] The at least one pivot pin can include at least one projecting tab extending laterally from the main body section, wherein the at least one bearing can include an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation.
[0047] The at least one pivot pin can comprise inner and outer projecting tabs extending laterally from the main body section, with the at least one bearing having a roller bearing on each tab.
[0048] The at least one pivot pin can include a convex upper pivot pin extending upwards from the main body section, wherein the at least one bearing can have a roller bearing on opposite sides of the upper pivot pin.
[0049] The locking element can be a planar or radial locking strut.
[0050] The locking strut can be an active locking strut.
[0051] The locking part may be a metal injection-molded locking part.
[0052] The locking part can have an inner and outer pivot pin that extend laterally from the main body section to allow a pivoting movement of the locking part about an axis that intersects the pivot pins.
[0053] Each pocket can have an inner and outer pocket wall. The inner pocket wall can be parallel to a normal to the centerline. The outer pocket wall can be angled with respect to the normal to the centerline to improve the dynamics of the locking element.
[0054] Furthermore, in carrying out the aforementioned objectives and other objectives of the at least one embodiment of the present invention, an engaging coupling assembly is provided. The assembly comprises a first and a second coupling part. The first coupling part rotates about an axis of rotation of the assembly and has a center line through the axis and a coupling surface with a pocket that is at least partially defined by a pocket surface. The pocket is dimensioned and shaped to receive and nominally retain the locking part and at least one bearing. During a free-running state of the assembly, the locking part pivots downward into the pocket. The locking part has a partially engaging first end face, a partially engaging second end face, a main body section between the end faces, and at least one pivot pin projecting from the main body section.The at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement.
[0055] The at least one pivot pin can include a convex upper pivot pin extending upwards from the main body section, wherein the at least one bearing can have a roller bearing on opposite sides of the upper pivot pin.
[0056] The at least one pivot pin can have a generally cylindrical end section for contacting the at least one bearing, wherein the at least one bearing can comprise an axial bearing that causes centrifugal forces to react, which are generated from the locking part at high speeds around the axis of rotation.
[0057] The end faces of the locking part can be movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thus enabling a one-way torque transmission between the coupling parts.
[0058] The at least one pivot pin can include at least one projecting tab extending laterally from the main body section, wherein the at least one bearing can include an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation.
[0059] The at least one pivot pin can comprise inner and outer projecting tabs extending laterally from the main body section, with the at least one bearing having a roller bearing on each tab.
[0060] The locking element can be a planar or radial locking strut.
[0061] The locking strut can be an active locking strut.
[0062] The locking part may be a metal injection-molded locking part.
[0063] The locking part can have an inner and outer pivot pin that extend laterally from the main body section to allow a pivoting movement of the locking part about an axis that intersects the pivot pins.
[0064] Each pocket can have an inner and outer pocket wall. The inner pocket wall can be parallel to a normal to the centerline, and the outer pocket wall can be angled with respect to the normal to the centerline to improve the dynamics of the locking element.
[0065] Furthermore, in carrying out the aforementioned objectives and other objectives of the at least one embodiment of the present invention, a free-running coupling and control assembly is provided. The assembly comprises a first and a second coupling part. The first coupling part rotates about a rotation axis of the assembly and has a center line through the axis and a first coupling surface with a pocket that is at least partially defined by a pocket surface. The pocket is dimensioned and shaped to receive and nominally hold a locking element and at least one bearing.The first coupling element has a second surface spaced apart from the first coupling surface and having a passage connected to the pocket to transmit an actuating force to the locking element, causing it to actuate within the pocket so that it moves between engaged and disengaged positions. During a free-running state of the assembly, the locking element pivots downward into the pocket. The locking element has a partially engaging first end surface, a partially engaging second end surface, a main body section between the end surfaces, and at least one pivot pin projecting from the main body section.The at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement.
[0066] The at least one pivot pin can have a generally cylindrical end section for contacting the at least one bearing, wherein the at least one bearing can comprise an axial bearing that causes centrifugal forces to react, which are generated from the locking part at high speeds around the axis of rotation.
[0067] The end faces of the locking part can be movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thus enabling a one-way torque transmission between the coupling parts.
[0068] The at least one pivot pin can include at least one projecting tab extending laterally from the main body section, wherein the at least one bearing can include an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation.
[0069] The at least one pivot pin can comprise inner and outer projecting tabs extending laterally from the main body section, with the at least one bearing having a roller bearing on each tab.
[0070] The locking element can be a planar or radial locking strut.
[0071] The locking strut can be an active locking strut.
[0072] The locking part may be a metal injection-molded locking part.
[0073] The at least one pivot pin can include a convex upper pivot pin extending upwards from the main body section, wherein the at least one bearing can have a roller bearing on opposite sides of the upper pivot pin.
[0074] The locking part can have an inner and outer pivot pin that extend laterally from the main body section to allow a pivoting movement of the locking part about an axis that intersects the pivot pins.
[0075] Each pocket can have an inner and outer pocket wall. The inner pocket wall can be parallel to a normal to the centerline, and the outer pocket wall can be angled with respect to the normal to the centerline to improve the dynamics of the locking element. List of characters Fig. Figure 1 is a partially separated top view of a locking element or strut from the prior art, which is located in a rotating pocket plate, together with a pivot axis of the strut, various reaction forces F R1 and F R2 , and a centrifugal force F C at a focal point of the strut; Fig. 2 is one of the views of Fig. 1. Similar view of another locking part from the prior art and other force arms and forces; Fig. 3 is a disassembled view of an active free-running clutch and control assembly constructed in accordance with at least one embodiment of the invention; Fig. 4 is one of the views of Fig. 3 similar views, but from a reversed perspective; Fig. Figure 5 is a perspective end view of the assembly of the Fig. 3 and Fig. 4 in their composite state; Fig. 6 is one of the views of Fig. 5. Similar view, but with the notched plate removed to show the locking parts and the cover plate; Fig. Figure 7 is a side view, partially offset and in cross-section, of a pair of roller bearings on opposite sides of a convex upper pivot pin of a radial strut; Fig. Figure 8 is a side view, partially offset and in cross-section, of a roller bearing on a lug of a radial strut; Fig. Figure 9 is a schematic side view, partially detached and in cross-section, of the radial strut of Fig. Figure 8 now shows a roller bearing on each tab of the radial strut; Fig. Figure 10 is a partially detached top view of a locking part or strut of the prior art which is located in a rotating pocket plate, wherein dashed lines indicate friction areas on the walls of the pocket caused by centrifugal force which may approach 200 US pounds on the outer pocket wall; Fig. Figure 11 is a side view, partially offset and in cross-section, showing a bearing on a tab of the locking part and various preload parts or springs with an actuating system for controlling the movement of the locking part; Fig. Figure 12 is a partially recessed top view of a locking part, its bearing and springs in a pocket of a pocket plate together with a mounting plate; Fig. 13 is one of the views of Fig. 12. Similar view, but with the mounting plate removed; Fig. 14 is one of the views of Fig. 11 similar view, but showing a mounting plate as part of the actuation system and the locking part in its retracted decoupling position; Fig. 15 is one of the views of Fig. 14 similar view, but showing the locking part in its extended coupling position; Fig. Figure 16 is a partially separated top view of a locking part of another embodiment in a pocket of a pocket plate together with a mounting plate; Fig. 17 is a Fig. 16 Similar view, but with the mounting plate removed to reveal a return spring in the form of a leaf spring and an axial bearing for the locking part; Fig. 18 is one of the views of Fig. 16 and Fig. 17 Similar view, but with the locking part and the mounting plate removed to show in particular the leaf spring, the bearing and an axial support spring for the locking part; Fig. 19 is one of the views of Fig. 14 similar view and shows the locking part, the leaf spring and the actuating spring of the Fig. 17 to Fig. 18, wherein the locking part is in its retracted decoupling position; Fig. Figure 20 is a perspective side view of the locking part or strut of the Fig. 16, Fig. 17 and Fig. 19; Fig. Figure 21 is a disassembled view of a free-running clutch and control assembly, which is in accordance with an embodiment of the present invention and with the components of the Fig. 16 to Fig. 20 is built; Fig. Figure 22 is a partially recessed top view of a locking part similar to the locking part of the Fig. 16, Fig. 17 and Fig. 20 in a pocket of a pocket plate together with a rotary selector plate, which allows the locking part to rise into a notch of a notched plate; Fig. 23 is one of the views of Fig. 22 Similar view, but with the selector plate removed to reveal a spring and axial bearing for the locking part; Fig. 24 is one of the views of Fig. 22 and Fig. 23 Similar view, but with the locking part and the selector plate removed in order to show in particular the spring and the axial bearing for the locking part; Fig. 25 is one of the views of Fig. 19 similar view with the locking part and the spring of the Fig. 22 and Fig. 23 and the dial of the Fig. 22 and wherein the locking part is in its extended coupling position; Fig. Figure 26 is a perspective side view of the locking part or strut of the Fig. 22, Fig. 23 and Fig. 25; Fig. 27 is a disassembled view of a free-running clutch and control assembly, which, in accordance with another embodiment of the present invention, is equipped with the components of Fig. 22 to Fig. 26 is built; Fig. 28 is one of the views of Fig. 17 similar view, but with the pocket of the pocket plate turned outwards; Fig. 29 is one of the views of Fig. 17 and Fig. 28 similar views, but without pocket rotation; and Fig. 30 is one of the views of Fig. 17, Fig. 28 and Fig. 29 similar view, but with pocket turned inwards. DETAILED DESCRIPTION
[0076] Detailed embodiments of the present invention are disclosed here as required; however, it should be clear that the disclosed embodiments are merely exemplary of the invention, which can be implemented in various and alternative forms. The figures are not necessarily to scale; some features may be exaggerated or minimized to show details of certain components. Therefore, the specific structural and functional details disclosed here should not be interpreted as limiting, but merely as a representative basis to teach a person skilled in the art how to use the present invention in various ways.
[0077] Generally, this refers to a locking component or strut, which is generally associated with 102 The information provided reveals that the respective coupling and control assembly is located within its respective coupling and control assembly. 100 ( Fig. 3 and Fig. 4) can be used. Various designs of the locking part. 102 are especially in the drawing of the Fig. 7 to Fig. 9 and Fig. 11 to Fig. 15 shown.
[0078] The active rotating or pivoting strut 102 is activated to move into its upward or clutch position ( Fig. 11 and Fig. 15) to move so that a locking mechanism is formed between a pocket plate 106 and a notched plate 110 This can take place. This occurs when there is an actuation system. 104 ( Fig. 11), which is generally associated with 105 specified mounting plate and actuating or mounting springs 115 exhibits, commands, the strut 102 to move. The rotating strut 102 The generated centrifugal force can affect the strut 102 in the notched plate 110To hold and prevent slippage due to friction, a more powerful return spring can be used to overcome this problem. 114 can be used. In at least one embodiment of the invention, the strut can be used. 102 They can be disengaged by a relatively small return spring. The contact springs 115 They are designed to move along the outer wall of the pockets to reduce the effects of centrifugal force. If they were not designed this way, the springs could... 115 It could get caught between the strut and the pocket, which could damage the spring or prevent the spring from pushing the strut into the engagement position. This could also happen with the return spring if, as in Fig. Eleven coil springs are used. A torsion spring 114 , which exhibits a low change in function under centrifugal force, is in Fig. 13 used on the inner flap of the strut (this spring is also used in this design due to the dense arrangement).
[0079] In at least one embodiment of the invention, at least one bearing is in the form of an axial bearing. 126 (i.e. Fig. 3, Fig. 4, Fig. 6 and Fig. 11 to Fig. 15) for the actively controlled strut 102 used with a dynamic clutch, where the active strut 102 is actuated to move into its upward position, so that a locking mechanism engages between the pocket plate 106 and the notched plate 110 This can take place. When the actuation system receives a command, the strut moves. 102 which can disengage itself, can be disengaged by the rotating strut. 102 centrifugal force generated automatically in the pocket plate 106They hold and prevent release due to friction. The force required for actuation also becomes too great to overcome. To overcome this problem, the return spring can be used. 114 and the spring 115 more force can be used.
[0080] In this embodiment of the invention, the strut can 102 either with a small return spring 114 or cannot be disengaged with any return spring, depending on how the strut is positioned. 102 It is designed to behave at lower speeds, and the force required is much lower. The axial bearing 126 is between the pocket plate 106 and the strut 102 used so that the entire thing passes through the strut 102 The force generated is applied directly to the bearing. 126 It works. This strut 102 is located in the more level direction, which allows the center of mass of the strut to102 does not affect the function of engaging or disengaging. The insensitivity of the strut's center of mass. 102 This stems from the orientation of the flatter design, which is important because with a strut in the radial direction (i.e. the Fig. 7 to Fig. 9) whose center of mass will always affect the forces that bring it into action and those that bring it out of action. The camp 126 This is used because the friction for rotation is called rolling friction, which tends to have a coefficient of friction of 0.0015 compared to a static coefficient of friction of 0.2 for lubricated steel on steel. A coefficient of friction between 0.0015 and 0.2 contributes, mathematically, to the bearing... 126 resists 0.8% of the force compared to that of lubricated steel on a steel interface.
[0081] The assembly 100 features a support or mounting plate 105, the pocket plate 106 , a generally with 108 specified cover or mounting plate, the notched plate 110 and a general one with 112 specified snap ring, which attaches to all plates 105 , 106 , 108 and 110 holds together. The preload components or springs. 115 span their respective struts 102 in their respective pockets 113 before.
[0082] The mounting plate 105 stores dowel pins 117 , and the pocket plate 106 stores bushings 118 in openings 119 , in which the dowel pins 117 through the sockets 118 They are stored in this way. 106 and 105 connected. The mounting plate 108 has several passes 111 , through which the struts 102 can extend so that they can fulfill their locking function.
[0083] Each strut 102 has a first end surface that engages a part 120 , a second end surface that engages a part 122 and an elongated main body section 124 between the end faces 120 and 122 at least one and preferably two projecting tabs 130 (so that each strut 102 (can be used either as a forward or backward brace) extend laterally from the main body section. 124 The end faces 122 and 120 of the locking part 102 are positions in engagement and out of engagement with regard to the coupling parts 106 and 110 movable during a swiveling movement, thus enabling a one-way torque transmission between the coupling parts. 106 and 110 can take place.
[0084] The greatest force present in this construction is the stabilizing force caused by high rotational speeds, which stabilizes the strut. 102 to hold it in the downward position. This force increases as the speed in the clutch increases. This force is present in the strut of the radial type of the Fig. 7 to Fig. 9 not available.
[0085] In the embodiments of the Fig. 7 to Fig. 9. The bearing takes the form of roller bearings. 128 and 128' The strut or locking part is a radial strut. 102' with end faces 120' and 122' and a major body section 124' The radial strut 102' the Fig. 7 has a convex upper pivot pin 126' on, whereby the roller bearings 128' in bearing contact on opposite sides of the pivot pin 126' condition.
[0086] The radial strut 102' the Fig. 8 and Fig. 9 has a pair of tabs 130' on, extending laterally from the main body section 124' extend roller bearings 128 are located around the tabs 130' , to the radial strut 102' to be mounted in a rotating position.
[0087] The design of the bearings 128' and 128 for the radial strut 102' the Fig. 7 to Fig. 9 is similar to the design of the bearings 126 for the planar strut 102 The radial strut 102' It is sensitive to the location of the center of mass, which must be shifted slightly into the decoupling position to prevent unintentional interference. There is no stabilizing force in a radial strut, meaning that the greatest force in this system acts on the center of mass relative to the strut's pivot point. 102' would be. Two constructions ( Fig. 7 to Fig. 9) could use roller bearings to maintain the centrifugal forces generated at high speeds. The first design ( Fig. 7) would have two camps 128' on the top of the strut 102' (continuing towards the outer diameter), which would necessitate a denser radial arrangement. The second design ( Fig. 8 and Fig. 9) would have a warehouse 128 in the middle of each of the "tabs" 130' the strut 102' , which necessitates a denser axial arrangement. The bearings 128 They help to manage the centrifugal forces, and thus the greatest force in the system would be the moment exerted by the center of mass of the strut. 102' is generated, which is not located at the center of rotation. The center of mass of the strut. 102'It should be directed towards the disengaged strut to prevent unintentional activation. The centrifugal forces can cause the rollers to move within the bearings. 128 inevitably lead to the outer diameter of the bearing. 128 being pushed around could create some problems. This would need to be taken into account when designing this option.
[0088] Each of the bags 113 in the pocket plate 106 provides sufficient clearance to allow for a sliding movement of its locking part. 102 during the movement of the locking part 102 to allow movement between the engaged and disengaged positions. Each locking component 102This could be an injection-molded locking component, such as a metal injection-molded locking part or a metal injection-molded strut. Alternatively, the struts can be manufactured using additive manufacturing, such as 3D printing. By using additive manufacturing, the density in the struts can be varied, which would help protect the stabilizing moment from centrifugal forces.
[0089] The first coupling part or the pocket plate 106 It also has an area with several passageways. 140 , which revolve around the axis of rotation 142 ( Fig. 5) the assembly 100 are spaced apart, and features a passageway 142 up, which comes with every bag 113 is connected. The passages 140 convey their respective locking parts 102 in their respective pockets 113 Actuating forces (typically via the actuating springs) 115 ). The surfaces of the pocket plate106 are generally ring-shaped and generally extend radially with respect to the axis of rotation 142 the assembly 100 Actuators, such as spring-loaded actuators 115 , can in the passages 140 must be recorded to account for the actuating forces required to operate the locking parts. 102 in their respective pockets 113 to provide so that the locking parts 102 move between their engaged and disengaged positions. In addition to the spring actuators. 115 Other types of actuators can also be used to provide the actuation forces. Pressurized fluid can also be used to provide the actuation forces.
[0090] Preload components such as the spiral return springs 114 guide the locking parts 102 contrary to a pivoting movement of the locking parts 102to their engaged positions. The spring actuators 115 pivot their locking parts 102 contrary to the preload of the spring preload parts 114 Each bag 113 can be an inner recess 144 have to adjust their respective preload spring 114 to take up the pockets 113 Pencil cases are.
[0091] Now, with regard to the Fig. 16 to Fig. 21 a locking part or strut, generally referred to as 202, hereby disclosed, which in its respective coupling and control assembly 200 ( Fig. 21) can be used. The shape of the strut 202 is optimized to reduce the “stabilizing force” that occurs at high speeds.
[0092] The active rotating or pivoting strut 202is actuated to move into its upward or clutch position (not shown), so that a locking mechanism is engaged between a pocket plate 206 and a notched plate 210 This can occur when an actuation system, such as the actuation system, malfunctions. 104 ( Fig. 11), which includes a mounting plate (not shown) and actuating or mounting springs 215 exhibits, is ordered to the strut 202 to move. The rotating strut 202 The generated centrifugal force can affect the strut 202 in the notched plate 210 To hold and prevent release due to friction, a more powerful return spring, such as a leaf spring, can be used to overcome this problem. 214 can be used. In at least one embodiment of the invention, the strut can be used. 202They can be disengaged by a relatively small return spring. The contact springs 215 They are designed to move along the outer wall of the pockets to reduce the effects of centrifugal force. If they were not designed this way, the springs could... 215 it could get caught between the strut and the pocket, which could damage the spring or prevent the spring from pushing the strut into the engagement position.
[0093] In at least one embodiment of the invention, at least one rotary bearing is in the form of an axial bearing. 226 (i.e. Fig. 17, Fig. 18 and Fig. 21) for the actively controlled strut 202 used with a dynamic clutch, where the active strut 202 is actuated to move into its upward position, so that a locking mechanism engages between the pocket plate 206 and the notched plate 210This can take place. When the actuation system receives a command, the strut moves. 202 which can disengage itself, can be disengaged by the rotating strut. 202 centrifugal force generated automatically in the pocket plate 206 They hold and prevent release due to friction. The force required for actuation also becomes too great to overcome. To overcome this problem, the return spring can be used. 214 and the spring 215 more force can be used.
[0094] In this embodiment of the invention, the strut can 202 either with a small return spring 214 or cannot be disengaged with any return spring, depending on how the strut is positioned. 202 It is designed to behave at lower speeds, and the force required is much lower. The axial bearing 226is between the outer side wall of a bag 213 in the pocket plate 206 and the strut 202 used so that the entire thing passes through the strut 202 The force generated is applied directly to the bearing. 226 It works. This strut 202 is located in the more level direction, which allows the center of mass of the strut to 202 does not affect the function of engaging or disengaging. The insensitivity of the strut's center of mass. 202 This stems from the orientation of the flatter design, which is important because with a strut in the radial direction (i.e. Fig. 7 to Fig. 9) whose center of mass will always affect the forces that bring it into action and those that bring it out of action. The camp 226This is used because the friction for rotation is called rolling friction, which tends to have a coefficient of friction of 0.0015 compared to a static coefficient of friction of 0.2 for lubricated steel on steel. A coefficient of friction between 0.0015 and 0.2 contributes, mathematically, to the bearing... 226 resists 0.8% of the force compared to that of lubricated steel on a steel interface.
[0095] The assembly 200 The support or mounting plate (not shown) indicates the pocket plate 206 , a cover or mounting plate generally designated with 208, the notched plate 210 and a general one with 212 specified snap ring, which attaches to all plates 206 , 208 and 210 holds together. The preload components or springs. 215 span their respective struts 202 in their respective pockets 213before. The leaf or preload spring 214 is located in a groove 203 , which are located on the underside of the strut 202 is trained.
[0096] As in the first embodiment, the mounting plate supports dowel pins (not shown), and the pocket plate 206 It holds bushings (not shown) in openings where the dowel pins are held by the bushings. In this way, the plates are connected. The mounting plate 208 has several passes 211 , through which the struts 202 can extend so that the struts 202 so they can fulfill their locking function.
[0097] Each strut 202 has a first end surface that engages a part 220 , a second end surface that engages a part 222 and a lobed main body section 224 between the end faces 220 and 222at least one and preferably two projecting flaps or tabs 230 (so that each strut 202 (can be used either as a forward or backward brace) extend laterally from the main body section. 224 The tabs 230 They essentially have flat, parallel ends, one of which is an inner end face. 225 of the axial bearing 226 intervenes. The end surfaces 222 and 220 of the locking part 202 are positions in engagement and out of engagement with regard to the coupling parts 206 and 210 movable during a swiveling movement, thus enabling a one-way torque transmission between the coupling parts. 206 and 210 can take place.
[0098] The greatest force present in this construction is the stabilizing force caused by high rotational speeds, which stabilizes the strut.202 to hold it in the downward position. This force increases as the speed in the clutch increases. This force is present in the strut of the radial type of the Fig. 7 to Fig. 9 not available.
[0099] Each of the bags 213 in the pocket plate 206 provides sufficient clearance to allow for a sliding movement of its locking part. 202 during the movement of the locking part 202 to allow movement between the engaged and disengaged positions. Each locking component 202 This could be an injection-molded locking component, such as a metal injection-molded locking component or a metal injection-molded strut. Alternatively, the struts could be... 202 They can be manufactured using additive manufacturing methods such as 3D printing. By using additive manufacturing, the density in the struts can be adjusted. 202varying, which would help protect the stabilizing moment from centrifugal forces.
[0100] The first coupling part or the pocket plate 206 It also has an area with several passageways. 240 , which are around the axis of rotation of the assembly 200 are spaced apart, and features a passage that connects to each pocket 213 is connected. The passages 240 convey their respective locking parts 202 in their respective pockets 213 Actuating forces (typically via the actuating springs) 215 ). The surfaces of the pocket plate 206 are generally ring-shaped and generally extend radially with respect to the axis of rotation of the assembly 200 Actuators, such as spring-loaded actuators 215 , can in the passages 240 must be recorded to account for the actuating forces required to operate the locking parts. 202 in their respective pockets 213to provide so that the locking parts 202 move between their engaged and disengaged positions. In addition to the spring actuators. 215 Other types of actuators can also be used to provide the actuation forces. Pressurized fluid can also be used to provide the actuation forces.
[0101] Preload components such as leaf springs 214 guide the locking parts 202 contrary to a pivoting movement of the locking parts 102 to their engaged positions. The spring actuators 215 pivot their locking parts 202 contrary to the preload of the spring preload parts 214 Each bag 213 can be an inner recess 244 have to adjust their respective preload spring 214 to take up the pockets 213 Pencil cases are.
[0102] Now, with regard to the Fig. 22 to Fig. 27 a lobed locking part or a lobed strut, generally designated by 302, hereby disclosed, which in its respective coupling and control assembly 300 ( Fig. 27) can be used. The strut 302 is in terms of size and shape of the strut 202 similar. The assembly 300 features a selector plate generally designated 301, which has openings 311 exhibits which the struts 302 in notches of a notched plate 310 It can be raised or pivoted. Alternatively, a fixed cover plate can be used for a passive one-way coupling function.
[0103] The active rotating or pivoting strut 302 is activated to move into its upward or clutch position ( Fig. 22, Fig. 23 and Fig. 25) to move so that a locking mechanism is formed between a pocket plate 306 and the notched plate 310 This can take place. This occurs when the dial plate... 301 is ordered to turn in a first direction, so that the strut 302 through an opening 311 in the dial plate 301 , as in the Fig. 22 and Fig. 25 shown, can extend. The rotating strut 302 The generated centrifugal force can affect the strut 302 in the notched plate 310 to hold and prevent loosening due to friction. In at least one embodiment of the invention, the strut can 302 be disabled by removing the selector plate 302 again, but rotated in the opposite direction.
[0104] In at least one embodiment of the invention, at least one rotary bearing is in the form of an axial bearing. 326(i.e. Fig. 23 and Fig. 24) for the strut 302 used, with the active strut 302 is actuated to move into its upward position, so that a locking mechanism engages between the pocket plate 306 and the notched plate 310 can take place. If the dial plate 301 a command is given to rotate so that the strut 302 The rotating strut can disable the mechanism. 302 centrifugal force generated automatically in the pocket plate 306 To hold and prevent detachment due to friction, the force required for actuation can become too great to handle. To overcome this problem, the retaining spring can be used. 315 more force can be used.
[0105] In this embodiment of the invention, the strut can 302 to be detached from the outer side wall of the bag, whereby the axial bearing326 between the outer side wall of a pocket in the pocket plate 306 and the strut 302 is used so that the entire length is covered by the strut 302 The generated force goes directly into the bearing. 326 is brought into a reaction. As in the embodiment of the Fig. 16 to Fig. 21 brings the axial bearing 326 the strut 302 Centrifugal forces generated at high speeds cause a reaction. The strut 302 is located in the more level direction, which means that the center of mass of the strut 302 does not affect the function of engaging or disengaging. The insensitivity of the strut's center of mass. 302 This stems from the orientation of the flatter design, which is important because with a strut in the radial direction (i.e. Fig. 7 to Fig. 9) whose center of mass will always act on the forces that engage and disengage. The axial bearing 326 This is used because the friction for rotation is called rolling friction, which tends to have a coefficient of friction of 0.0015 compared to a static coefficient of friction of 0.2 for lubricated steel on steel. A coefficient of friction between 0.0015 and 0.2 contributes, mathematically, to the bearing... 326 resists 0.8% of the force compared to that of lubricated steel on a steel interface.
[0106] The assembly 300 The pocket plate 306 , the dial 301 (or possibly a cover or mounting plate), the notched plate 310 and a snap ring generally designated 312, which secures all plates 301 , 306 and 310 holds together. The preload components or springs. 315 span their respective struts302 in their respective pockets 313 before.
[0107] Each strut 302 has a first end surface that engages a part 320 , a second end surface that engages a part 322 and an elongated main body section 324 between the end faces 320 and 322 at least one and preferably two projecting flaps or tabs 330 (so that each strut 302 (can be used either as a forward or backward brace) extend laterally from the main body section 324. The tabs 330 They essentially have flat, parallel ends, one of which is an inner end face. 325 of the axial bearing 326 intervenes. The end surfaces 322 and 320 of the locking part 302 are positions in engagement and out of engagement with regard to the coupling parts306 and 310 movable during a swiveling movement, thus enabling a one-way torque transmission between the coupling parts. 306 and 310 can take place.
[0108] The greatest force present in this construction is the stabilizing force caused by high rotational speeds, which stabilizes the strut. 302 to hold it in the downward position. This force increases as the speed in the clutch increases. As mentioned previously, this force is present in the strut of the radial type of the Fig. 7 to Fig. 9 not available.
[0109] Each of the bags 313 in the pocket plate 306 provides sufficient clearance to allow for a sliding movement of its locking part. 302 during the movement of the locking part 302 to allow movement between the engaged and disengaged positions. Each locking component 302This could be an injection-molded locking component, such as a metal injection-molded locking component or a metal injection-molded strut. Alternatively, the struts could be... 302 They can be manufactured using additive manufacturing methods such as 3D printing. By using additive manufacturing, the density in the struts can be adjusted. 302 varying, which would help protect the stabilizing moment from centrifugal forces.
[0110] The first coupling part or the pocket plate 306 has an opening 342 up, which comes with every bag 313 is related. Preload components, such as coil springs. 315 , can be found in the openings 342 to be recorded in order to apply the preload forces for preloading the locking parts 302 in their respective pockets 313 to provide so that the locking parts 302 move between their engaged and disengaged positions. Besides the springs315 Other types of prestressing components can also be used to provide the prestressing forces.
[0111] The sections of the dial that do not have an opening 301 prevent a pivoting movement of the locking parts 302 to their engaged positions. The springs 315 pivot their locking parts 302 , if the openings 311 with the locking parts 302 are aligned.
[0112] Now with reference to the Fig. 28 to Fig. 30 (the Fig. 17), in addition to many previously described factors that affect the speed of a “depositing” or “locking” of a strut, the inventors of this application discovered that a “pocket rotation” (i.e. the angle of the pocket outer wall) 225 in relation to a line (or center line) 227, which runs through the center of the coupling,) is another factor that affects the amount of actuating force required to rotate the strut. 202 is necessary. A counterclockwise (i.e., outward) rotation of the pocket, as in Fig. As shown in Figure 28, the actuation force for a rotating pocket plate is reduced, thereby allowing or compensating for relatively large clearance angles, which lowers manufacturing costs. A clockwise (i.e., inward) pocket rotation, as shown in Figure 28, reduces the actuation force for a rotating pocket plate, thus permitting or compensating for relatively large clearance angles, which in turn reduces manufacturing costs. Fig. Figure 30 shows an increase in the laying speed. The desired speed (i.e., the rotational speed) at which struts lay down determines the ability of the clutches to engage. Therefore, if it is desired that the clutch engages at a relatively high speed (i.e., rotational speed), the pocket twist inwards would be used.
[0113] As described in US publication application 2017 / 0343060, which is assigned to the same assignee as the assignee of the present application, with the addition of a pocket rotation, the geometric composition of the strut and its pocket changes, which, due to the centrifugal force now acting on the strut, leads to the generation of a new moment. Centrifugal force is a physical force that causes the strut / locking wall dynamics as described here. This new moment arises from the relative change of a pivot point about which the strut ascends or descends.
[0114] The largest one on the strut 202 The force acting at high speeds is the Euler torque (also known as the stabilizing torque). If the strut is 202 turned inwards (i.e. Fig. 30), increases the moment due to the center 229 the mass of the strut 202 , if the strut 202The bearing is fixed in its engagement position, subjecting it to the Euler torque. 226 This eliminates friction, and the inward rotation cancels out the Euler torque. This allows the strut to 202 operating at high speeds with a small amount of actuation force in the notched plate 210 to fix and remove from this. This can be applied to all of the different struts described here, regardless of whether they are applied actively or passively.
[0115] Although exemplary embodiments have been described above, these embodiments are not intended to describe all possible forms of the invention. Rather, the words used in the technical description are descriptive and not limiting, and it is clear that various modifications can be made without altering the content and scope of the invention. Furthermore, the features of different implementations can be combined to form further embodiments of the invention. QUOTES INCLUDED IN THE DESCRIPTION
[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature
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[0023]
Claims
[1] Locking element for transmitting a controllable moment between a first and second coupling element of a coupling assembly, wherein the first coupling element rotates about an axis of rotation of the assembly and has a centerline through the axis and a coupling surface with a pocket that is at least partially defined by a pocket surface, wherein the pocket is dimensioned and shaped to receive and nominally hold the locking element and at least one bearing, wherein during a free-running state of the assembly the locking element pivots downwards into the pocket, the locking element comprising: a first end surface that engages a part; a second end surface that engages part of the area; a main body section between the end faces; and at least one pivot pin projecting from the main body section, wherein the at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement. [2] Locking part according to claim 1, wherein the at least one pivot pin has a generally cylindrical end section for contacting the at least one bearing and wherein the at least one bearing comprises an axial bearing which causes centrifugal forces to react which are generated from the locking part at high speeds about the axis of rotation. [3] Locking part according to claim 1, wherein the end faces of the locking part are movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, whereby a one-way torque transmission between the coupling parts can take place. [4] Locking part according to claim 1, wherein the at least one pivot pin comprises at least one projecting tab extending laterally from the main body section, and wherein the at least one bearing comprises an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation. [5] Locking part according to claim 1, wherein the at least one pivot pin comprises inner and outer projecting tabs extending laterally from the main body section, and wherein the at least one bearing has a roller bearing on each tab. [6] Locking part according to claim 1, wherein the at least one pivot pin comprises a convex upper pivot pin extending upwards from the main body section, and wherein the at least one bearing comprises a roller bearing on opposite sides of the upper pivot pin. [7] Locking element according to claim 1, wherein the locking element is a planar or radial locking strut. [8] Locking part according to claim 7, wherein the locking strut is an active locking strut. [9] Locking part according to claim 1, wherein the locking part is a metal injection molded locking part. [10] Locking part according to claim 1, wherein the locking part has an inner and outer pivot pin which extend laterally from the main body section to allow a pivoting movement of the locking part about an axis which intersects the pivot pins. [11] Locking part according to claim 1, wherein each pocket has an inner and outer pocket wall, wherein the inner pocket wall is parallel to a normal to the center line and wherein the outer pocket wall is angled with respect to the normal to the center line to improve the dynamics of the locking part. [12] Engageable coupling assembly comprising a first and second coupling part, wherein the first coupling part rotates about an axis of rotation of the assembly and has a centerline through the axis and a coupling surface with a pocket that is at least partially defined by a pocket surface, wherein the pocket is dimensioned and shaped to receive and nominally hold the locking part and at least one bearing, wherein during a free-running state of the assembly the locking part pivots downwards into the pocket, the locking part comprising: a first end surface that engages a part; a second end surface that engages part of the area; a main body section between the end faces; and at least one pivot pin projecting from the main body section, wherein the at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement. [13] Assembly according to claim 12, wherein the at least one pivot pin comprises a convex upper pivot pin extending upwards from the main body section, and wherein the at least one bearing comprises a roller bearing on opposite sides of the upper pivot pin. [14] Assembly according to claim 12, wherein the at least one pivot pin has a generally cylindrical end section for contacting the at least one bearing and wherein the at least one bearing comprises an axial bearing that causes centrifugal forces to react which are generated from the locking part at high speeds about the axis of rotation. [15] Assembly according to claim 12, wherein the end faces of the locking part are movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thereby enabling a one-way torque transmission between the coupling parts. [16] Assembly according to claim 12, wherein the at least one pivot pin comprises at least one projecting tab extending laterally from the main body section, and wherein the at least one bearing comprises an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation. [17] Assembly according to claim 12, wherein the at least one pivot pin comprises inner and outer projecting tabs extending laterally from the main body section, and wherein the at least one bearing has a roller bearing on each tab. [18] Assembly according to claim 12, wherein the locking part is a planar or radial locking strut. [19] Assembly according to claim 18, wherein the locking strut is an active locking strut. [20] Assembly according to claim 12, wherein the locking part is a metal injection molded locking part. [21] Assembly according to claim 12, wherein the locking part has an inner and outer pivot pin which extend laterally from the main body section to allow a pivoting movement of the locking part about an axis which intersects the pivot pins. [22] Assembly according to claim 12, wherein each pocket has an inner and outer pocket wall, wherein the inner pocket wall is parallel to a normal to the center line and wherein the outer pocket wall is angled with respect to the normal to the center line to improve the dynamics of the locking part. [23] Free-running clutch and control assembly, comprising: a first and second coupling part, wherein the first coupling part rotates about an axis of rotation of the assembly and has a centerline through the axis and a coupling surface with a pocket that is at least partially defined by a pocket surface, wherein the pocket is dimensioned and shaped to receive and nominally hold the locking part and at least one bearing, wherein during a free-running state of the assembly the locking part pivots downwards into the pocket, the locking part comprising: a first end surface that engages a part; a second end surface that engages part of the area; a main body section between the end faces; and at least one pivot pin projecting from the main body section, wherein the at least one pivot pin enables a pivoting movement of the locking part and is dimensioned, shaped and arranged with respect to the main body section such that the at least one pivot pin makes contact with the at least one bearing located between the pocket surface and an outer surface of the at least one pivot pin in order to reduce friction during the pivoting movement. [24] Assembly according to claim 23, wherein the at least one pivot pin has a generally cylindrical end section for contacting the at least one bearing and wherein the at least one bearing comprises an axial bearing that causes centrifugal forces to react which are generated from the locking part at high speeds about the axis of rotation. [25] Assembly according to claim 23, wherein the end faces of the locking part are movable between engaged and disengaged positions with respect to the coupling parts during the pivoting movement, thereby enabling a one-way torque transmission between the coupling parts. [26] Assembly according to claim 23, wherein the at least one pivot pin comprises at least one projecting tab extending laterally from the main body section, and wherein the at least one bearing comprises an axial bearing that responds to centrifugal forces generated from the locking part at high speeds around the axis of rotation. [27] Assembly according to claim 23, wherein the at least one pivot pin comprises inner and outer projecting tabs extending laterally from the main body section, and wherein the at least one bearing has a roller bearing on each tab. [28] Assembly according to claim 23, wherein the locking part is a planar or radial locking strut. [29] Assembly according to claim 28, wherein the locking strut is an active locking strut. [30] Assembly according to claim 23, wherein the locking part is a metal injection molded locking part. [31] Assembly according to claim 23, wherein the at least one pivot pin comprises a convex upper pivot pin extending upwards from the main body section, and wherein the at least one bearing comprises a roller bearing on opposite sides of the upper pivot pin. [32] Assembly according to claim 23, wherein the locking part has an inner and outer pivot pin which extend laterally from the main body section to allow a pivoting movement of the locking part about an axis which intersects the pivot pins. [33] Assembly according to claim 23, wherein each pocket has an inner and outer pocket wall, wherein the inner pocket wall is parallel to a normal to the center line and wherein the outer pocket wall is angled with respect to the normal to the center line to improve the dynamics of the locking part.