DE112020000732T5 - FRICTION-FREE CLUTCH AND CONTROL ARRANGEMENT, LOCKING CLUTCH ARRANGEMENT AND LOCKING PART FOR USE IN THE ARRANGEMENTS - Google Patents

Abstract

An overrunning clutch and control assembly comprising a snap-in clutch assembly and locking members (23, 43) for use in the assembly. The center of gravity or center of mass of at least one of the locking parts (23, 43) is offset from the pivot axis of the locking part (23, 43) so that when the locking part (23, 43) moves from an engagement position, a moment arm of the center of gravity relative to the pivot axis decreases from a maximum value to essentially zero in a disengaged position in order to facilitate the disengagement of the locking part (23, 43) at high speeds.

Description

CROSS REFERENCE

This application is a continuation of the US application with the serial number 15 / 712,651 , which was filed on September 22, 2017, which takes advantage of the US Provisional Application with serial number 62 / 453,578 claimed, which was filed on February 2, 2017.

TECHNICAL AREA

• 1.) einrastbare reibungsfreie Kupplungsanordnungen wie radiale Kupplungsanordnungen;
• 2.) überholende, reibungsfreie (Freilauf-) Kupplungs- und Steuerungsanordnungen wie radiale Kupplungs- und Steuerungsanordnungen; und
• 3.) Verriegelungsteile zur steuerbaren Übertragung von Drehmomenten zwischen Kupplungsteilen von reibungsfreien Kupplungsanordnungen wie radialen Kupplungsanordnungen.

The present invention relates to:

• 1.) Snap-in frictionless clutch assemblies such as radial clutch assemblies;
• 2.) Overtaking, frictionless (freewheeling) clutch and control arrangements such as radial clutch and control arrangements; and
• 3.) Locking parts for the controllable transmission of torques between coupling parts of frictionless coupling arrangements such as radial coupling arrangements.

STATE OF THE ART

A typical one-way clutch (OWC) consists of an inner ring, an outer ring, and a locking device between the two rings. The one-way clutch is designed to lock in one direction and rotate freely in the other. Two types of one-way clutches are widely used in automatic vehicle transmissions:

A type of roller that consists of spring-loaded rollers between the inner and outer races of the one-way clutch. (Rollers without springs are also used in some applications); and
a sprag type that has asymmetrically shaped splines located between the inner and outer rings of the one-way clutch.

The one-way clutches are usually used in the transmission to prevent an interruption of the drive torque (i.e. the flow of power) during certain gear changes and to enable the motor to be braked when coasting.

Controllable or selectable one-way clutches (i.e., OWCs) are a departure from traditional one-way clutch designs. Optional OWCs add a second set of locking parts in combination with a sliding plate. The additional set of locking parts and the sliding plate add several functions to the OWC. Depending on the design requirements, controllable OWCs are able to establish a mechanical connection between rotating or standing waves in one or both directions. Depending on the design, OWCs can also run / run freely in one or both directions. A controllable OWC contains an externally controlled selection or control mechanism. The movement of this selection mechanism can be between two or more positions corresponding to different modes of operation.

U.S. 5,927,455 describes a bi-directional one-way clutch of the claw type, U.S. 6,244,965 describes a planar overrunning clutch, and U.S. 6,290,044 describes a selectable one-way clutch assembly for use in an automatic transmission.

U.S. 7,258,214 and U.S. 7,344,010 describe one-way clutch assemblies, and U.S. 7,484,605 describes an overriding radial clutch assembly or clutch.

A properly designed controllable OWC can have almost no parasitic losses in the "OFF" state. It can also be activated by electromechanics and has neither the complexity nor the parasitic losses of a hydraulic pump and valves.

Other related U.S. patent publications include: US 2015/0 014 116 ; US 2011/0 140 451 ; US 2011/0 215 575 ; US 2011/0 233 026 ; US 2011/0 177 900 ; US 2010/0 044 141 ; US 2010/0 071 497 ; US 2010/0 119 389 ; US 2010/0 252 384 ; US 2009/0 133 981 ; US 2009/0 127 059 ; US 2009/0 084 653 ; US 2009/0 194 381 ; US 2009/0 1422 07 ; US 2009/0 255 773 ; US 2009/0 098 968 ; US 2010/0 230 226 ; US 2010/0 200 358 ; US 2009/0 211 863 ; US 2009/0 159 391 ; US 2009/0 098 970 ; US 2008/0 223 681 ; US 2008/0 110 715 ; US 2008/0 169 166 ; US 2008/0 169 165 ; US 2008/0 185 253 ; US 2007/0 278 061 ; US 2007/0 056 825 ; US 2006/0 252 589 ; US 2006/0 278 487 ; US 2006/0 138 777 ; US 2006/0 185 957 ; US 2004/0 110 594 ; and the following writings U.S. 9,874,252 ; U.S. 9,732,809 ; U.S. 8,888,637 ; U.S. 7,942,781 ; U.S. 7,806,795 ; U.S. 7,695,387 ; U.S. 7,690,455 ; U.S. 7,491,151 ; U.S. 7,484,605 ; U.S. 7,464,801 ; U.S. 7,349,010 ; U.S. 7,275,628 ; U.S. 7,256,510 ; U.S. 7,223,198 ; U.S. 7,198,587 ; U.S. 7,093,512 ; U.S. 6,953,409 ; U.S. 6,846,257 ; U.S. 6,814,201 ; U.S. 6,503,167 ; U.S. 6,328,670 ; U.S. 6,692,405 ; U.S. 6,193,038 ; U.S. 4,050,560 ; U.S. 4,340,133 ; U.S. 5,597,057 ; U.S. 5,918,715 ; U.S. 5,638,929 ; U.S. 5,342,258 ; U.S. 5,362,293 ; U.S. 5,678,668 ; U.S. 5,070,978 ; U.S. 5,052,534 ; U.S. 5,387,854 ; U.S. 5,231,265 ; U.S. 5,394,321 ; U.S. 5,206,573 ; US 5,453,598 ; US 5,642,009 ; US 6,075,302 ; US 6,065,576 ; U.S. 6,982,502 ; US 7,153,228 ; U.S. 5,846,257 ; U.S. 5,924,510 ; and U.S. 5,918,715 .

A linear motor is an electric motor whose stator and rotor have been "unrolled" so that instead of torque (rotation) it generates a linear force along its length. The most common operating mode is a Lorentz-type actuator in which the force applied is linearly proportional to the current and the magnetic field. the US 2003/0 102 196 describes a bidirectional linear motor.

Linear stepper motors are used for positioning applications that require fast acceleration and high speeds with low payloads.

Mechanical simplicity and precise open-look operation are further features of linear stepper motor systems.

A linear stepper motor works on the same electromagnetic principles as a rotating stepper motor. The stationary part or plate is a passive serrated steel rod that extends the desired travel length. Permanent magnets, electromagnets with teeth and bearings are built into the moving elements or armatures / forcers. The actuator moves in two directions along the plate and provides discrete positions in response to the state of the currents in the field windings. In general, the motor is two-phase, but a greater number of phases can be used.

The linear stepper motor is well known in the art and operates on known principles of magnet theory. The stator or plate component of the linear stepper motor consists of an elongated, rectangular steel rod with a large number of parallel teeth, which extends over the distance to be traveled and functions like a rail for the so-called forcer component of the motor.

The plate is completely passive during the operation of the motor and all magnets and electromagnets are integrated into the forcer or armature component. The forcer moves in two directions along the plate and takes discrete positions in response to the state of the electrical current in its field windings.

United States patent documents that have the same assignee as the present application and are related to the present application include: U.S. 8,813,929 ; U.S. 8,888,637 ; U.S. 9,109,636 ; U.S. 9,121,454 , U.S. 9,186,977 ; U.S. 9,303,699 ; U.S. 9,435,387 ; and the US 2012/0 14 9 518 ; US 2013/0 256 078 ; US 2013/0 277 164 ; 2014/0 100 071 ; and US 2015/0 014 116 . The descriptions of all of the above patent documents are hereby incorporated by reference in their entirety.

Some of the above related patent documents belonging to the assignee of the present application describe a 2-position linear motor eCMD (Electrically Controllable Mechanical Diode). This device is a dynamic one-way clutch as both races (i.e., recess and pocket plates) rotate. The linear motor or actuator moves, which in turn moves the tappets coupled to the struts via a magnetic field generated by a stator. The actuator has a ring of permanent magnets that engages the clutch in two states, namely ON and OFF. Electricity is only consumed when transitioning from one state to the other. As soon as the desired state is reached, the magnet engages and the current is switched off.

the US 2015/0 000 442 , US 2016/0 047 439 and the U.S. 9,441,708 describe magnetically locking 2-way CMDs with 3 positions and a linear motor.

Mechanical forces resulting from local or remote magnetic sources, i.e. electrical currents and / or permanent magnets (PM), can be determined by examining the magnetic fields generated or "excited" by the magnetic sources. A magnetic field is a vector field that indicates the magnitude and direction of the influence of local or distant magnetic sources at any point in space. The strength or magnitude of the magnetic field at any point in any area of interest depends on the strength, amount, and relative location of the exciting magnetic sources and the magnetic properties of the various media between the locations of the exciting sources and the area of interest. Magnetic properties are material properties that determine "how light" or "how low" an excitation has to be in order to "magnetize" a unit volume of the material, i.e. to build up a certain magnetic field strength. In general, areas that contain ferrous material are much easier to “magnetize” than areas that contain air or plastic material.

Magnetic fields can be represented or described as three-dimensional lines of force, which are closed curves that move through areas of space and within material structures. If within a magnetic structure a magnetic "action" (generation of measurable mechanical forces) takes place, these lines of force are regarded as coupling or connection of the magnetic sources within the structure. Magnetic lines of force are coupled / connected to a power source when the current path encompasses all or a portion of the structure. Lines of force are coupled / connected to a PM source as they traverse the PM material, generally in the direction or the opposite direction of permanent magnetization. Individual lines of force or field lines that do not cross each other have a degree of tensile stress at every point along the line extension, similar to the tensile force in a stretched "rubber band" that is stretched in the form of the closed field line curve. This is the primary method of generating force through air gaps in a magnetic machine structure.

One can generally determine the direction of net force generation in the areas of a magnetic machine by examining the representations of the magnetic field lines within the structure. The more field lines (i.e. the more stretched rubber bands) run in one direction across an air gap between the machine elements, the greater the "tensile force" between the machine elements in this direction.

Metal Injection Molding (MIM) is a metalworking process in which finely powdered metal is mixed with a measured amount of binder to create a “feedstock” that can be processed by plastic processing equipment through a process known as injection molding. With the injection molding process, complex parts can be formed in a single operation and in large quantities. The end products are usually components that are used in various industries and applications. The type of flow of the MIM material is determined by the so-called rheology. With current facilities, processing is limited to products that can be molded into the mold with a typical volume of 100 grams or less per "shot". The rheology makes it possible to distribute this “shot” over several cavities, which makes the production of small, complicated products in large numbers cost-effective, which would otherwise be quite expensive with alternative or classic methods. The various metals that can be used in the MIM raw material are known as powder metallurgy and contain the same alloy components found in the industry standards for common and exotic metal applications. The shaped shape is then conditioned, the binder being removed and the metal particles being brought into the desired state of the metal alloy.

A "moment of force" (often just moment) is the tendency of a force to twist or turn an object. A moment is mathematically evaluated as the product of the force and a moment arm. The moment arm is the vertical distance between the point or the axis of rotation and the line of action of the force. Moment can be viewed as a measure of the tendency of the force to cause rotation about an imaginary axis through a point.

In other words: A “moment of force” is the rotational effect of a force around a certain point or a certain axis, measured as the product of the force and the perpendicular distance of the point from the line of action of the force. In general, clockwise moments are called “positive” and counterclockwise moments are called “negative” moments. When an object is in equilibrium, 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.

For the purposes of this application, the term "clutch" should be interpreted to include clutches or brakes in which one of the plates is drivably connected to a torque transmitting element of a transmission and the other plate is drivably connected to another torque transmitting element or anchored in relation to a transmission housing and is held stationary. The terms “connection”, “clutch” and “brake” can be used interchangeably.

SUMMARY OF EMBODIMENTS

An object of at least one embodiment of the present invention is to provide a free-running, frictionless clutch and control assembly, an engageable clutch assembly and one or more locking parts for use in such assemblies, wherein at least one of the locking parts has a center of gravity which is offset from a pivot axis of the locking part is, whereby the locking part is easier to move at high speeds.

To achieve the above purpose and other purposes of at least one embodiment of the present invention, a locking part is provided for the controllable transmission of torques between first and second coupling parts of a coupling arrangement. The first coupling part has a coupling surface with a pocket which is dimensioned and shaped so that it the locking member can accommodate and nominally hold. The locking member includes a first end face that engages a part, a second end face that engages a part, and an elongated main body portion between the end faces. The main body area is designed to allow the locking part to pivot about a pivot axis. The end faces of the locking part are movable between engagement and disengagement positions with respect to the coupling parts during the pivoting movement, as a result of which a one-sided torque transmission can take place between the coupling parts. A center of gravity of the locking part is offset with respect to the pivot axis, so that when the locking part is moved out of the engaged position, a moment arm of the center of gravity relative to the pivot axis decreases from a maximum value to essentially zero in the disengaged position in order to facilitate the disengagement of the locking part .

The main body portion may have a protruding spherical portion to enable pivoting movement.

The locking part can be a radial locking part.

The pivot axis can be located essentially in the middle of the spherical area.

The main body portion may have a protruding spherical portion which is offset from the center of gravity and which can be received in a pocket portion of the first coupling part to enable the pivoting movement. The first coupling part can be pivotably connected to the locking part via the spherical region.

The locking part can be a strut such as a ball socket strut.

To further accomplish the above and other purposes of at least one embodiment of the present invention, a detachable clutch assembly is provided. The arrangement includes a first and a second coupling part. The first coupling part has a coupling surface with a pocket that is sized and shaped to receive and nominally hold a locking part. The locking member includes a first end face that engages a part, a second end face that engages a part, and an elongated main body portion between the end faces. The main body area is designed to allow the locking part to pivot about a pivot axis. The end faces of the locking part are movable between engagement and disengagement positions with respect to the coupling parts during the pivoting movement, as a result of which a one-sided torque transmission can take place between the coupling parts. A center of gravity of the locking part is offset from the pivot axis, so that when the locking part is moved out of the engaged position, a movement arm of the center of gravity relative to the pivot axis decreases from a maximum value to essentially zero in the disengaged position in order to facilitate the disengagement of the locking part .

The main body portion may have a protruding spherical portion to enable pivoting movement.

The first coupling part can have a socket area in order to receive and hold the spherical area on a ball-socket interface and to enable the pivoting movement.

The locking part can be a strut, such as. B. a ball socket strut.

In further carrying out the above purpose and other purposes of at least one embodiment of the present invention, an overrun clutch and control assembly is provided. The arrangement includes a first and a second coupling part. The first coupling part has a first surface with a pocket sized and shaped to receive and nominally hold a locking part, and a second surface with a passage communicating with the pocket for an actuating force on the locking part to actuate the locking member in the pocket, so that the locking member moves between an engaged and a disengaged position. The locking member includes a first end face that engages a part, second end face that engages a part, and an elongated main body portion between the end faces. The main body area is designed to allow the locking part to pivot about a pivot axis. The end faces of the locking part can be moved between the engaged and disengaged positions during the pivoting movement with respect to the coupling parts, as a result of which a one-sided torque transmission can take place between the coupling parts. The center of gravity of the locking part is offset from the pivot axis, so that when the locking part is moved out of the engagement position, the moment arm of the center of gravity relative to the pivot axis decreases from a maximum value to essentially zero in the disengaged position in order to release the locking part from the second Coupling part to facilitate.

The main body portion may have a protruding spherical portion to enable pivoting movement.

The arrangement may further include a linear actuator received in the passage to provide the actuation force.

The linear actuator may include a solid plunger that moves between first and second axial positions to control the mode of operation of the assembly. The locking part can be biased by a biasing part so that it moves from the engaged position to the disengaged position.

The biasing element can include a return spring in order to exert a spring force on the locking part which counteracts the actuating force and the frictional force at the interface between the ball and socket.

While exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms of the invention. Rather, the words used in the specification are intended to be rather descriptive than restrictive, and it is to be understood that various changes can be made without departing from the spirit and scope of the invention. In addition, the features of the various embodiments can be combined to form further embodiments of the invention.

Figure list

• 1 Fig. 3 is a schematic, partially broken away view of an overrunning, frictionless, radial clutch and control assembly for coupling torque between first and second gears and an output shaft;
• 2 FIG. 13 is an enlarged view of FIG 1 to show details of the clutch and control assembly;
• 3 Fig. 3 is a schematic end view showing spring loaded latches or pawls in various pivotal positions including clutch and disconnect positions as actuated by cam surfaces of cams;
• 4th Figure 3 is a schematic end view of a second embodiment with locking members or pawls in various pivoting positions including clutch and disengagement positions actuated by cam surfaces of cams;
• 5 FIG. 13 is an enlarged side elevational view, partially broken away, of one of the locking members or cams of FIG 4th in its engagement position as actuated by a cam surface of a cam;
• 6th Figure 3 is an enlarged, partially broken away side view of another embodiment of one of the locking members or cams in its disengaged position;
• 7th FIG. 13 is a view similar to that of FIG 6th but with the locking member in its engaging position as actuated by a cam surface of cams;
• 8th FIG. 13 is a view similar to the views of FIG 5 and 7th which shows a return spring and frictional and return spring moments acting on the seesaw strut;
• 9 Fig. 3 is an enlarged, partially broken away side view of another embodiment of the locking member in its engaged position in solid lines and in its disengaged position in dashed lines;
• 10 FIG. 13 is a side elevational view, partially broken away, showing the spring-plunger actuation system of FIG 1 and 2 and for use with the locking part of FIG 8th shows, and
• 11 FIG. 13 is a view similar to that of FIG 10 , a plunger actuation system for use with the locking member of FIG 9 .

DESCRIPTION OF EMBODIMENTS

The following describes detailed embodiments of the present invention; however, it is to be assumed that the described embodiments are merely exemplary configurations of the invention, which can be implemented in various and alternative forms. The illustrations are not necessarily to scale; some features may be exaggerated or scaled down to show details of certain components. Therefore, the specific structural and functional details described herein are not to be understood as limiting, but merely as a representative basis to show those skilled in the art how to put the present invention into effect in various ways.

A free running, frictionless, radial clutch and control assembly according to at least one embodiment of the present invention is shown in FIGS 1 and 2 generally designated 10. The order 10 contains preferably one or more radial, claw-like clutch arrangements with bearings.

The order 10 includes a first pair of coupling parts 12th and 13th . The part 12th is a pocket plate and the part 13th contains a recess plate into which a first gear wheel 11 made of metal powder that is integrated on a shaft 14th can be rotatably mounted. The pocket plate has pockets 16 and the recess plate has recesses 17th . The parts 12th and 13th are relative to each other around a common axis of rotation 15th an output shaft 19th rotatably mounted. The part 13th is through a warehouse 21 rotatable on the shaft 19th stored. The coupling part 12th is about keyways 25th non-rotatably with the output shaft 19th tied together.

First locking parts or claws 23 swim freely in their pockets 16 and couple the first pair of parts 12th and 13th selectively mechanically together when in recesses 17th engage to relative rotation of the first pair of parts 12th and 13th with respect to each other in at least one direction around the axis 15th to prevent.

The order 10 also includes a second pair of coupling parts 32 and 33 designed to rotate relative to each other around the common axis of rotation 15th are stored, and second locking parts or claws 43 that are free in their pockets 36 swim to the second pair of parts 32 and 33 selectively mechanically couple together for relative rotation of the second pair of parts 32 and 33 to each other in at least one direction around the axis 15th to prevent. A second gear 31 made of metal powder is integral with the part 33 designed and rotatable on the shaft 14th appropriate. The part 33 is about stock 41 rotatable on the shaft 19th stored. The coupling part 32 is about keyways 45 non-rotatably with the output shaft 19th tied together.

The inner plate-shaped parts 12th and 32 have outer peripheral surfaces 18th respectively. 38 ( 2 ). The outer plate-shaped parts 13th and 33 have inner peripheral surfaces 20th and 40 attached to the outer peripheral surfaces 18th respectively. 38 adjoin radially inside and radially outside ( 2 ). Each of the parts 12th and 32 includes the bags 16 respectively. 36 around the axis 15th are angularly spaced around. Each of the pockets 16 and 36 has a closed end 22nd respectively. 42 and one open end that is the closed end 22nd or 42 axially opposite ( 2 ).

Each of the claws 23 and 43 is in their respective pocket 16 or 36 and is supported so that it faces the inner peripheral surface 20th or 40 their part 13th or 33 can pivot. The claws 23 and 43 will be in their respective pockets 16 and 36 by plate-like sleeves or brackets 27 and 47 kept that on their respective part 12th or 32 via locking or snap rings 28 and 48 are attached. The mounts 27 and 47 cover the open ends of the bags 16 respectively. 36 partially off.

The inner and outer peripheral surfaces 20th respectively. 18th define a first radial bearing interface attached to the closed end 22nd each of the bags 16 adjoins. The holder 27 has a storage area 29 having a bearing interface adjacent to the open end of each of the pockets 16 forms.

The inner and outer peripheral surfaces 40 respectively. 38 form a second radial bearing surface adjacent the closed end 42 each of the bags 36 . The holder 47 has a storage area 49 having a bearing interface adjacent to the open end of each of the pockets 36 Are defined.

As in 3 is best seen, includes the arrangement 10 several sets of actuators, indicated generally at 51, including biasing members such as springs 50 . Any actuator 51 includes a slide pin 52 with a head 53 which is received in an opening formed in the lower surface of an end portion 54 its respective claw 23 is trained. An opposite end area 55 every claw 23 is designed so that it fits into the recesses 17th intervenes. Each of the prestressing parts 50 presses its respective pin 52 to its respective claw 23 in the direction of the peripheral surface 20th of the part 13th to move.

As in the 1 and 2 shown includes the arrangement 10 also a three position linear stepper motor that is commonly used with 144 is designated. The stepper motor 144 is typically controlled by a controller and includes the stator structure or sub-assembly 135 with at least one coil 166 (three are shown) to generate a switched electromagnetic magnetic field and magnetic flux when the at least one coil 166 is excited.

The stepper motor 144 further includes a magnetically locking transmitter structure or actuator sub-assembly, generally with 170 and at least one bi-directionally movable connecting structure, such as a spring-loaded rod or shaft, generally with 172 is designated. Every pole 172 includes a pair of spaced apart, funnel-shaped (conical) cams 174 and 176 each of which has a contour surface 175 respectively. 177 has to the first and second locking parts 23 respectively. 43 on their respective contour surfaces 175 and 177 to cause a pivoting movement of the locking member with a small stroke between coupling and disengaging positions, as generally in FIG 3 shown.

The actuator sub-assembly 170 also includes a magnetic actuator, generally with 171 denotes the one with each pole 172 coupled and mounted for controlled reciprocating movement along the axis of rotation 15th relative to the first and second pairs of coupling parts 12th and 13th respectively. 32 and 33 between a first extended position corresponding to a first mode of the first pair of coupling parts 12th and 13th and a second extended position corresponding to a second mode of the second pair of coupling parts 32 and 33 is equivalent to. The cam 174 actuates the first locking part 23 in its extended position so that the first locking part 23 the first pair of coupling parts 12th and 13th for rotation with one another in at least one direction about the axis of rotation 15th couples.

The cam 176 actuates the second locking part 43 to get the second pair of coupling parts 32 and 33 for rotation with one another in at least one direction about the axis of rotation 15th to pair. The magnetic actuator 171 completes a magnetic flux path to effect a magnetic lock in the first and second extended positions. A control force caused by the magnetic flux is applied to the magnetic actuator 171 between the first and second extended positions along the axis of rotation 15th to move linearly.

The magnetic actuator 171 preferably includes a permanent magnet source 178 between a pair of annular field deflection rings 179 is arranged. The magnetic source 178 is preferably an annular rare earth magnet that is axially magnetized.

In other words, it controls the electromechanical device or the motor 144 the mode of operation of a pair of coupling devices, each of which has drive and driven parts adapted to rotate relative to one another about the common axis of rotation 15th the output shaft 19th are stored. Any driven part can be the pocket plate 12th or 32 and in the case of the drive part around the recess plate 13th or 33 Act. Each coupling device or arrangement can have two or more rocker arms or pawls 23 or 43 to selectively mechanically couple the parts of each clutch assembly together and change the mode of operation of each clutch assembly. Preferably the rocker arms or claws 23 and 43 at intervals around the axis 15th arranged (s. 3 ).

The actuator sub-assembly 170 is configured or adapted to be coupled to the parts or plates of the two coupling devices to rotate with them. The sub-arrangement 170 is on the output shaft 19th for rotation relative to the coils 166 around the axis of rotation 15th stored. The sub-arrangement 170 typically includes two or more bi-directional rods or shafts 172 . Any shaft area 180 or 182 the funnel-shaped cam 174 respectively. 176 is designed so that it during the selective pivoting movement of the locking part with a small stroke in an opening 184 or 186 slides in its respective coupling part. One socket 188 or 190 can the shaft areas 180 respectively. 182 in the openings 184 and 186 support gliding.

The actuator 171 is with the bars 172 for a selective bidirectional shifting movement along the axis of rotation 15th between a first position of the actuator 171 that corresponds to a mode (e.g. 1st gear) of the first coupling device (plate 12th and plate 13th ) and a second position of the actuator 171 corresponding to a mode (e.g. 2nd gear) of the coupling device (plate 32 and plate 33 ) corresponds, operationally connected. Two or more poles 172 can, as in 3 shown, be spaced from each other. The various modes can be locked and unlocked (ie, free running) modes and can be in either or both directions of rotation about the axis 15th lock.

A first magnetic control force is applied to the actuator 171 applied when the at least one coil 166 is energized to the actuator 171 to cause itself between its first, second and neutral positions along the axis 15th to move.

The actuator 171 includes a pair of spaced apart bias spring members 192 and 194 for each rod 172 to apply appropriate preload forces on an I-shaped hub or support 196 in opposite directions along the axis 15th exercise when the hub 196 between their first, second and third positions along the axis 15th emotional. The hub 196 has holes 197 for the sliding reception and support of the connecting rods or shafts 172 . When the carrier 196 moves, he pushes / pulls his respective springs 192 and 194 between opposing faces 195 of the wearer 196 and cylindrical areas 193 the funnel-shaped cam 174 and 176 .

The hub 196 rotates with the shaft 19th around the axis of rotation 15th . The hub 196 supports the interconnected wave ranges 199 of the waves 172 with a corresponding shifting movement along the axis of rotation 15th over in the holes 197 attached sockets 198 sliding off.

The part 12th may include spaced stops to indicate the extended positions of the actuator 171 define.

The actuator 171 also preferably includes a set of spaced guide pins (not shown) interposed between the inner surface of the part 12th and the outer surface of the hub 196 are arranged and along the axis of rotation 15th extend. The inner surface and the outer surface may have V-shaped grooves or recesses (not shown) formed therein to hold the guide pins. The hub 196 slides on the guide pins during the displacement movement of the hub 196 along the axis of rotation 15th . The guide pins guide the hub 196 on the part 12th . The hub 196 can also spread oil on the guide pins.

The stator subassembly 135 includes a ferromagnetic housing 167 with fingers spaced 168 and the electromagnetic inductive coils 166 that between adjacent fingers 168 are housed.

The actuator 171 is an annular part with a magnetic ring 178 between a pair of ferromagnetic back-up rings 179 lies. The magnetic control forces bring the fingers 168 and their corresponding backup rings 179 magnetically in a line when the coil is excited. These forces lock the actuator 171 in the two "ON" or extended positions and the "OFF" or neutral position. The Rings 179 are from the stator sub-assembly 135 applied to the actuator 171 to move.

Axial shift locking force in the permanent magnet (PM) linear motor (taken from US 9,435,387)

Let us now consider the magnetic field line diagram, which is also referred to as the magnetic flux line diagram and is shown in the cross-sectional view of the linear motor structure in question in FIG 13th the US 2015/0 014 116 is shown. This is a circularly symmetrical machine structure, the axial direction of movement of the transducer being shown in the x-direction and the radial direction being shown in the y-direction. The cross section of the stator 24 , 28 is a structure with three iron teeth 72 and two slots / coils 26th , wherein the slot openings face the movable element or transmitter via a radial air gap. The transmitter structure includes a single, axially magnetized PM ring 78 made of rare earths, the one between two iron field deflection rings 80 lies. The size of the various components can be estimated using the scaling specified in meters on the x and y axes. The magnetic field lines were determined with a commercially available software package for magnetic finite element analysis (MFEA). The solution shown in FIG. 13 applies in the event that no coil current flows in the stator windings and the transformer axial position is somewhat to the right of the “neutral” or middle position. The magnetic field lines that act solely on the transformer magnetic ring 78 “flow” in closed paths, with the majority of the lines flowing in a stator-iron-air-gap-transformer-iron / magnet circuit.

In general, the lines of force are limited to paths with much of the iron content, as the field in the iron material is easy to build up. If you look at the field lines that cross the air gap between the stator and the transformer, most of them follow a path that leads from the iron deflection rings of the transformer up and to the right to the iron tooth parts in the stator. If one imagines the field lines as stretched rubber bands, one would expect a net force that pulls the entire transformer to the right. The actual shear force density or x-directional shear stress, which in turn was determined from the MFEA analysis, at the axially directed center line of the air gap for this case is in 14A of the above-mentioned application. In 14A the shear stress can be seen both to the right and to the left, which can be reconciled with the distribution of the air gap field lines, which "tilt" both to the right and to the left along the air gap, but the total force (the integrated shear across the x-directional expansion of the air gap) shows a net force on the transducer to the right for this particular transducer position.

If you "scan" the transmitter position from left to right and recalculate the field lines at each position, you get a "slide show" of the generation of magnetic field lines based on the transmitter position. If the transducer structure is to the left of center or the neutral position, most of the flux lines will flow radially up and to the left of the transducer position, so a leftward force on the transducer body is expected. Conversely, as also shown in FIG. 13, the majority of the flux lines flow radially upwards and to the right when the transmitter structure is to the right of the central position, so that a force directed to the right on the transmitter body can be expected. A diagram of the actual total axial force on the transducer body as a function of the axial position, given in Newtons, is shown in 15A of the above registration. If the transducer is positioned to the right of center it will be pushed to the right due to its own magnetic field, and if it is positioned to the left of center it will be pushed further to the left. This is known as "locking" the assembly. The exact middle position, in which the left-right pushing force is balanced to exactly zero, is an unstable equilibrium point where even the smallest movements lead to forces. which tend to push the transformer away from the middle position. The other two points shown near the two axial ends of the stator structure, where the net translational force also passes through a zero value, are stable equilibrium points where tiny movements lead to the generation of position restoration forces.

Axial translational force in the permanent magnet linear motor in the event of a coil current (taken from US Pat. No. 7,435,387)

• Die Lösung für die Magnetfeldlinien für diese Situation ist in 16 der oben erwähnten Anmeldung dargestellt. Es wird angenommen, dass ein gleichmäßiger Strom, der gleichmäßig über die Wicklungsquerschnitte verteilt ist, aus der Seite heraus in Richtung des Betrachters in den Drähten der Spule in der Nut auf der rechten Seite des Stators fließt. Die axiale Magnetisierungsrichtung des Ringmagneten spielte in der reinen Haftkraftsituation von FIG.. 13 keine Rolle, ist aber in dem Fall der „doppelten“ magnetischen Erregung sehr wichtig. Für den gezeigten Fall wird die axiale Magnetisierung des Magneten nach rechts, in positiver x-Richtung, festgelegt und daher ist die Richtung oder Polarität der magnetischen Kraftlinien im geschlossenen „Fluss“-Pfad durch den Magneten allein eine Drehung gegen den Uhrzeigersinn. Die Polaritätsrichtung der zirkulierenden magnetischen Kraftlinien aufgrund des elektrischen Stroms ist durch die „Rechte-Hand-Regel“ gegeben. Wenn der Daumen der rechten Hand in die Richtung des Stromflusses in einem Draht oder einer Drahtspule zeigt und die Finger den Querschnitt des Drahtes oder der Spule umschließen, umschließen die magnetischen Feldlinien oder Flusslinien ebenfalls den Querschnitt des Drahtes oder der Spule und haben eine Umlaufrichtung in der gleichen Richtung wie die eingerollten Finger.

If you now consider the same machine structure as in 13th , but with the addition of a constant electric current in the two stator windings:

• The solution for the magnetic field lines for this situation is in 16 of the above-mentioned application. It is assumed that an even current, which is evenly distributed over the winding cross-sections, flows out of the side towards the viewer in the wires of the coil in the slot on the right-hand side of the stator. The axial direction of magnetization of the ring magnet played no role in the pure holding force situation of FIG. 13, but is very important in the case of "double" magnetic excitation. For the case shown, the axial magnetization of the magnet is set to the right, in the positive x-direction, and therefore the direction or polarity of the magnetic lines of force in the closed “flux” path through the magnet is only a counterclockwise rotation. The direction of polarity of the circulating magnetic lines of force due to the electric current is given by the “right-hand rule”. If the thumb of the right hand points in the direction of the current flow in a wire or a wire coil and the fingers enclose the cross section of the wire or the coil, the magnetic field lines or lines of flux also enclose the cross section of the wire or the coil and have a direction of rotation in the same direction as the curled fingers.

In 16 the magnetic lines due solely to the current in the left coil orbit this coil counterclockwise, while the magnetic lines due to the current in the right coil orbit this coil clockwise. The net or total generation of magnetic field lines, as in 16 is due to all three magnetic sources, the current in both coils and the transmitter magnet, so there are obviously areas in the machine structure where the individual sources of magnetic excitation are mutually reinforcing and adding, and there are areas in the machine structure, in which the individual sources of magnetic excitation cancel or subtract from one another. Since the coil current is reversible (plus or minus), the areas in which the two sources strengthen and weaken each other can be canceled out within the machine structure and especially within the machine air gap. This is the basis of the linear motor presented here with controllable / reversible direction of movement.

The flow of most of the lines of flux created by the transducer magnet alone resulted in a net force on the transducer to the right for the in 13th Transmitter position shown. But for the same transformer position, with the addition of the coil currents, for the case in 16 , the flux of the majority of the flux lines has shifted to a net orbit around the left coil and transducer structure. The majority of the flow lines now cross the air gap upwards and to the left, which is indicated by the illustration in 17A of the above-mentioned application. If the transformer was in a “stop” mode prior to introduction into the transformer magnet, the introduction of the coil current would be as in 16 then overcome the locking force to the right and generate a net motor force to the left, which forces the transmitter to move to the left. If the transformer moves and then crosses the middle or neutral position, the motor or switching current can then even be stopped, as the locking force now directed to the left, due to the magnet alone, takes the remaining left movement to a similar OFF-state locking position to the left of the Forces middle or neutral position. The net axial distance between the two locked positions to the left and right of the center position is then referred to as the “stroke length” of the machine.

A range of slideshow solutions for all the magnetic field lines within the linear motor structure with the same coil current drive as in the one in 16 The case shown, as a function of the axial position of the transmitter, similar to that given for the previous case of magnetic excitation alone, show that for the assumed level of the coil current, the net force on the transmitter structure is always directed to the left, regardless of the assumed value of the transmitter position.

Finally, the solutions for the magnetic field and the axial shear stress in the event that the coil current assists the drive, ie the drive in the direction of the magnetic locking force, are in the 18th respectively. 19A of the above-mentioned application. The polarity of the Coil currents in the event of 18th and 19A are simply from the in 16 and 17A reverse case shown, the transmitter position is the same as in the case of 16 and 17A . In this case, the coil current will drive in the direction of the magnetic locking force when the transmitter position has moved to the left from the center position.

In the 4th and 5 is a further embodiment of a first coupling part 12 ' , Recesses 17 ' a second coupling part (not shown) and locking parts or claws 23 ' shown with in a coupling surface of the coupling part 12 ' trained pockets 16 ' be recorded and held. Parts of the second embodiment which are identical or similar to parts of the first embodiment have the same reference number but a single main designation.

The second embodiment of the free-running, frictionless radial clutch and the control arrangement has essentially the same parts as the first embodiment, with the exception of the parts with a single main designation. The assembly preferably includes one or more radial, journal-type clutch assemblies.

The coupling and control arrangement of the second embodiment includes the first coupling part or the first pocket plate 12 ' and a second coupling part or a second recess plate which, as already mentioned, is not shown in its entirety, but rather its recesses 17 ' shown for simplicity. The first and the second part or the second plate are relative to one another about a common axis of rotation 15 ' an output shaft 19 ' rotatably mounted. The second part is rotatable on the shaft via bearings (not shown) 19 ' stored, and the first part 12 ' is rotationally fixed to the output shaft via keyways (not shown) 19 ' tied together.

The locking parts or claws 23 ' are in their respective pockets 16 ' through upper and lower spherical or base areas 200 ' and 202 ' the pocket plate 12 ' pivoted. Each of the plinth areas 200 ' and 202 ' has a concave bearing surface 204 ' respectively. 206 ' that are in appropriate storage areas 208 ' respectively. 210 ' of protruding, convex upper and lower tenons 212 ' respectively. 214 ' of the locking part 23 ' issue. Preferably the pivot pins provide 212 ' and 214 ' a smooth, curved support surface for the locking part 23 ' when it comes to its pivot axis 216 ' pivots between its engaged and disengaged positions with respect to the coupling parts or plates, so that a one-way torque transmission between the coupling parts can take place.

The upper and lower pivot pins 212 ' respectively. 214 ' extend from a main body area 218 ' of the locking part 23 ' . The main body area 218 ' extends between a dividing first end face 220 ' and a dividing second end face 222 ' .

The center of gravity (i.e. gravity) is essentially on the pivot axis 216 ' centered so that the locking part 23 ' is essentially centrifugally neutral or balanced. The centrifugal force acts on the center of gravity of the locking part 23 ' when turning the pocket plate 12 ' . The pivot axis 216 ' is located substantially midway between the first and second end surfaces 220 ' and 222 ' . Would be the locking part 23 ' not essentially centrifugal force neutral or balanced would be that for rotating the locking part 23 ' required force at high speeds such. B. 10,000 RPM high. While it is possible to counteract the problem of the unbalance of the locking part, such measures are often impractical. By the center of gravity of the locking part 23 ' on the axis of rotation 216 ' inside the pocket 16 ' is the locking part 16 ' essentially centrifugal force neutral or balanced, which makes the one-way clutch lighter and more compact.

One or more biasing parts, such as springs (not shown), are in recesses 224 ' arranged in their respective pockets 16 ' are formed around the end regions 54 ' their respective locking parts 23 ' to pretension and thereby the locking parts 23 ' in their respective pockets 16 ' to their disengaged positions. The spring forces act on the cam forces of the cams 174 ' contrary, since the undersides of the opposite end regions the locking parts 23 ' on the contour surfaces 175 ' slide. As in the first embodiment, there is a shaft portion 180 ' the funnel-shaped cam 174 ' set up to, during the pivoting movement of the locking part in an opening (in the 4th and 5 not shown) in the pocket plate 12 ' to slide.

Die Radialkraft nimmt also mit dem Quadrat der Geschwindigkeit zu. Ein Beispiel aus der Konstruktion des Verriegelungsteils in einer Kupplung, das 4,17 Gramm wiegt, bei einer Drehzahl von 15.000 U/min entspricht also einer Radialkraft des Verriegelungsteils in ihrer Tasche von 151 lbs (etwa 672 N). Dies sind die neuen Realitäten, mit denen die eCMD-Konstrukteure nun konfrontiert sind. Das Steuersystem (elektromechanischer Bereich) der eCMD muss in der Lage sein, das Verriegelungsteil bei diesen enormen Radialkräften zu drehen. Diese Radialkräfte werden von der Außenwand der Taschenplatte nicht aufgenommen. Es entsteht eine Reibungskraft, die ein der gewünschten Drehung des Verriegelungsteils entgegengesetztes Moment erzeugt. Die Gleichung für die Reibungskraft (Formel) lautet: $${\text{F}}_{\text{r}}=\mathrm{\mu {\rm N}}{\text{ mit N=F}}_c\text{ und }\mathrm{\mu }=\text{Reibungskoeffizient}$$

Die Gleichung für das entgegengesetzte Moment ist ... $$\text{M}={\text{F}}_{\text{r}}\text{r}$$

Wobei r = der Momentarm ist, d.h. der Abstand zwischen dem Drehpunkt und dem Kontaktpunkt des Verriegelungsteils mit der Tasche.With the increasing acceptance of eCMDs as a viable technology for advanced hybrids and EVs, the specifications and requirements for the clutches are increasing rapidly. E-motors are characterized by a high torque at zero / low speed and can turn three times faster than conventional combustion engines. eCMDs must be able to be switched on and off at speeds of at least 15,000 rpm. The formula for the radial force produced by rotation is $${\text{F.}}_{\text{c}}={\text{MV}}^2/\text{r}$$

The radial force increases with the square of the speed. So an example of the design of the locking part in a coupling that weighs 4.17 grams at a speed of 15,000 rpm corresponds to a radial force of the locking part in its pocket of 151 lbs (about 672 N). These are the new realities that the eCMD designers are now faced with. The control system (electromechanical area) of the eCMD must be able to turn the locking part with these enormous radial forces. These radial forces are not absorbed by the outer wall of the pocket plate. A frictional force is created which generates a moment opposite to the desired rotation of the locking part. The equation for the frictional force (formula) is: $${\text{F.}}_{\text{r}}=\mathrm{\mu {\rm N}}{\text{with N = F}}_c\text{and}\mathrm{\mu }=\text{Coefficient of friction}$$

The equation for the opposite moment is ... $$\text{M.}={\text{F.}}_{\text{r}}\text{r}$$

Where r = the moment arm, ie the distance between the pivot point and the contact point of the locking part with the pocket.

The smaller the value of M, the easier it is for the electromechanical section of the eCMD to turn the locking part. For a given coupling speed, the parameters that can be manipulated to reduce the torque are the mass of the locking part, the value of µ and the length of the moment arm. The following description refers to the 6th and 7th Embodiment shown and its objective to reduce the torque arm.

In the 6th and 7th is a further embodiment of a first coupling part 12 " , of recesses 17 " a second coupling part 13 " and a locking member or a pawl 23 " shown in a in a coupling surface of the coupling part 12 " trained pocket 16 " is recorded and held. Parts of the third embodiment that are the same or similar to parts of the first and second embodiment have the same reference numerals but are primed twice.

The third embodiment of the freewheeling frictionless radial clutch and control assembly has essentially the same parts as the first and second embodiments, with the exception of the parts that are double-painted. The arrangement preferably includes one or more radial clutch assemblies of the pawl type having a bearing.

The coupling and control arrangement of the third embodiment includes the first coupling part or the first pocket plate 12 " and the second coupling part or the second recess plate 13 " which, as already mentioned, is not shown in its entirety, but its recesses 17 " shown for simplicity. The first and the second part or the second plate are mounted rotatably relative to one another about a common axis of rotation of an output shaft (not shown). The second part is rotatably mounted on the shaft via bearings (not shown), and the first part 12 " is non-rotatably connected to the output shaft via keyways (not shown).

The locking part or the claw 23 " will be inside the bag 16 " through upper and lower spherical or base areas 200 " and 202 " the pocket plate 12 " held. The base area 202 " has a concave support surface 206 " that are attached to the corresponding support surface 210 " a protruding, convex lower pin 214 " of the locking part 23 " is adapted. Preferably the pin offers 214 " a smooth, beaded contact surface of the locking part 23 " when it comes to its pivot axis 216 " pivots between its engaged and disengaged position with respect to the coupling parts or plates, so that a one-way torque transmission between the coupling parts can take place.

The design of the 6th and 7th shows a modification of the radial claw and pocket of the 4th and 5 . The radial claw 23 " is a MIM part with a shaped oval hole 240 " centered around the center of gravity of the locking part. The pocket plate has a pressed-in hardened and polished pin 242 " with a diameter of about 2 mm. The width of the slot in the oval hole is about 2.2 mm. Would be the pen 242 " does not exist, the contact of the radial claw at point A would take place with a moment arm of C. With the pen 242 " if the sliding contact occurs at point B with a moment arm of D. The advantage is that D is much shorter than C, then M is reduced linearly as the length of the moment arm is reduced.

The radial claw 23 " and the pen 242 " could both be provided with a friction-reducing coating such as Teflon, which reduces the µ.

The reason that the pen 242 " not tight in a hole in the radial claw 23 " fits, lies in the fact that when the strut is locked and loaded 23 " a game to the pen 242 " must be present. The function of the pen 242 " is to create a reaction point when going from OFF to ON and ON to OFF. It should not be loaded beyond the load of the radial force generated by the rotation, hence the oval through hole 240 " .

The lower pivot point 214 " extends from a main body area 218 " of the locking part 23 " . The main body area 218 " extends between a partially engaging first end surface 220 " and a partially engaging second end surface 222 " .

The center of gravity (i.e. gravity) is essentially on the pivot axis 216 " centered so that the locking part 23 " is essentially centrifugally neutral or balanced. The centrifugal force acts on the center of gravity of the locking part 23 " when turning the pocket plate 12 " . The pivot axis 216 " is located substantially midway between the first and second end surfaces 220 " and 222 " . When the locking part 23 " is essentially centrifugal force neutral or balanced, is the force that is required to the locking part 23 " to rotate, high at high speeds like 10,000 rpm. Although it is possible to counteract the problem of the unbalance of the locking part, such measures are often impractical.

By the center of gravity of the locking part 23 " on the axis of rotation 216 " inside the pocket 16 " is the locking part 23 " Essentially centrifugal force neutral or balanced, which makes the one-way clutch lighter and more compact.

One or more biasing parts, such as springs (not shown), are in the pocket 16 " trained recess 224 " arranged around the end regions 54 " of the locking part 23 " to pretension and thereby the locking part 23 " in his pockets 16 " to push into its disengaged positions. The spring force acts against the cam forces of the cams 174 " by removing the underside of the opposite end portions of the locking part 23 " on the contour surface 175 " rests. As in the first embodiment, there is a shaft portion 180 " the funnel-shaped cam 174 " set up to, during the pivoting movement of the locking part in an opening (in the 6th and 7th not shown) in the pocket plate 12 " to slide.

In 8th is a locking member or strut, indicated generally at 323, in its coupled position between its pocket plate 312 and its recess plate 313 its clutch assembly, generally designated 311, is shown. Theoretically there is no net moment attempting the locking part 323 rotate in either direction while the clutch is rotating. The rotation of the locking part 323 a return spring is used to switch to the "OFF" position 325 that is in a recess 324 is arranged and directly on the locking part 323 works. The return spring 325 (see return spring torque 313 ) must have frictional forces (see frictional torque 315 ) to make sure that the locking part 323 from a recess 317 the recess plate 313 freaks out.

The spring-tappet actuator system of the 1 , 2 and 10 is a "fire and forget" system, because the ram or the rod 172 by a spring 194 is biased to apply an “ON” force to the locking part 323 exercise in a tooth-on-tooth position. Thus, the locking part 323 snap into place as soon as the relative movement between the panels 312 and 313 provides a recess.

In other words, the center of gravity of the locking part is located 323 and the axis of rotation 316 of the locking part 323 in the same place. That means that it is between the center of gravity and the pivot point 316 of the locking part 323 there is no momentary alarm, as in 8th shown. If there is no moment arm, there will be no moment created by the center of gravity trying the locking part 323 to turn.

When the clutch assembly 311 is switched off at a high speed, the only forces and the corresponding moments acting on the rotation of the locking part 323 act, the return spring 325 that is the OFF spring torque 313 generated, and the frictional torque 315 that acts in the ON (opposite) direction. So that the locking part 323 switches off, the return spring torque must 313 be greater than the frictional torque 315 . When the coefficient of friction between the locking part 323 and the pocket plate 312 is low, this switches to the locking part 323 acting net torque the locking part 323 THE END. Oil, surface condition, inadequate center of gravity relative to the pivot point 316 can help reduce the sum of the return spring torque 313 opposite moments the return spring torque 313 overcomes. This would lead to the locking part 323 does not turn to the OFF position. The clutch assembly 311 cannot switch off after the actuator system has moved to the OFF position. This means that the return spring torque 313 that is used to turn off the locking part 323 acts at about 9000 rpm or more, is not robust. The net breaking torque must be increased to ensure that the locking part 323 to 100 % of the time is turned off.

Referring to the 9 and 11 For example, a ball socket locking member, generally designated 423, is formed in accordance with at least one embodiment of the present invention. The ball socket locking part 423 has a focus 417 that of the point of rotation or the axis 416 is offset, resulting in a net OFF torque when the clutch assembly, indicated generally at 411, rotates.

A return spring 425 acts directly on the locking part 423 and becomes in addition to the new locking moment (i.e. center of gravity moment arm 419 ) used to the locking part 423 to turn to "OFF". In this way, the OFF force is significantly increased to the locking part 423 reliably from its coupling or recess plate 413 to solve.

As a result, a greater "ON" force is now required from the actuation system, which is shown in 11 generally indicated at 430 to overcome this increased "OFF" force. The sum of these new “OFF” forces would become the spring 194 of the actuation system of 10 overcome and make the magnetic locking of the system in the tooth-on-tooth position inadequate. The system off 10 is modified to the system 430 the 11 as described below.

The system 430 is not a "Fire and Forget" system like the system of 10 , whereby the use of the "massive ram actuation system" 430 from 11 is made possible. The “massive ram actuation system” 430 has fewer components compared to the system of 10 that the feather 194 , a plunger, a sleeve or a bearing 198 and plunger fasteners (not shown).

• 1.) Seine Kugelpfannen-Konstruktion hält den Kontakt zwischen dem Verriegelungsteil 423 und seiner Taschenplatte 412 auf die Kugelpfannen-Zwischenfläche beschränkt, außer wenn das Verriegelungsteil 423 in seiner verriegelten oder Eingriffs-Position ist, wie in 9 gezeigt. Dadurch soll der Reibungsmomentarm (zwischen Kugel und Pfanne) klein gehalten werden, bis der volle Hub des Betätigungssystems 430 beim Übergang von AUS zu EIN erreicht ist. Dadurch wird die Kontaktfläche von der Rückwand der Tasche ferngehalten, während sie sich dreht, bis die EIN-Position erreicht ist. Dies reduziert den Axialkraftbedarf des Linearmotor-Betätigungssystems 430 der 11 beim Einschalten und unterstützt die Rückstellfeder 425 und das Fliehkraftmoment beim Ausschalten.
• 2.) Die Umschlingung der Taschenplatte 412 (Buchse) um einen Kugelbereich 421 des Verriegelungsteils 423 ist weit genug, um das Verriegelungsteil 423 in ihrer Tasche in der Taschenplatte 412 zu halten. Dies unterstützt die Funktion von Nr. 1 unmittelbar darüber und hält das Verriegelungsteil 423 in der Tasche fest.
• 3.) Der Schwerpunkt bildet einen Momentarm in der EIN-Position des Verriegelungsteils 423, so dass:
  • (1) der Momentenarm 419 seine maximale Länge 419 für den Drehbereich in der EIN-Stellung hat und
  • (2) in der AUS-Stellung die Länge des Momentenarms 419 vom CG aus Null ist (in der Phantomstellung).
  Dieses Merkmal gewährleistet ein maximales Moment 419 in der AUS-Richtung, wenn das Verriegelungsteil 423 vollständig eingeschaltet ist (durchgezogene Linien) und kein AUS-Moment, wenn das Verriegelungsteil 423 in der AUS-Position ist (unterbrochene Linien), was es dem Linearmotor des Betätigungssystems 430 erleichtert, das Verriegelungsteil 423 beim Einschalten in Drehung zu versetzen.
• 4.) Die „wippenartige“ Form des Verriegelungsteils 423 unterscheidet sich in wichtigen Punkten von Wippen oder Verriegelungsteilen des Standes der Technik:
  • (1) Die Form ist speziell für eine radiale STEUERBARE Kupplung, wie hierin beschrieben, entworfen;
  • (2) Das Verriegelungsteil 423 ist für eine 2-Wege-Kupplung und ist nicht passiv;
  • (3) Das Verriegelungsteil 423 läuft nicht über, es wird ausgeschaltet und bleibt ausgeschaltet, wenn es kein Drehmoment überträgt; und
  • (4) Das Verriegelungsteil 423 hat mehr Umhüllung um die Spitze (d.h. den Kugelbereich 421) des Verriegelungsteils 423, um ein echtes Kugelgelenk zu schaffen.

The locking part 423 from 9 has the following characteristics:

• 1.) Its ball socket construction keeps the contact between the locking part 423 and its pocket plate 412 limited to the ball socket interface, except when the locking member 423 is in its locked or engaged position, as in FIG 9 shown. This is intended to keep the low friction torque (between the ball and socket) small until the actuation system has reached its full stroke 430 is reached during the transition from OFF to ON. This will keep the contact surface away from the back wall of the bag while it rotates until the ON position is reached. This reduces the axial force requirement of the linear motor actuation system 430 the 11 when switching on and supports the return spring 425 and the centrifugal force when switching off.
• 2.) The wrapping of the pocket plate 412 (Socket) around a spherical area 421 of the locking part 423 is far enough to the locking part 423 in her pocket in the pocket plate 412 to keep. This assists the function of # 1 immediately above and holds the locking part 423 stuck in the pocket.
• 3.) The center of gravity forms a moment arm in the ON position of the locking part 423 , so that:
  • (1) the moment arm 419 its maximum length 419 for the range of rotation in the ON position and
  • (2) in the OFF position, the length of the moment arm 419 from the CG is zero (in the phantom position).
  This feature ensures maximum moment 419 in the OFF direction when the locking part 423 is fully switched on (solid lines) and no OFF moment when the locking part 423 is in the OFF position (broken lines) what it is to the linear motor of the actuation system 430 facilitates the locking part 423 to rotate when switched on.
• 4.) The "rocker-like" shape of the locking part 423 differs in important points from rockers or locking parts of the state of the art:
  • (1) The shape is specifically designed for a radial STEERABLE coupling as described herein;
  • (2) The locking part 423 is for a 2-way coupling and is not passive;
  • (3) The locking part 423 does not overflow, it turns off and stays off when it is not transmitting torque; and
  • (4) The locking part 423 has more wrap around the tip (i.e. the sphere area 421 ) of the locking part 423 to create a real ball joint.

As already mentioned, the locking part has 423 a claw geometry in which the center of gravity 417 not at its pivot point or its axis 416 lies. The location of the center of gravity in relation to the pivot point 416 ensures the maximum amount of linear momentum 419 in the ON position, which is a centrifugal OFF moment of the locking member 423 generated. This centrifugal OFF torque is in addition to the return spring torque. The sum of these two moments now exceeds the frictional moment at around 9000 rpm and more, which ensures that the locking part 423 is turned off. When the locking part 423 turns from ON to OFF, the moment arm picks up 419 of focus 417 relative to the pivot point 416 of the locking part 427 off, so that with the fully OFF position the length of the moment arm 419 is equal to zero and therefore no centrifugal force acts in the OFF position. This property helps the actuation system 430 to move the actuator from OFF to ON more easily. There is initially no centrifugal resistance to the locking part 423 move from OFF to ON.

• - Die Stator-Unter-Anordnung 135 bleibt nun länger eingeschaltet, um den Laufringen oder Kupplungsteilen 412 und 413 die nötige Zeit zu geben, sich in einen verriegelten Zustand zu drehen.
• - Für eine bestimmte Zeit, in der die Stator-Unter-Anordnung 135 eingeschaltet ist, muss eine Mindest-Relativgeschwindigkeit zwischen den Laufringen 412 und 413 vorhanden sein, damit sie sich aus der Zahn-auf-Zahn-Stellung in die verriegelte Position drehen können. Der maximale Abstand (S=RO), den das Verriegelungsteil 423 relativ zu den Aussparungen der Aussparungsplatte 413 zurücklegen muss, ist gleich dem Spiel der Kupplung 411 in Radiant x Radius der Aussparungsplatte ID/OD.
• - Die „Fire and Forget“-Funktion ist nicht mehr gegeben, so dass die Notwendigkeit der Stößelfeder 194 entfällt. An dieser Stelle kommt der „massive Stößel“ aus 11 ins Spiel.
• - Die Steuerstrategie wird komplizierter, wenn die „Fire and Forget“-Funktion entfällt.
• - Die Stößelhülsen entfallen ebenfalls, da es keine Relativbewegung zwischen den Stößeln und dem Aktuator mehr gibt.
• - Die Anforderungen an die magnetische Einschaltverriegelung können etwas reduziert werden, da sie den Aktuator nicht mehr aus der Zahn-auf-Zahn-Stellung EIN-schalten müssen. Die einzige Funktion der Verriegelung besteht darin, EIN und AUS zu halten.

The locking part 423 solves the aforementioned OFF problem when disengaging at high speed. However, this increases the required axial force of the actuator tappet of the actuation system 476 when going from OFF to ON to overcome these new OFF forces. The actuation system 430 dispenses with the “fire and forget” control strategy / function of the previous actuation system and uses the ON stator forces to move the actuator from a tooth-on-tooth position to an ON position. The use of the coil 166 to turn the clutch ON means that the system is 430 in the following respects from the actuation system in 10 differs:

• - The stator sub-assembly 135 now remains switched on longer, around the races or coupling parts 412 and 413 to give the necessary time to rotate into a locked state.
• - For a certain time in which the stator sub-arrangement 135 is switched on, there must be a minimum relative speed between the races 412 and 413 be present so that they can rotate from the tooth-on-tooth position to the locked position. The maximum distance (S = RO) that the locking part 423 relative to the recesses of the recess plate 413 has to travel is equal to the play of the clutch 411 in radians x radius of the recess plate ID / OD.
• - The "Fire and Forget" function is no longer available, so that the plunger spring is necessary 194 not applicable. This is where the “massive ram” comes out 11 in the game.
• - The control strategy becomes more complicated if the "Fire and Forget" function is no longer available.
• - The plunger sleeves are also omitted since there is no longer any relative movement between the plungers and the actuator.
• - The requirements for the magnetic switch-on interlock can be reduced somewhat, as you no longer have to switch the actuator ON from the tooth-on-tooth position. The only function of the interlock is to hold ON and OFF.

While exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms of the invention. Rather, the words used in the description are rather descriptive than restrictive, and it is to be understood that various changes can be made without departing from the spirit and scope of the invention. In addition, the features of different embodiments can be combined to form further embodiments of the invention.

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

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Claims (20)

A locking member for controllably transmitting torque between first and second coupling parts of a clutch assembly, the first coupling part having a coupling surface with a pocket which is sized and shaped to receive and nominally hold the locking part, the locking part comprising: a first end face engaging a part, a second end surface engaging a part, and an elongated main body portion between the end surfaces, the main body portion being configured to permit pivotal movement of the locking member about a pivot axis, the end surfaces of the locking member being movable with respect to the coupling members during pivotal movement between engaged and disengaged positions, thereby providing a one-way Torque can be transmitted between the coupling parts, and the center of gravity of the locking part is offset from the pivot axis so that when the locking part moves out of the engaged position, a moment arm of the center of gravity relative to the pivot axis from a maximum value to essentially zero in the disengaging Position decreases to facilitate the disengagement of the locking part. Locking part after Claim 1 wherein the main body portion has a protruding spherical portion to enable pivoting movement. Locking part after Claim 1 wherein the locking part is a radial locking part. Locking part after Claim 2 , wherein the pivot axis is arranged substantially in the middle of the spherical area. Locking part after Claim 1 wherein the main body portion has a protruding spherical portion which is offset from the center of gravity and can be received in a base portion of the first coupling part to enable the pivoting movement, wherein the first coupling part can be pivotably connected to the locking part via the spherical region. Locking part after Claim 3 , wherein the locking part is a strut. Locking part after Claim 6 , wherein the locking part is a ball socket strut. A snap-in coupling assembly comprising: first and second coupling parts, the first coupling part having a coupling surface with a pocket sized and shaped to receive and nominally hold a locking part, the locking part comprising: a first end face engaging a part, a second end surface engaging a part, and an elongated main body portion between the end surfaces, the main body portion being configured to permit pivotal movement of the locking member about a pivot axis, the end surfaces of the locking member being movable during pivotal movement between engaged and disengaged positions with respect to the coupling members, thereby providing a one-way Torque can be transmitted between the coupling parts, and wherein the center of gravity of the locking part is offset from the pivot axis so that when the locking part moves out of the engaged position, a moment arm of the center of gravity relative to the pivot axis from a maximum value to essentially zero in the disengagement -Position decreases to make it easier to disengage the locking part. Arrangement according to Claim 8 wherein the main body portion has a protruding spherical portion to enable pivoting movement. Arrangement according to Claim 9 wherein the first coupling part has a socket area in order to receive and hold the spherical area at a ball-socket interface and to enable the pivoting movement. Arrangement according to Claim 8 , wherein the locking part is a strut. Arrangement according to Claim 11 , wherein the locking part is a ball socket strut. An overrunning clutch and control assembly comprising: first and second clutch members, the first clutch member having a first surface with a pocket sized and shaped to receive and nominally retain a locking member, and a second surface with a passage which is in communication with the pocket to transmit an operating force to the locking member to actuate the locking member within the pocket so that the locking member moves between an engaged and a disengaged position, the locking member comprising: one on one Part engaging first end face; a second end surface engaging a part, and an elongated main body portion between the end surfaces, the main body portion being configured to permit pivotal movement of the locking member about a pivot axis, the end surfaces of the locking member being movable between the engaged and disengaged positions with respect to the coupling members during the pivotal movement; whereby a one-way torque transmission can take place between the coupling parts, and wherein the center of gravity of the locking part is offset from the pivot axis so that when the locking part moves out of the engaged position, a moment arm of the center of gravity relative to the pivot axis from a maximum value to im Substantially zero decreases in the disengaged position in order to facilitate the release of the locking part from the second coupling part. Overrunning clutch and control arrangement according to Claim 13 wherein the main body portion has a protruding spherical portion to enable pivoting movement. Overrunning clutch and control arrangement according to Claim 14 wherein the first coupling part has a socket area in order to receive and hold the spherical area at a ball-socket interface and to enable the pivoting movement. Overrunning clutch and control arrangement according to Claim 13 , wherein the locking part is a ball socket strut. Overrunning clutch and control arrangement according to Claim 13 , further comprising a linear actuator received in the passage to provide the actuation force. Overrunning clutch and control arrangement according to Claim 17 wherein the linear actuator includes a solid plunger that moves between first and second axial positions to control the mode of operation of the assembly. Overrunning clutch and control arrangement according to Claim 17 wherein the locking member is biased from the engaged position toward the disengaged position by a biasing member. Overrunning clutch and control arrangement according to Claim 15 which also has a return spring in order to exert a spring force on the locking part which counteracts the actuating force and a frictional force at the interface between the ball and socket.

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