GB2270958A - Power transmitting assembly - Google Patents

Power transmitting assembly Download PDF

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Publication number
GB2270958A
GB2270958A GB9318739A GB9318739A GB2270958A GB 2270958 A GB2270958 A GB 2270958A GB 9318739 A GB9318739 A GB 9318739A GB 9318739 A GB9318739 A GB 9318739A GB 2270958 A GB2270958 A GB 2270958A
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United Kingdom
Prior art keywords
assembly
rotating member
rotatable
cam
cam follower
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB9318739A
Other versions
GB9318739D0 (en
GB2270958B (en
Inventor
David R Weilant
Craig B Fowler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
Original Assignee
Borg Warner Automotive Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Borg Warner Automotive Inc filed Critical Borg Warner Automotive Inc
Publication of GB9318739D0 publication Critical patent/GB9318739D0/en
Publication of GB2270958A publication Critical patent/GB2270958A/en
Application granted granted Critical
Publication of GB2270958B publication Critical patent/GB2270958B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/30—Arrangement or mounting of transmissions in vehicles the ultimate propulsive elements, e.g. ground wheels, being steerable
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B60K17/20—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing in which the differential movement is limited
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/348—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed
    • B60K17/35—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches
    • B60K17/3515—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having differential means for driving one set of wheels, e.g. the front, at one speed and the other set, e.g. the rear, at a different speed including arrangements for suppressing or influencing the power transfer, e.g. viscous clutches with a clutch adjacent to traction wheel, e.g. automatic wheel hub
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/04—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for differential gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K23/00—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for
    • B60K23/08—Arrangement or mounting of control devices for vehicle transmissions, or parts thereof, not otherwise provided for for changing number of driven wheels, for switching from driving one axle to driving two or more axles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/14—Clutches in which the members have interengaging parts with clutching members movable only axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/118—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with interengaging jaws or gear teeth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D2011/002—Clutches in which the members have interengaging parts using an external and axially slidable sleeve for coupling the teeth of both coupling components together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H2048/204—Control of arrangements for suppressing differential actions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/34—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators
    • F16H2048/346—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using electromagnetic or electric actuators using a linear motor

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

A locking hub assembly (18) for operatively engaging and disengaging a power driven axle (26) to a wheel includes a first rotatable assembly (16, 40, 42) in communication with the wheel, a second rotatable assembly (66) in communication with the power driven axle (26) having an axially movable rotating member (68), means (98, 102) for moving the rotating member and a nonrotatable electromagnetic means (122, 166) fixed for nonrotation about the axle (26) for activating the moving means (98, 102). The rotating member (68) is moved between a first position, wherein the first rotatable assembly (16, 40, 42) operatively engages the second rotatable assembly (66), and a second position, wherein the first rotatable assembly (16,40, 42) is disengaged from the second rotatable assembly (66). A bevel gear differential (FIGS 20 or 24) has an electromagnetically actuated lock that selectively locks an axle shaft to a differential case so that the differential case and axle shafts rotate in unison. The electromagnetically actuated lock may be engaged and disengaged manually or automatically in response to wheel slip. <IMAGE>

Description

2270958 Power Transmitting Assembly Our U.S. patent application No.
954,854 discloses several embodiments of an electromagnetically actuated locking hub assembly for part time four wheel drive vehicles and a method of actuating the locking hub assembly.
Our U.S. patent application No. 111,190 includes other mechanical power transmitting devices in addition to the locking hub assembly of the earlier patent application, such as a locking differential where one drive member of the diffiarential is locked to another drive member of the differential for changing the mode of operation of the differential.
Our U.S. patent application No. 111,190 is directed to the concept of an electromagnetically actuated power transmitting assembly that has at least two rotatable drive members that are engaged to rotate in unison or disengaged to rotate relative to each other and more particularly to such power transmitting assemblies that can be used with wheel driven and/or engine driven members of automotive vehicles.
With respect to differentials, U.S. Patent 5,030,181 granted to Walter Keller July 9, 1991 discloses a bevel gear differential that has an electromagnetic clutch for positively locking one of the side gears to the differential case. The electromagnetic clutch includes an armature plate that is attached to a sleeve that is slidably splined on the shaft of side gear and that has clutch teeth. When the electromagnet is energized, sleeve slides to the right as view in Figure 1 of the patent drawincy ta engage the clutch teeth of the sleeve with cooperating clutch teeth on the case locking the side gear to the case. When the electromagnet is deenergized, the clutch is disengaged BWA-91096A - 2 - by a return spring. This lock-up arrangement requires continuous energization of the electromagnet for clutch engagement.
U.S. Patent 5,092,825 granted to Edward J.
Goscenski and David A. Janson March 3, 1992 discloses a modulating limited slip differential in which an electromagnetic actuator mounted on the differential housing frictionally retards an actuating plate (cam) that is rotationally mounted on the differential case.
Relative rotation of the actuating plate with respect to the differential case translates balls (cam follower) that apply pressure to clutch pack creating a frictional bias between one side gear and the case.
U.S. Patent 4,776,234 granted to Dennis W.
Shea October 11, 1988 discloses a modulating limited slip differential in which a coil attached to the housing magnetizes a shell which is attached to a differential case when it is energized. This pulls an armature axially causing pressure to be applied to a clutch pack via mechanism creating a frictional bias between one side gear and the case. These modulating arrangements also require continuous energization of the electromagnet for clutch engagement. 25 With respect to hub locks, it is desirable to provide increased--- automation in f our-wheel drive vehicles and in particular to permit selective engagement and disengagement of half of the drive train under the complete control of the operator. Numerous approaches have been taken to permit engagement and disengagement between two wheel drive mode and four wheel drive mode.
one such approach employs a mechanism which is normally disengaged to allow the wheels to rotate independently of the front drive system. This system BWA-91096A - 3 - requires that the operator lock each clutch manually to engage the front drive axle and wheels, and to unlock them manually to disengage.
Another approach provides an overrunning clutch which engages automatically when power is applied to the f ront drive axle and when operation is in the drive mode. However, such an overrunning clutch disengages automatically upon operation in the coast mode. In other words, the overrunning clutch engages when the rotational speed of the axle tends to exceed the rotational speed of the wheel, but disengages when the rotational speed of the wheel tends to overrun that of the axle. Such overrunning clutches generally provide some means by which the operator may override manually to insure locking engagement between the axle and wheels.
Yet another approach provides a clutch which operates in response to the application of torque to the front drive axle to move pins into slots so as to engage the axle with its associated wheels. Although this type of clutch will effect engagement in either the drive or coast mode of operation, there is the possibility that the pins will slip out during movement between drive and coast in which case the clutch would disengage and then re-engage automatically.
For a more detailed discussion of various mechanically actuated locking hub assemblies reference is made to U.S. Patent Nos. 4,192,411 and 4,281,749 assigned to the Borg-Warner Corporation.
Further approaches have been employed to actuate a locking hub assembly such as by the use of a supplementary power source to actuate a locking hub assembly such as by the use of a supplementary power source to actuate a drive gear, or to employ pneumatic systems where vacuum or pressure motors or valves cause BWA-91096A - 4 - the drive gear to engage or disengage by spring pressure when the vacuum or f luid is removed, or to employ a solenoid for activating a drive gear into dynamic engagement.
For example, U.S. Patent No. 4,694,943 discloses a clutch assembly for converting between two wheel drive mode and four wheel drive mode. The clutch assembly includes a f ixed locking member, a receiver gear connected to a wheel, a drive gear connected to a drive shaft and a shift means. The drive gear includes at least one cam follower and an axially movable camming assembly having a camming surface means engageable with the cam follower to impart axial movement to the drive gear when the camming assembly is fixed against rotation is and the drive gear is rotated. A solenoid is provided forwardly of the axle and external of the wheel hub or rotor within a cap to operatively activate the clutch assembly.
It will be appreciated that a solenoid or 20 electromagnetically activated locking hub assembly is more flexible in operation. For example, because the locking hub assembly responds to an electrical signal the sequence of engaging the locking hub assembly may be modified to correspond to the activities of various other power train components. Although a solenoid as disclosed in U.S. Patent 4,694,943 possess certain advantages over the prior art, a solenoid which is positioned external of the wheel hub or rotor is more susceptible to damage than an electromagnetic activating means which is surrounded by the wheel hub or rotor. Notwithstanding that an electromagnetic means surrounded by the wheel hub is less susceptible to damage than an electromagnetic means positioned external of the wheel hub, it will be appreciated that the internal volume of the wheel hub severely limits the area available f or the BWA-91096A - 5 - working components of the electromagnetic activating means. Accordingly, the design and construction of the locking hub assembly including an electromagnetic means positioned internal of the wheel hub is crucial.
Although the many variations in locking hub assemblies have been proven to perform satisfactorily, further advancements in the design and construction of locking hub assemblies is desired.
SUMMARY OF THE INVENTION
It is therefore broadly an object of the present invention to provide a power transmitting assembly, such as a differential assembly or a locking hub assembly which is electromagnetically actuated and which may be simply and economically manufactured.
Another object of this invention is to provide a mechanical power transmitting assembly for use in a motor vehicle that has an electromagnetic lock of simple and rugged constitution that can be engaged and disengaged by an intermittent energization of an electromagnet.
In one aspect a more specific object of this invention is to provide a locking differential for use in a motor vehicle that has an electromagnetic lock that can be engaged and disengaged by a timed or intermittent energization of the electromagnet.
A feature of the differential aspect of the invention is that the mechanical power transmitting device or differential assembly has an electromagnetic lock that can be maintained in an engaged position without the need for continuous application of electrical power. This improves the efficiency of the device from both an electrical and a mechanical BWA-91096A - 6 - standpoint. Less electrical power is consumed when the device operates in a lock-up mode because the electromagnet can be deenergized once the lock is engaged. The device also consumes less mechanical power when it operates in the lock-up mode because the electromagnet is deenergized after the device is engaged which eliminates the clutch drag of prior art locking differentials.
Another feature of the invention is that the transmitting assembly is electromagnetically actuated lock is bidirectional so that it engages and disengages in response to either clockwise or counterclockwise rotation of the drive member that is in the process of being locked to or unlocked from another drive member. This is an advantage in an automotive application because the electromagnetically actuated lock can be engaged or disengaged whether the vehicle is going forward or in reverse in the case of a hub lock or in response to the traction condition of either the right or left driven wheel in the case of a locking differential.
BRIEF DESCRIPTION OF THE DRAWINGS
The above and other objects, features and advantages of the invention will become more apparent from the following description taken in conjunction with the accompanying drawings wherein like references refer to like parts and wherein:
Figure 1 is an enlarged partial cross sectional view of a wheel hub assembly of a vehicle including a tire, wheel, automatic locking hub, axle and steering mechanism; BWA-91096A - 7 - Figures 2-4 are an exploded view of an automatic locking hub in accordance with one embodiment of the present invention; Figure 5 is a cross sectional view ofan assembled automatic locking hub of the type shown in Figures 2-4 wherein the upper half demonstrates the assembly in the disengaged position and the lc-..-ar half demonstrates the assembly in the engaged position; 10 Figures 6-9 are cross sectional views of assembled automatic locking hubs in accordance with various alternative embodiments of the present invention wherein the upper half of each view demonstrates the assembly in the disengaged position and the lower half demonstrates the assembly in the engaged position; Figure 10 is a cross sectional view of the assembled automatic locking hub of Figure 7 including a synchronizer assembly; Figure 11 is an enlarged partial view of the clutch plate, reaction hub, cam ramp and cam follower of Figure 5 in the engaged position; Figure 12 is an enlarged partial view of the clutch plate, reaction hub, cam ramp and cam follower of Figure 5 in the disengaged position; Figure 13 is an enlarged f ront view of the powered washer of Figure 5; Figure 14 is a cross-sectional view of the powered washer of Figure 13 taken along line 14-14; BWA-91096A - 8 - Figure is is an enlarged partial view of the powered washer of Figure 13- 13 taken along line 15-15; Figure 16 is an enlarged partial perspective 5 view of the connector portion of the powered washer of Figure 13; Figure 17 is an enlarged partial view of the locking hub assembly and synchronizer assembly of Figure 10 10; Figure 18 is an enlarged view of the top half of the locking hub assembly and synchronizer assembly of Figure 17 illustrating the synchronizer assembly in 15 partially engaged position; and Figure 19 is an enlarged view of the top half of the locking hub assembly and synchronizer assembly of Figure 17 illustrating the synchronizer assembly'in the 20 fully engaged position.
Figure 20 is a fragmentary sectional view of a differential having a lock in accordance with the invention; Figure 21 is a top view of internal components of the differential shown in figure 20 Figure 22 is an exploded perspective view of 30 the locking components shown in figure 20; and Figure 23 is an enlargement of a portion of figure 21; BWA-91096A - 9 Figure 24 is a fragmentary sectional view of a differential having an alternative lock in accordance with the invention; and Figure 25 is an enlargement of a portion of figure 24.
DESCRIPTION OF THE INVENTION
In the following description, like reference numerals designate like or corresponding parts. Also in the following description it is to be understood that terms such as "forward" and "rearward" and the like are words of convenience to assist in the relative description of a component or element with respect to another component or element.
Referring now to Figure 1, there is generally shown a wheel assembly 10 of a vehicle ' which in one preferred form of the present invention is the front wheel assembly of a four-wheel drive vehicle. As shown, the wheel assembly 10 broadly includes a tire 12 mounted on a wheel 14 which is fastened to a rotor or wheel hub 16 of a locking hub assembly 18 having forward and rearward radial flanges 20 and 22. It will be appreciated that the terms Orotor" and "wheel hub" are equivalent terms and may be used interchangeably, however, for clarity and conciseness only the term rotor shall be used from this point forward. Extending rearward f rom the back of the rotor 16 of the locking hub assembly 18 is a tubular spindle 24 and axle 26 having a central axis 28 concentric with a central axis of the wheel 14, tire 12 and rotor 16. As shown in Figure 3, the axle 26 is a solid cylindrical member having a plurality of external circumferentially spaced splines 30 extending longitudinally rearward from a forward end of the axle. Spaced from the forward end of BWA-91096A - 10 - the axle is a slot 32 encircling the external diameter of the axle for receiving a retaining ring 34. The thickness of the retaining ring 34 may be greater than the depth of the slot 32. The wheel 14 is attached to the forward flange 20 of the rotor 16 by threaded fasteners 36 extending through openings formed within the forward flange 20. Similarly, a brake disc 38 is attached by threaded fasteners 36 extending through openings formed within the rearward flange 22 of the rotor 16.
The locking hub assembly 18 of Figures 2-10 broadly includes a first rotatable assembly, a second rotatable assembly having an axially movable rotating member, a means for moving the rotating member axially between a first position and a second position and a nonrotatable electromagnetic means fixed for nonrotation about the axis 26 for activating the axially moving means.
As used herein "first position" refers to the arrangement of the locking hub assembly 18 wherein the first rotatable assembly operatively engages the second rotatable assembly and, similarly, the "second position" refers to the arrangement of the locking hub assembly wherein the first rotatable assembly is disengaged from the second rotatable assembly.
As shown in Figures 2-10, the first rotatable assembly of the locking hub assembly 18 includes a rotor 16, outer clutch housing 40 and cap 42. The rotor 16 is of a generally a tubular shape having a plurality of internal splines 44 spaced about the inner circumference thereof extending longitudinally rearward from a forward end of the rotor. Formed within the inner forward end of the rotor 16 is a circumferential retaining groove 46 which in cooperation with a retaining ring 48 and an opposing external circumferential retaining groove 50 of BWA-91096A - 11 - the outer clutch housing 40 maintains the axial position of the rotor with respect to the outer clutch housing.
The outer clutch housing 40 is positioned concentrically within the rotor 16 and is of a tubular shape having internal forward spaced radially inward circumferential teeth 52 and external radially outwardly directed spaced circumferential splines 54 which intermesh with the inner splines 44 of the rotor. The retaining ring 48 having angular ends 56 is positioned within the external retaining groove 50 about the outer circumference of the outer clutch housing 40. In the expanded condition, the retaining ring 48 restricts the axial movement of the outer clutch housing 40 relative to the rotor 16. However, for ease of installation, a second rearward o-ring 58 may be positioned within a groove 60 to secure a retaining clip 62 over the angular ends 56 of the retaining ring 48 to compress the retaining ring within the retaining groove 50 prior to installation of the locking hub assembly 18. During installation of the outer clutch housing 40 within the rotor 16, the retaining clip 62 moves axially forward thereby releasing the retaining ring 48 from the retaining clip such that the retaining ring expands outwardly within the external retaining groove 50 providing an interference fit between the retaining ring and internal retaining groove 46 and external retaining groove 50.
A cap 42 having a cylindrical cup like shape may be secured by threaded fasteners 64 within threaded holes formed within the forward end of the outer clutch housing 40. The cap 42 overlaps the outer clutch housing 40 and abuts against the rotor 16 thereby sealing the forward open end of the rotor.
Positioned concentrically within the first rotatable assembly is the second rotatable assembly. As BWA-91096A - 12 - shown in Figure 2-10, the second rotatable assembly include a hub sleeve 66 and axially movable rotating member 68.
The hub sleeve 66 surrounds a portion of the axle 26 forward of the axle retaining ring 34. The hub sleeve 66 is a tubular member having external spaced circumferential splines 70 and internal spaced circumferential splines 72 which intermesh with the external axle splines 30. Forward groove 74, rearward groove 76 and intermediate groove 78 are formed transverse to the longitudinal splines 70 within the external circumferential surface of the hub sleeve 66 to receive spring retainer clip 80, thrust washer 82 and intermediate retaining ring 84, respectively. The thickness of the spring retainer clip 80, thrust washer 82 and intermediate retaining ring 84 may be greater than the depth of the respective grooves. Formed within the interior forward end of the hub sleeve 66 is a concave recess 86 which serves as a supporting surface for a bearing ring 88.
Surrounding the hub sleeve 66 is an axially movable rotating member 68, Figures 2-10. The axially movable rotating member 68 is a clutch gear or the like. The rotating member 68 includes a tubular member having a radially extending rim 90 including circumferentially spaced radially outwardly extending teeth 92. Formed about the circumference of the interior of the cylindrical member of the rotating member 68 are splines 94 which engage the splines 72 of the hub sleeve 66.
Referring to Figure 2-10, a means for moving the rotating member 68 between a first position and a second position is shown. The moving means includes a cam assembly 96, an engaging spring 98, a return assembly 100 and an axially movable cam follower 102.
BWA-91096A - 13 - The cam assembly 96 acts as a reaction surface for the cam follower 102 to actuate the axial movement of the cam follower. AS shown in Figures 2-5, the cam assembly 96 includes a clutch plate 104f reaction hub 106 and cam ramp 107 freely rotatable concentrically with respect to the axle 26. Although it is preferred that the clutch plate 104, reaction hub 106 and cam ramp 107 are formed as separate elements for greater tolerance control in assembly and manufacture, it will be appreciated that the clutch plate and/or reaction hub and/or cam ramp may be f ormed as one or two elements and perform equally as well.
In a preferred embodiment of the cam assembly as shown in Figures 3 and 5, the clutch plate 104 is is positioned adjacent a vertical forward face of an electromagnetic coil 122 and is of a generally tubular shape including a rearward flange 108 defining an outer annular shoulder surface 110 and an inner annular shoulder surface 112. The outer annular shoulder surface 110 is contoured to include opposing ramp surfaces 114 for variable surface contact with a matching reaction hub 106. One or more cylindrical retaining pins 116 may extend transversely from the external cylindrical surface of the clutch plate 104 through an elongated slot 118 formed within the side surface of the reaction hub 106 to assist in ease of assembly and transport of the component parts prior to assembly in a vehicle. A helical preload spring 120 is biased between the clutch plate 104 and reaction hub 106 to maintain the clutch plate 104 adjacent the electromagnetic coil 122, more fully described herein, thereby preventing excessive gap between the electromagnetic coil and clutch plate.
Positioned forward of the clutch plate 104 is the reaction hub 106. The reaction hub 106 is a BWA-91096A - 14 - generally rearwardly directed cam having a bottom disc 124 and projecting integral tubular side 126 having a scalloped rim 128 for engagement with the matching ramp surfaces 114 of the clutch plate 104. It will be appreciated that the reaction hub 106 allows for freedom of motion of the rotor 16 and reduces the necessity for positional tolerance control of the cam ramp 107 and cam follower 102.
Securely fastened to the back surface of the bottom disc 124, which is transverse to the axis of the reaction hub 106, is the cam ramp 107. The cam ramp 107 is a forwardly directed cam having a bottom disc 130 and projecting tubular side 132 having a contoured outer rim 134. The outer rim 134 of the cam ramp 107 has formed is therein at least one, and preferably two diametrically opposing V- shape notches 136 to provide a variable reaction surface consisting of at least one low height edge portion and at least one high height edge portion for the cam follower 102. In a preferred embodiment, the back surface of the bottom disc 124 of the reaction hub 106 and the back surface of the bottom disc 130 of the cam ramp 107 are securely fastened to one another by weldment of the like and rotate about a pilot diameter of the hub sleeve 66 between the thrust washer 82 and retaining ring 84 secured within grooves 76 and 78 of the hub sleeve 66 and rearward end of splines 70 of the hub sleeve. The thrust washer 82 acts to absorb the force resulting from the axial movement of the cam ramp 107.
Now referring to Figures 6-10. various additional alternative configurations of a clutch plate 104 and reaction hub 106 are shown. As shown in Figure 6, the clutch plate 104 includes a disc like member having in integral tubular projection including a plurality of spaced radially inwardly directed splines BWA-91096A - is - 138. The opposing reaction hub 106 includes a disc like member having an integral projecting tubular side including a plurality of spaced outwardly directed circumferential splines 140 which intermesh with the inwardly directed splines 138 of the clutch plate 104.
Secured to the back surface of the reaction hub 106 is the cam ramp 107 as shown in Figure 3.
The clutch plate 104 of Figure 7 is a general frustoconical member having a tubular front portion and rearward rim for structural support. The tubular front portion includes a plurality of spaced radially inwardly directed circumferential splines 142. The opposing reaction hub 106 includes a disc like member having an integral projecting tubular side including a plurality of spaced outwardly directed circumferential splines 144 which intermesh with the radially inwardly directed splines 142 of the clutch plate 104. The cam ramp 107 as shown in Figure 3 is also secured to the back surf ace of the reaction hub 106.
In yet another embodiment as shown in Figure 8, the clutch plate 104 and reaction hub 106 may be formed as one element having a general form of a stepped frustoconical member 105. A cam ramp 107 as shown in Figure 3 is secured to the back surface of the stepped frustoconical member 105.
As shown in Figure 9, the clutch plate 104 includes a frustoconical member including a projecting tubular member having a plurality of spaced circumferential inwardly directed splines 146. The reaction hub 106 is a disc member having an integral projecting tubular member including a plurality of spaced circumferential outwardly directed splines 148 which intermesh with the splines 146 of the clutch plate 104. Interposed between the clutch plate 104 and reaction hub 106 is a spring 120 for biasing the clutch BWA-91096A - 16 - plate against the electromagnetic coil 122. Secured to the back surface of the clutch plate 104 is the cam ramp 107 as shown in Figure 3.
Referring to Figures 3 and 5-10, positioned f orward of the cam ramp 107 between the cam ramp and intermediate retaining ring of the hub sleeve 66 is a cam follower 102. The cam follower 102 includes a disc member having interior teeth 150 extending radially inwardly for meshing engagement with the splines 70 of the hub sleeve 66. Two prong members 152 extend radially outwardly and forwardly from the external edge of the disc member of the cam follower 102. The prong members 152 are stepped inwardly toward the axle 26 and extend longitudinally over diametrically opposed flats 154 formed between the gear teeth 92 of the rim 90 of the rotating member 68 and the external circumferential surface of the cylindrical member of the rotating member. The radially inwardly extending teeth 150 of the cam follower 102 and inner circumferentially spaced splines 94 of the rotating member 68 intermesh with external circumferentially spaced longitudinal splines 70 of the hub sleeve 66 to provide axial guidance to the rotating member 68 and cam follower 102 and, in the engaged position, transmit rotary motion and/or torque from the axle 26 to the outer clutch housing 40.
As shown in Figures 3, 11 and 12, an optional detent 156 may be provided at the top of the prong member 152 of the cam follower 102 to position the cam follower relative to the cam ramp 107 and act as a sliding ramping surface to accommodate a complimentary notched cam ramp surface.
The engaging spring 98 and the return assembly 100 are positioned for yieldably biasing the rotating member 68 between the f irst position and the second position. As shown in Figures 2 and 5-10, the engaging BWA-91096A - 17 - spring 98 is positioned between the cam follower 102 and rotating member 68. The engaging spring 98 provides axial forward force to the rotating member 68 as a return spring 101 of the return assembly 100 is compressed by the cam follower 102 as further described herein. Surrounding the cylindrical member of the rotating member 68 is the return assembly 100. The return assembly 100 includes a helical return spring 101 contained between opposing spring retainer rings 158.
Positioned forward of the return assembly 100 is a spring support washer 160 and spring retainer clip 80. The spring retainer clip 80 is secured within a forward groove 74 of the hub sleeve 66 to restrict the forward axial movement of the return assembly 100 and rotating member 68 on the hub sleeve 66. In a preferred embodiment, the return spring 101 force is greater than the opposing force of the engaging spring 98.
As shown in Figures 2-10, the prong members 152 of the cam follower 102 extend over the rim 90 between the rotating member gear teeth 92 within flats 154 such that during locking hub assembly engagement, surface 162 compresses the return spring 101 positioned within the spring retainer rings 158 between the spring support washer 160 and surface 162 of the prong members 25 152 of the cam follower 102. Fixed for nonrotation about the axle 26 is an electromagnetic means for activating the moving means. The electromagnetic activating means includes an electromagnetic coil 122 and power washer 166 secured to a spindle 24 fixed for nonrotation about the axle 26.
The spindle 24 is a hollow cylinder positioned concentrically between the rotor 16 and axle 26 and axially rearward of the hub sleeve 66. A spacerwasher 171 includes radially inwardly extending teeth which 35 engage with the splines 30 of the axle 26 and protect BWA-91096A - is - the rearward hub sleeve 66 end and f orward end of the spindle 24. The exterior of the spindle 24 includes a threaded forward end 168 and enlarged diameter portion 170 separated by step 172. As shown in Figures 5-10, mounted between the external surface of the spindle 24 and the internal surface of the rotor 16 are bearings 174 which support the rotor 16 such that the axle 26 and rotor rotate freely with respect to the spindle 24.
Threaded on the forward end 168 of the spindle 24 is a retaining member 180 through which the electromagnetic activating means is secured for nonrotation about the axle 26. As shown in Figures 3, 5-10, the retaining member 180 includes at least one cylindrical retaining nut threaded on one or both sides of the electromagnetic coil 122 for retaining the electromagnetic coil. The retaining member 180 includes one or more circumferentially spaced bores 184 formed within the front surface of the retaining member. Slots 186 may be formed parallel to the central axis about the periphery of the retaining member 180 to assist in torquing the threaded retaining member on the threaded spindle 24.
An annular passage 176 may be formed between the spindle 24 and axle 26 and functions as a channel for a wire 178, cable, fibre-optic and the like to provide electrical power and a signal to activate the locking hub assembly 18 as more fully described herein. It will be appreciated that the annular passage 176 may also function as a conduit for assembling bearings, nuts, and other coaxial elements over the wire, cable or fibre-optic. In a preferred embodiment, electrical power and/or signal are conveyed through a wire 178 to a connector block 188 (Figures 14-16) of the power washer 166 and connected to a signal processor 189, Figures 3, 5, 13-16. As shown in Figures 13-16, the BWA-91096A - 19 - power washer 166 is a disc-like member includinga plurality of insulator rings 190 which separate the powered washer into an inner retaining ring 192, sensor conductor rings 194 and electromagnetic coil conductor rings 196. One or more pins 198, circumferentially spaced about the periphery of the retaining ring 192, extend through the power washer 166 such that the pins in cooperation with bores 184 of the retaining member secure the power washer to the retaining member. It will be appreciated that the power washer 166 may also be fastened to the retaining member 180 through most any suitable means such as by threaded fasteners, weldment, adhesive and the like.
Threaded on the spindle 24 forward of the power washer 166 is an electromagnetic coil 122 having a threaded interior bore. The electromagnetic coil 122 is generally of an annular shape consisting of encapsulated interior windings of wire. In a preferred embodiment as shown in Figures 3 and 5, a collar 200 projects axially from the forward f ace of the electromagnetic coil 122 to assist in the torquing of the threaded electromagnetic coil onto the external spindle threads.
To determine the relative position of the second rotatable assembly and the moving means with respect to the electromagnetic means one or more detection sensors may be utilized. Suitable detection sensors include Hall sensors 202 in combination with magnets 204 and/or proximity switches 206 in combination with position markers 207.
As shown in Figure 3, the magnets 204 may be secured to the hub sleeve 66 and the reaction hub 105 and the Hall sensors 202 may be formed with or secured to the end of the collar 200 or the end of the spindle 24. The magnets 204 and the Hall sensors 202 BWA-91096A - 20 - cooperatively produce a fluctuating signal as a result of the sensor magnetic f ield being interrupted by the magnets as the magnets rotate about the axis 28. As shown in Figure 3, magnets 204 of the hub sleeve 66 rotate with the axle 26 and magnets 204 of the reaction hub 106 rotate about the axle to assist in determining the relative rotation between two separately rotating assemblies and the magnetic coil 122. The fluctuating signal is then conveyed to a signal processor 189 whereby the relative angular displacement of each rotating part is calculated to determine whether locking hub assembly 18 is in the f irst position or in the second position.
In yet another embodiment as shown in Figure 9, a position marker 207 such as a washer or other cylindrical member containing one or more equally spaced circumferential slots or apertures is mounted on the axle 26 adjacent to the proximity switch 206 mounted on the spindle 24. It will be appreciated that the proximity switch 206 may also be positioned above the electromagnetic coil 122 and/or adjacent a frustoconical cylindrical drum, Figures 6, 7, 8 and 10. The proximity switch 122 is responsive to the position of the slot or aperture such that after the slot or aperture rotates a predetermined number of degrees the signal processor 189 signals the electromagnetic means to activate the moving means. Power may be supplied to the Hall sensors 202 and/or proximity switches 206 through wire 178 or sliding contact with the appropriate annular ring 194 of the power washer 166.
Biased between the cap 42 and hub sleeve 66 is an axial bearing support assembly 212. The axial bearing support assembly 212 includes a bearing race spring 214, a bearing collar 216, bearing clip 218 and a bearing ring 88 of substantially the same diameter as BWA-91096A - 21 - the internal diameter of the hub sleeve 66. The bearing ring 88 slides over the exterior of the cylindrical bearing collar 216 and is secured thereto by bearing clip tabs which are flexibly engaged within an aperture 5 of the bearing collar. The bearing race spring 214 is positioned within a notch 222 within the cap 42 against the bearing collar 216 to maintain the axial bearing support assembly 212 adjacent the hub sleeve 66 thereby rotatably supporting the forward end of the hub sleeve.
To operatively engage the rotor 16, an electric signal from a signal processor 189 energizes through wire 178 the electromagnetic coil 122 via the powered washer 166. Magnetic attraction generated by the electromagnetic coil 122 fixes the clutch plate 104 15 of the cam assembly 96 to the electromagnetic coil thereby locking the cam assembly in a fixed position as the axle 26, hub sleeve 66, rotating member 68 and cam follower 102 rotate. As the cam follower 102 rotates about the axle 26, the prong members 152 move from the 20 V- shaped notches 136 to a high height edge portion along the contoured edge surf ace of the cam ramp 107 of the cam assembly 96 thereby driving the cam follower 102 axially forward. As the cam follower 102 moves axially forward, the return spring 101 is compressed thereby 25 removing the rearwardly acting pressure of the return spring and allowing the engaging spring 98 to force the rotating member 68 axially forward into meshing engagement with the teeth 52 of the outer clutch housing 40 to connect the axle 26 to the rotor 16 such that the 30 automatic locking hub assembly is in the first position.
As the cam follower 102 moves axially, the cam follower also rotates a magnet 204 and/or position marker 207. The magnet 204 and/or position marker 207 rotate adjacent to a Hall sensor 202 and/or proximity switch 206. After the magnet 204 and/or position marker BWA-91096A 207 rotate a predetermined number of degrees relative to the first position, the Hall sensor 202 and/or proximity switch 206 signals the signal processor 189 to interrupt the electric current to the electromagnetic coil 122.
The electromagnetic coil 122 is deenergized such that the magnetic field collapses allowing the clutch plate 104 and cam ramp 107 of the cam assembly 96 to rotate free of the electromagnetic coil 122 and axle 26.
To disengage the locking hub assembly 18 from the first position, an electrical signal from the signal processor 189 reenergizes the electromagnetic coil 122 thereby preventing the clutch plate 104, reaction hub 106 and cam ramp 107 of the cam assembly 96 from rotating. The rotating cam follower 102 moves the high height edge portion of the contoured edge surface of the cam ramp 107 of the cam assembly 96 to the low height edge portion of the V-shaped notches 136 of the cam ramp 107 of the can assembly thereby moving the rotating cam follower axially rearward. As the cam follower 102 moves axially rearward, the return spring 101 pushes the rotating member 68 out of engagement with the outer clutch housing and compresses the engaging spring 98 between the rotating member 68 and the cam follower 102. After the Hall sensor 303 and/or proximity switch 206 sense that the first rotatable assembly has rotated a predetermined number of degrees, the signal processor 189 interrupts electric current to the electromagnetic coil 122 thereby releasing the clutch plate 104, reaction hub 106 and cam ramp 107 of the cam assembly 96 to freely rotate in synchronization with the cam follower 102. The rotor 16 and the locking hub assembly 18 are no disengaged and in the second position.
Although the operation of the locking hub assembly 18 has been described in detail with respect to the embodiment of the present invention as shown in BWA-91096A - 23 - Figures 2-5, it will be readily apparent to one skilled in the art that the same principle of operation is applicable to the various embodiments of the present invention as shown in Figures 6-10.
As shown in Figures 10 and 17, the locking hub assembly 18 may also include a synchronizer assembly 224 to assist in proper alignment of the first rotatable assembly and the second rotatable assembly without clash during operation. As shown in Figure 17-19, the engaging spring 98 may push the rotating member 68 to activate a synchronizer assembly 224 rotatably fixed by bearings 226 with the first rotatable assembly and press fit within a notch formed in the cap 42.
The synchronizer assembly 224 includes a synchronizer collar 228, a cone ring 230 and a plurality of struts 232. The synchronizer collar 228 is a tubular member having a slot 234 formed about the external circumference of the member to receive a pin 236 extending from the rotating member 68. Spaced about the inner circumference of the synchronizer collar 228 are splines 238 to receive at least three circumferentially spaced struts 232. The struts 232 extend longitudinally within the splines 238 and are pivotally balanced by springs 240 about a ring. Positioned forwardly of the struts 232 is the cone ring 230. The cone ring 230 includes a conical braking surface 242 at the rearward end of the ring and a plurality of spaced radially outwardly directed teeth 244 at the forward end of the external diameter of the ring.
In operation, as the rotating member 68 moves axially from the second position to the first position the pin 236 extending from the rotating member engages the forward side surface of the slot 234 of the synchronizer collar 228 moving the synchronizer collar forwardly, Figure 18. The struts 232 pivot causing the BWA-91096A - 24 - f orward end of the strut to frictionally engage the conical braking surface 242 of the cone ring 230 causing deceleration of the second rotatable assembly.
As the synchronizer collar 228 is pushed forwardly by the pin 236, the inner splines 238 on the synchronizer collar 228 engage the teeth 244 of the cone ring 230. Upon engagement of the inner splines 238 with the teeth 244 of the cone ring 230 the axle 26 becomes synchronous with the rotating wheel 14 and the rotating member 68 engages with the outer clutch housing 40 connecting the first rotatable assembly with the second rotatable assembly, Figure 19.
Referring now to figure 20, it illustrates a bevel gear differential 310 having an electromagnetically actuated lock 312 in accordance with the invention. The bevel gear differential comprises a housing 314 that rotatably supports a case 316 that carries an external ring gear 318, an internal spider 20 319, and a plurality of internal bevel gears 320 that are rotatably mounted on radial pins 321 of the spider, one of which is illustrated. The ring gear 318 is usually driven by a bevel drive gear attached to the propeller shaft of an automobile (not shown). 25 Consequently the case 316 and internal bevel gears 320 constitute the rotatable input member or element of the differential 310 which is classically described as a planetary gear set having three relatively rotatable drive members or elements. In this case the other two 30 drive members or elements are the side gears 322 and 324 that are attached to the respective output axle shafts 326 and 328 that have their adjacent ends supported in bearings pressed into the bore of the spider 19. The differential 310 as thus far described operates in a well-known manner that allows the output axle shafts 326 BWA-91096A - 25 - and 328 to be rotated at different speeds to accommodate turning maneuvers, tire size variations, etc.
It is also well-known that a differential can be locked up so that all three drive members or elements are f orced to rotate in unison at the same speed by locking any two of the three drive members or elements together. This embodiment of the invention employs an electromagnetically actuated lock f or locking two of the three drive members together.
The differential lock 312 broadly includes a f irst rotatable assembly, a second rotatable assembly having an axially movable rotating member, a means for moving the rotating member axially between a first position and a second position and a nonrotatable electromagnetic means fixed for nonrotation with respect to the rotatable assemblies for activating the axially moving means.
In the arrangement of the differential assembly 310 the first rotatable assembly positively engages the second rotatable assembly for simultaneous rotation in the first position. In the second position the first rotatable assembly is disengaged from the second rotatable assembly allowing relative rotation between the two assemblies.
The first rotatable assembly includes differential case 316 and an integral extension of the case 316 that forms an outer clutch housing 330. The outer clutch housing 330 is tubular and has internal teeth 332.
The second rotatable assembly is positioned concentrically within the first rotatable assembly. The second rotatable assembly includes a hub sleeve 334 and axially movable rotating member 336. The hub sleeve 334 is an integral part of the side gear 324 that is attached to the axle shaft 28 by mating internal and BWA-91096A - 26 - external circumferentially spaced splines which intermesh.
The axially movable rotating member 336 is a clutch gear or the like that includes a tubular member having a radially extending rim 338 which has circumferentially spaced radially outwardly extending teeth 340. The interior of the tubular member has internal splines which slidably engage straight external splines of the hub sleeve 334.
The means for moving the rotating member 336 between the first position and the second position includes a cam assembly 342, an engaging spring 344, a return spring assembly 346 and an axially movable cam follower 348.
The cam assembly 342 acts as a reaction surface for the cam follower 348 to actuate the axial movement of the cam follower. The cam assembly 342 includes a clutch plate 350, reaction hub 352 and cam ramp 354 all of which are freely rotatable concentrically with respect to the axle shaft 328 and hub sleeve 334. The clutch plate 350, reaction hub 352 and cam ramp 354 are preferably formed as separate elements for greater tolerance control in assembly and manufacture. However, the clutch plate and/or reaction hub and/or cam ramp may be formed as one or two elements and perform equally as well.
The clutch plate 350 is positioned adjacent a vertical forward face of an electromagnet 356 and is tubular including a rearward flange 358 and an annular body 360. The external cylindrical surface of the body 360 is contoured to include opposing radial ramp surfaces 362 for variable surface contact with a matching radial reaction surface 364 formed on an annular extension 366 that forms part of the reaction 35 hub 352.
BWA-91096A - 27 - one or more cylindrical retaining pins 68 may extend transversely from the external cylindrical surface of annular body 360 through an elongated slot 370 formed in the extension 366 of reaction hub 352 to assist in ease of assembly and transport of the component parts prior to assembly into the differential 310. An optional helical preload spring 372 is biased between the clutch plate 350 and reaction hub 352 to maintain the clutch plate 350 adjacent the electromagnet 356, thereby preventing excessive gap between the electromagnet 356 and the clutch plate 350.
The reaction hub 352 is positioned forward of the clutch plate 350. The reaction hub 352 is a generally rearwardly directed cam having a forward flange and a scalloped rim cut into the external cylindrical surface of the annular extension 366 which provides the radial reaction surface 364 for engagement with the matching ramp surfaces 362 of the clutch plate 350. This engagement of the reaction hub 352 allows for freedom of motion of the differential case 316 and reduces the necessity for positional tolerance control of the cam ramp 354 and cam follower 348.
The cam ramp 354 is securely fastened to the back surface of the forward flange of the reaction hub 352. The cam ramp 354 is a forwardly directed cam having a rearward flange 374 and projecting tubular side 376 having a contoured outer rim 378. The outer rim 378 of the cam ramp 354 includes at least one, and preferably two diametrically opposed V-shape notches 380 to provide a variable reaction surface consisting of at least one low height edge portion and at least one high height edge portion for the cam follower 348. The back surface of the forward flange of the reaction hub 352 and the back surface of the rearward flange 374 of the cam ramp 354 are securely fastened to one another by BWA-91096A - 28 - weldment or the like and rotate about a pilot diameter 382 of the hub sleeve 334 between a thrust washer and retaining ring 384 secured within a groove of the hub sleeve 334 and the rearward end of splines 386 of the hub sleeve. The thrust washer and retaining ring 384 act to absorb the force resulting from the axial movement of the cam ramp 354.
The cam follower 348 is positioned forward of the cam ramp 354. The cam follower 348 includes a disc member 390 having interior teeth meshing with the splines 386 of the hub sleeve 334 between the cam ramp and an intermediate retaining ring 388 that is attached to the hub sleeve 334 to retain the rotating member 336. Two prong members 392 extend radially outwardly and then forwardly from an external edge of the disc member 390 of the cam follower 348. The forwardly extending portions of the prong members 392 pass between the teeth 340 of the rim 338 and then are stepped inwardly behind the rim 338 to terminate in diametrically opposed external flats 394 formed in the tubular member of the rotating member 336. The interior teeth of the cam follower 348 and inner circumferentially spaced splines 396 of the rotating member 336 intermesh with external circumferentially spaced longitudinal splines 388 of the hub sleeve 334 to provide axial guidance to the rotating member 336 and cam follower 348 and, in the engaged position, transmit rotary motion and/or torque to the axle shaft 328 and the hub sleeve 334 from the outer clutch housing 330 and differential case 316.
An optional detent 398 may be provided at the corner of the prong member 392 to position the cam follower 348 relative to the cam ramp 354 and act as a sliding ramping surface to accommodate a complimentary notched cam ramp surface.
BWA-91096A - 29 - The engaging spring 344 and the return assembly 346 are positioned for yieldably biasing the rotating member 336 between the first position and the second position. The engaging spring 344 is positioned between the cam follower 348 and rotating member 336.
The engaging spring 344 provides axial forward force to the rotating member 336 as a return spring 400 of the return assembly 346 is compressed by the cam follower 348 as further described herein. The return spring assembly 346 which surrounds the cylindrical member of the rotating member 336 includes a helical return spring 400 contained between spring retainer rings 402 and 403. The integral side gear 324 is positioned forward of the return spring assembly 346 and engages spring retainer ring 402 to restrict the forward axial movement of the return spring assembly 346 and rotating member 336 on the hub sleeve 334. Spring retainer ring 403 engages riser surfaces 393 of the prong members 392 that abut the rim 338 of the rotating member 336. During locking engagement, the riser surfaces 393 of the prong members 392 and the rim 338 compress the return spring 400 which preferably has a force greater than the opposing force of the engaging spring 344.
An electromagnetic means for activating the moving means described above is fixed for nonrotation in the axle housing 314 so that it does not rotate relative to the axle shaft 328 and differential case 316. The electromagnetic activating means includes the electromagnet 357 comprising an encapsulated electromagnetic coil 358 secured in a shell that includes a ring 359 of magnetizable material and may include a power washer such as that shown in figures 14 through 16 and described earlier in the specification.
Passage (not shown) may be formed in the axle housing 314 to provide channels for wires, cables, BWA-91096A - 30 - f ibre-optics and the like to provide electrical power and signals to operate the differential lock 312.
Electrical power and/or signal are conveyed from a power and control source such as microprocessor 404 through a wire 406 to the electromagnetic coil 358 via a power washer or the like.
To determine the relative position of the second rotatable assembly and the moving means with respect to the electromagnetic means one or more detection sensors may be utilized. Suitable detection sensors include Hall sensors 408 and 410 in combination with circumferential arrays of magnets 412 and 414, such as described earlier in connection with the embodiment shown in figures 1-5.
As shown in figures 20 and 23, the Hall sensors 408 and 410 may be secured to an integral collar of the axle housing 314 that is inward of the electromagnet 356 while the magnets 412 and 414 may be secured to the reaction hub 352 and hub sleeve 334 respectively. The Hall sensors 408 and 410 and the magnets 412 and 414 cooperatively produce two respective fluctuating signals as a result of the respective sensor magnetic fields being interrupted by the respective arrays of magnets 412 and 414 as the reaction hub 352 and hub sleeve 334 rotate. These two fluctuating signals are used to determine the respective relative rotations of the cam assembly 342 and the cam follower 348 that is splined to the hub sleeve 334 with respect to the fixed axle housing 314. The fluctuating signals are conveyed to the microprocessor 404 which uses the signals to determine the relative angular displacement of the cam assembly 342 with respect to the cam follower 348. This relative angular displacement shows whether the electromagnetically engaged lock 312 is engaged or not. That is the relative angular displacement of the BWA-91096A cam assembly 342 with respect to the cam follower 348 indicates the axial position of the axially moveable rotating member 336 and whether it is in the first position engaging the outer clutch housing 330 for simultaneous rotation or in the second position shown in figure 24 where member 336 is disengaged from the outer clutch housing 330 to allow relative rotation between the differential case 316 and the axle shaft 328. The hall sensors 408 and 410 communicate with microprocessor 404 via wires 416 and 418.
To operatively engage the differential lock 312, an electric signal from microprocessor 404 energizes the electromagnetic coil 357 via wire 406 which magnetizes ring 359. Magnetic attraction generated by the electromagnet 356 fixes the clutch plate 350 of the cam assembly 342 to the electromagnet 356 thereby locking the cam assembly 342 in a fixed position as the axle shaft 328, side gear 324 and hub sleeve 334, rotating member 336 and cam follower 348 continue to rotate. As the cam follower 348 rotates, the prong members 392 move from the V-shaped notches 380, that is, from a low height edge portion (shown in solid line in figure 21), to a high height edge portion along the contoured edge surface 378 of the cam ramp 376 of the cam assembly 342 (shown in phantom in figure 21) thereby driving the cam follower 348 axially forward, that is, to the left as viewed in figures 20 and 21. As the cam follower 348 moves axially forward, the return spring 400 is compressed thereby removing the rearwardly acting pressure of the return spring 400 and allowing the engaging spring 344 to force the rotating member 336 axially forward to the first position into meshing engagement with the teeth 332 of the outerclutch housing 330. This connects the axle shaft 328 and side gear 324 to the differential case 316 for simultaneous BWA-91096A rotation via the engaged integral hub sleeve 334 and thus the differential 310 is locked-up.
As the clutch plate 350 becomes grounded on the electromagnet 356 and the cam follower 348 continues to rotate, the fluctuating signals of the Hall sensors 408 and 410 are constantly fed to the microprocessor 404 which continually monitors the relative angular or rotational position of the cam follower 348 with respect to the clutch plate 350. As indicated earlier, this relative angular position shows whether the rotating member 336 is engaged with the outer clutch housing 330 or not. When the relative angular position indicates that the rotating member 336 is engaged, the microprocessor 404 interrupts electric current to the electromagnetic coil 358. The electromagnetic coil is then deenergized such that the magnetic field collapses allowing the clutch plate 350 and cam ramp 354 of the cam assembly 342 to rotate free of the electromagnet 356 and housing 314.
The differential lock 312 remains engaged with the rotating member 336 in the first position coupling the axle shaft 328 and the differential case 316 for simultaneous rotation by virtue of the cam follower 348 engaging the high height edge portion of the cam ramp 376 as shown in phantom in figure 21. The return spring 400 does not return the cam follower 348 even if it has a greater force than that of the engaging spring 344 because of the blocking effect of the high height edge portion of the cam ramp 376.
To disengage the differential lock 312 from the first position, an electric signal from the microprocessor 404 reenergizes the electromagnetic coil 358 thereby preventing the clutch plate 350, reaction hub 352 and cam ramp 354 of the cam assembly 342 from rotating. The rotating cam follower 348 then moves from BWA-91096A - 33 - the high height edge portion of the contoured edge surface 378 of the cam ramp 354 to the low height edge portion of the V-shaped notches 380 of the cam ramp 354 thereby moving the rotating cam follower 348 axially rearward. As the cam follower 348 moves axially rearward, the return spring 400 pushes the rotating member 336 out of engagement with the outer clutch housing 330 and compresses the engaging spring 344 between the rotating member 336 and the cam follower 348. The hall sensors 408, 410 and microprocessor 404 then detects from the relative angular position of the cam follower 348 with respect to the cam assembly when the rotating member 336 is disengaged. When this occurs the microprocessor 404 interrupts electric current to the electromagnetic coil 358 thereby releasing the clutch plate 350, reaction hub 352 and cam ramp 354 of the cam assembly 342 to freely rotate in synchronization with the cam follower 348. The differential lock 312 is now disengaged with the rotating member 336 in the second positionshown in figure 20. This frees the axle shaft 328 and differential case 316 for relative rotation with respect to each other and restores differential action to the differential 310.
The electromagneticAlly actuated lock 312 is bidirectional as it engages and disengages in response to clockwise or counterclockwise rotation of the axle shaft 328. The electrically actuated lock 312 can be controlled manually with a simple on-off switch for microprocessor 404. It can also be controlled automatically by an auxiliary system. For instance, the differential 310 can be locked automatically in the event of excessive wheel slip by feeding a wheel acceleration signal to the microprocessor 404 from an accelerometer 420 that is attached to the axle shaft 328 BWA-91096A - 34 - and linked to the microprocessor 404 by a slip ring 422 and wire 424.
Although the operation of the differential lock 12 has been described in detail with respect to the embodiment of the present invention as shown in figures through 23, it will be readily apparent to one skilled in the art that the same principle of operation is applicable to other locations in the differential and to other type differentials.
For instance, the differential lock 312 can be adapted to couple the axle shaft 326 rather than the axle shaft 328 to the case 316 to lock-up the differential or to couple the axle shafts 326 and 328 together, it being merely necessary to lock any two of the three drive members together. Moreover, the rotating member 336 can be slidably attached to any of the three drive members. The differential lock 312 can also be adapted to a planetary gear differential of the type that has a concentrically arranged sun gear, planet carrier and ring gear.
It is also possible to use alternatives to determine the relative position of the second rotatable assembly and the moving means with respect to the electromagnetic means. One such alternative is illustrated in connection with a modified differential 500 shown in figures 24 and 25.
The modified differential 500 includes proximity switches in combination with position markers such as described earlier in connection with the embodiment shown in figure 9 in place of the Hall sensors 408 and 410 and the arrays of magnets 412 and 414. With the exception of a suitably programmed microprocessor 504, the modified differential 500 is otherwise basically the same and corresponding parts are identified by the same numbers.
BWA-91096A - 35 - This position signal generating alternative has been incorporated in the modified differential 500 in the form of two position or proximity switches 508 and 510 and two position markers 512 and 514.
As shown in figures 24 and 25, the proximity switches 508 and 510 are secured to an integral collar of the axle housing 314 outward of the electromagnet 356.
The first position marker 512 is journalled in an axially fixed position in the bore of the outer clutch housing 330 that is integrally formed as part of the differential case 316. The body 516 of position marker 512 lies in the bore so that it is rotated by cam follower 348. Position marker 512 also has a flange 518 containing one or more equally spaced circumferential slots or apertures that rotate adjacent to the first proximity switch 508 that is nonrotatably mounted in the axle housing 314.
The second position marker 514 is an integral part of the cam assembly 342 and more particularly the clutch plate 350. In this instance, the rearward flange 358 of the clutch plate 350 contains one or more equally spaced circumferential slots or apertures that rotate adjacent to the second proximity switch 510 that is nonrotatably mounted in the axle housing 314.
The proximity switches or sensors 508 and 510 and the position markers 512 and 514 cooperatively produce two respective signals as a result of the slots or apertures of the respective position markers 512 and 514 passing the respective sensors 508 and 510 as the clutch plate 350 and the cam follower 348 splined to the hub sleeve 334 rotate. These two signals are used to determine the respective relative rotations of the cam assembly 342 and the cam follower 348 with respect to the axle housing 314. The signals are conveyed to the BWA-91096A - 36 - microprocessor 504 which uses the signals to determine the relative angular displacement of the cam assembly 342 with respect to the cam follower 348. This relative angular displacement shows whether the electromagnetically engaged lock 312 is engaged or not.
That is the relative angular displacement of the cam assembly 342 with respect to the cam follower 348 indicates the axial position of the axially moveable rotating member 336 and whether it is in the first position engaging the outer clutch housing 330 for simultaneous rotation or in the second position disengaged from the outer clutch housing to allow relative rotation between the differential case 316 and the axle shaft 328. 15 The proximity sensors 508 and 510 communicate with microprocessor 504 via wires 520 and 522. To operatively engage the differential lock 312, an electric signal from microprocessor 504 energizes the electromagnet 356 to lock the cam assembly 20 342 in a fixed position as the axle shaft 328, side gear 324 and hub sleeve 334, rotating member 336 and cam follower 348 continue to rotate. As the cam follower 348 rotates, the prong members 392 move from the Vshaped notches 380, that is, from a low height edge portion (shown in solid line in figure 21), to a high height edge portion along the contoured edge surface 378 of the cam ramp 376 of the cam assembly 342 (shown in phantom in figure 21) thereby driving the cam follower 348 to the left as viewed in figures 21 and 24 to the first position into meshing engagement with the teeth 332 of the outer clutch housing 330. This connects the axle shaft 328 and side gear 324 to the differential case 316 for simultaneous rotation via the engaged integral hub sleeve 34 and thus the differential 310 is locked-up.
BWA-91096A As the clutch plate 350 becomes grounded on the electromagnet 356 and the cam follower 348 continues to rotate, the signals of the proximity switches 508 and 510 are constantly fed to the microprocessor 504 which continually monitors the relative angular or rotational position of the cam follower 348 with respect to the clutch plate 350. When the relative angular position indicates that the rotating member 336is engaged, the microprocessor 504 deenergizes the electromagnet 356 allowing the clutch plate 350 and cam ramp 354 of the cam assembly 342 to rotate free of the electromagnet 356 and housing 314.
To disengage the differential lock 312 from the first position, an electric signal from the microprocessor 504 reenergizes the electromagnet 356 coil 358 thereby preventing the clutch plate 350, reaction hub 352 and cam ramp 354 of the cam assembly 342 from rotating. The rotating cam follower 348 then moves from the high height edge portion of the contoured edge surface 378 of the cam ramp 354 to the low height edge portion of the V-shaped notches 380 of the cam ramp 354 thereby moving the rotating cam follower 348 axially rearward and the return spring 400 pushes the rotating member 336 out of engagement with the outer clutch housing 330. The sensors 508 and 510 and microprocessor 504 then detect from the relative angular position of the cam follower 348 with respect to the cam assembly 342 when the rotating member 336 is disengaged. When this occurs the microprocessor 504 interrupts electric current to the electromagnetic coil 358 thereby releasing the clutch plate 350, reaction hub 352 and cam ramp 354 of the cam assembly 342 to freely rotate in synchronization with the cam follower 348. The differential lock 312 is now disengaged with the rotating member 336 in the second position shown in BWA-91096A - 38 figure 24. This frees the axle shaft 328 and differential case 316 for relative rotation with respect to each other and restores dif f erential action to the differential 310.
The electromagnetically actuated lock 312 of differential 500 can also be controlled manually with a simple on-off switch for microprocessor 504. It can also be controlled automatically by an auxiliary system.
For instance, the differential 500 can be locked automatically in the event of excessive wheel slip by feeding two speed signals to the microprocessor 504 that indicate the respective speeds of the differential case 316 and the axle shaft 328. These speed signals may be generated by series of teeth 524 and 526 that are is integrally formed on the differential case 316 and the axle shaft 328 that are located next to respective proximity switches or sensors 528 and 530 thatare mounted on the axle housing 314. As the differential case 316 and the axle shaft 328 rotate, the series of teeth 524 and 526 pass by the sensors 528 and 530 generating speed signals that are fed to the microprocessor 504 via wires 532 and 534. The microprocessor 504 compares the speed signals and when a speed differential above a predetermined threshold which indicates wheel slip occurs, the microprocessor 504 energizes the electromagnet 356 to engage the differential lock 312. The microprocessor 504 constantly monitors the speed signals so that when the speed differential drops below the predetermined threshold, the electromagnet 356 is energized by the microprocessor 504 to disengage the differential lock 312.
This auxiliary system for operating the differential lock 312 automatically can be used with the earlier embodiment of the differential shown in figures BWA-91096A - 39 20-23. On the other hand the auxiliary system of that embodiment that uses an accelerometer 420 can also be used in this latter embodiment shown in figures 24 and 25.
The documents, patents and patent applications referred to herein are hereby incorporated by reference.
Having described presently preferred embodiments of the invention, it is to be understood that it may be otherwise embodied within the scope of the appended claims.
- 40

Claims (18)

1. A power transmitting assembly having a first drive member (16, 318) and a second drive member (26, 328) that are mounted on a fixed support (24, 314) and a lock for locking the f irst drive member and the second drive member together so that the drive members rotate in unison with respect to the support, the power transmitting assembly comprising:
a first rotatale assembly (16, 40, 42, 316) in communication with the first drive member (16, 318), a second rotatable assembly (66, 68, 334, 336) in communication with the second drive member (26, 328), the second rotatable assembly including an axially movable rotating member (68, 336), means (86, 98, 100, 102, 342, 344, 348, 400) for moving the rotating member axially between a first position, wherein the first rotatable assembly operatively engages the second rotatable assembly, and a second position, wherein the first rotatable assembly disengages from the second rotatable assembly; and a non rotatable electromagnetic means (122, 166, 356) attached to the fixed support for nonrotation with respect to the first drive member and the second drive member for activating the moving means.
2. The power transmitting assembly of Claim 1 wherein said moving means comprises: 30 a cam assembly (96, 342) rotatable about said second rotatable assembly (66, 68, 334, 336) including a contoured outer rim (134, 376) having at least one vshape notch (136, 380) to form a low height edge portion and a high height edge portion; BWA-91096A a return spring (101, 400) for yieldably biasing the rotating member (68, 336) toward said second position; and an axially movable cam follower (102, 348) rotatable with the second rotatable assembly and responsive to the contoured outer rim of the cam assembly; whereby the electromagnetic means (122, 166, 356) activates the moving means by locking the cam assembly against (96, 342) rotation to cause the cam follower (102, 348) to move axially as the cam follower rotates between said low height edge portion and high height edge portion and compresses the return spring (101, 400) enabling axial movement of the rotating member (68, 336) to the first position.
is
3. The power transmitting assembly of Claim 2 wherein the moving means further comprises an engaging spring (98, 344) for axially moving the rotating member to the first position, wherein the cam assembly (96, 342) comprises a clutch plate (140, 350) juxtaposed the electromagnetic means (122, 166, 356) and a cam ramp (107, 354) that includes a contoured outer rim (107, 376) having two v-shaped notches (136, 380) forming a low height edge portion and a high height edge portion, wherein the cam follower (102, 348) comprises two prong members (152, 392) that extend over the rotating member and provide a reaction surface (162, 382) to compress the return spring (101, 400) as the cam follower moves axially forward, and wherein the power transmitting assembly further comprises a spring (120, 372) disposed between the clutch plate (140, 350) and the reaction hub (106, 352) for biasing the clutch plate (140, 350) against the electromagnetic means (122, 166, 356).
BWA-91096A
4. The power transmitting assembly of Claim 1 further comprising a means (202, 204, 206, 207, 408r 410, 412, 414, 508, 510, 512, 514) for determining the position of the rotating member for controlling the
5 electromagnetic means (122, 166, 356) in response to the position of the rotating member. 5. The power transmitting assembly of claim 4 wherein the electromagnetic means (122, 166, 356) is energized to activate the moving means for moving the rotating member (68, 336). axially to the first position or to the second position and wherein the means (202, 204, 206, 207, 408, 410, 412, 414, 508, 510, 512, 514) for determining the position of the rotating member deenergizes the electromagnetic means (122, 166, 356) aftertthe rotating member (68, 336) is moved axially to the first position or to the second position.
6. A locking hub assembly (18) for operatively engaging and disengaging a power driven axle (26) to a wheel, the locking hub assembly (18) comprising:
a first rotatable assembly (16, 40, 42) in communication with the wheel (14); a second rotatable assembly (66, 68) in communication with the power driven axle (26), the second rotatable assembly including an axially movable rotating member (68); a means (96, 98, 100, 102) for moving the rotating member axially between a first position, wherein the first rotatable assembly (16, 40, 42) operatively engages the second rotatable assembly (66, 68), and a second position, wherein the first rotatable BWA-91096A assembly (16, 40, 42) is disengaged from the second rotatable assembly (66); and a nonrotatable electromagnetic means (122, 166), rearward of the second rotatable assembly (66, 68) fixed for nonrotation about the axle for activating the moving means.
7. The locking hub assembly of claim 6 wherein the first rotatable assembly comprises a rotor (16) of a tubular shape having about the inner circumference thereof, a plurality of spaced splines (44) extending longitudinally rearward from a forward end of the rotor and an inner circumferential retaining groove (46) forward of the splines; and an outer clutch housing (40) positioned concentrically within the rotor and of a tubular shape having about the forward inner circumference, spaced radially inwardly directed teeth (52), and about the outer circumference, spaced radially outwardly directed splines (54) and a retaining groove (50), wherein the outer clutch housing splines (54) engage the rotor splines (44) and the rotor retaining groove (46) and the outer clutch housing retaining groove (50) are in opposing relation to receive a retaining ring (40) to cooperatively maintain the axial position of the rotor with respect to the outer clutch housing; and wherein the second rotatable assembly (66, 68) comprises a hub sleeve (66) surrounding a portion of the power driven axle (26) forward of the axle retaining ring (34), the hub sleeve (66) of a tubular member having external spaced circumferential splines (70) and inner spaced circumferential splines (72), the inner hub sleeve splines (72) engaging the axle splines (30); and an axially movable rotating member (68) including a tubular member and a radially extending rim (90) having about the external circumference, spaced radially BWA-91096A outwardly extending teeth (92) and at least two opposing f lat surfaces (154) extending longitudinally between opposing two pairs of teeth and along said tubular member, and about the inner circumference, spaced longitudinally extending splines (94); the rotating member inner splines (94) engaging the splines (72) of the hub sleeve.
8. The locking hub assembly of claim 7 wherein the moving means (96, 98, 100, 102) comprises:
a cam assembly (96) rotatable about the second rotatable assembly (66, 68) including a contoured outer (134) rim having at least one v-shape notch (136) to form a low height edge portion and a high height edge portion; an engaging spring (98) and a return spring (101) for yieldably biasing the rotating member (68) between the first position and the second position; and an axially movable cam follower (102) 20 rotatable with the axle (26) and responsive to the contoured outer rim (134) of the cam assembly (96); whereby said electromagnetic means (122, 166) activates the moving means (96, 98, 100, 102) by locking the cam assembly (96) against rotation to cause the cam follower (102) to move axially as the cam follower (102) rotates between the high height edge portion, such that the cam follower (102) compresses the return spring (101) enabling the engaging spring (98) to axially move the rotating member (68) to the first position; and the low height edge portion, such that the cam follower (102) releases the return spring (101) to axially move the rotating member (68) to the second position thereby compressing the engaging spring (98).
BWA-91096A - 45 -
9. The locking hub assembly of claim8 wherein the cam assembly (96) comprises a clutch plate (140) juxtaposed the electromagnetic means (122, 166) and a cam ramp (107) that includes a contoured outer rim (134) having two v-shaped notches (136) forming a low height edge portion and a high height edge portion, wherein the cam follower (102) comprises two prong members (152) that extend over the rotating member (68) and provide a reaction surface (162) to compress the return spring (101) as the cam follower moves axially forward, and wherein the locking hub assembly further comprises a spring (120) disposed between the clutch plate (104) and a reaction hub (106) for biasing the clutch plate (104) against the electromagnetic means.
is
10. The locking hub assembly of claim 9 further comprising a means (202, 204, 206, 207) for determining the position of the rotating member (68) by detecting the relative angular displacement of the second rotatable assembly (66, 68) with respect to the electromagnetic means (122, 166), the said determining means comprising a means (202, 204, 206, 207), in communication with the second rotatable assembly (66, 68), for signaling the angular displacement of the second rotatable assembly (66, 68); at least one sensor (202, 206) in communication with the electromagnetic means (122, 166) responsive to the signaling means to detect the relative angular displacement between the second rotatable assembly (66, 68) and the electromagnetic means; and a signal processor (189) in communication with the sensor for measuring the relative angular displacement between the second rotatable assembly and the electromagnetic means to determine the position of the axially movable rotating member; and wherein the electromagnetic means (122, 166) comprises BWA-91096A - 46 - a magnetic coil of encapsulated interior windings of wire having an annular shape; and a power washer (166) of a disc shape positioned contiguous and rearward of the magnetic coil, the power washer (166) including a plurality of conductor rings separated by a plurality of insulator rings, the conductor rings (190) in communication with the magnetic coil, at least one sensor and the signal processor.
BWA-91096A 47 -
11. A dif f erential assembly having a f irst drive member (318) and a second drive member (328) that are mounted in a housing (314) and a lock (312) for locking the first drive member and the second drive member together so that the drive members rotate in unison in the housing, the differential assembly comprising:
a first rotatable assembly (316) in communication with the first drive member, a second rotatable assembly (334, 336) in communication with the second drive member (328), the second rotatable assembly including an axially movable rotating member (336), means (342, 344, 348, 400) for moving the rotating member axially between a first position, wherein the first rotatable assembly operatively engages the second rotatable assembly, and a second position, wherein the first rotatable assembly disengages from the second rotatable assembly, a non rotatable electromagnetic means (356) attached to the housing for nonrotation with respect to the first drive member and the second drive member for activating the moving means, and a means (408, 410, 412, 414, 508, 510, 512, 514) for determining the position of the rotating member for controlling the electromagnetic means in response to the position of the rotating member.
12. The differential assembly of Claim 11 wherein said moving means comprises:
a cam assembly (342) rotatable about said second rotatable assembly including a contoured outer rim (376) having at least one v-shape notch (380) to BWA-91096A f orm a low height edge portion and a high height edge portion; a return spring (400) for yieldably biasing the rotating member (336) toward said second position; and an axially movable cam follower (348) rotatable with the second rotatable assembly and responsive to the contoured outer rim of the cam assembly; whereby the electromagnetic means (356) activates the moving means by locking the cam assembly (342) against rotation to cause the cam follower (348) to move axially.as the cam follower rotates between said low height edge portion and high height edge portion and compresses the return spring (400) enabling axial movement of the rotating member to the first position.
13. The differential assembly of Claim 12 wherein the moving means further comprises an engaging spring (344) for axially moving the rotating member (336) to the first position, wherein the cam assembly (342) comprises a clutch plate (350) juxtaposed the electromagnetic means (356) and a cam ramp (354) that includes a contoured outer rim (376) having two v-shaped notches (380) forming a low height edge portion and a high height edge portion, wherein the cam follower (348) comprises two prong members (392) that extend over the rotating member (336) and provide a reaction surface (393) to compress -the return spring (400) as the cam follower moves axially forward, and wherein the differential assembly further comprises a spring (372) disposed between the clutch plate (350) and the reaction hub (352) for biasing the clutch plate (350) against the electromagnetic means (356).
BWA-91096A - 49 -
14. The differential assembly of claim 13 wherein the means for determining the position of the rotating members detects the relative angular displacement of the cam follower (348) with respect to the cam assembly (342) and wherein the electromagnetic means (356) is energized to activate the moving means (342, 344, 348, 400) for moving the rotating member (336) axially to the first position or to the second position and wherein the means for determining the position of the rotating member (336) deenergizes the electromagnetic means (356) after the rotating member is moved axially to the first position or to the second position.
15. The differential assembly of claim 14 wherein the first rotatable assembly (316) comprises an outer clutch housing (330) of tubular shape having internal teeth (332), and wherein the axially movable rotating member (336) of the second rotatable assembly (334, 336) has external teeth (340) that engage the internal teeth of the first rotatable assembly when the rotating member is in the first position.
16. A power transmitting assembly substantially as herein described with reference to the accompanying drawings.
17. A locking hub assembly substantially as herein described with reference to the accompanying drawings.
18. A differential assembly substantially as herein described with reference to the accompanying drawings.
GB9318739A 1992-09-29 1993-09-09 Power transmitting assembly Expired - Fee Related GB2270958B (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US95485592A 1992-09-29 1992-09-29
US11119093A 1993-08-27 1993-08-27

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GB2270958A true GB2270958A (en) 1994-03-30
GB2270958B GB2270958B (en) 1996-02-14

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KR (1) KR100285140B1 (en)
DE (1) DE4333205A1 (en)
GB (1) GB2270958B (en)

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GB2286435A (en) * 1994-02-14 1995-08-16 Borg Warner Automotive Power transmitting assembly
WO2007100594A2 (en) 2006-02-22 2007-09-07 American Axle & Manufacturing, Inc. Method and apparatus for transmitting axle sensor data
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US7837585B2 (en) 2006-11-27 2010-11-23 American Axle & Manufacturing, Inc. Linear actuator with position sensing system
CN105034796A (en) * 2014-04-23 2015-11-11 沃恩工业有限公司 Electromagnetic pulse disconnect system and methods

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GB2286435B (en) * 1994-02-14 1998-08-12 Borg Warner Automotive Power transmitting assembly
GB2286435A (en) * 1994-02-14 1995-08-16 Borg Warner Automotive Power transmitting assembly
US7878314B2 (en) 2005-05-26 2011-02-01 American Axle & Manufacturing, Inc. Power transfer device having sensor circuit with dual sensors for identifying locking state
EP1994305A4 (en) * 2006-02-22 2009-07-29 American Axle & Mfg Inc Method and apparatus for transmitting axle sensor data
EP2002155A2 (en) * 2006-02-22 2008-12-17 American Axle & Manufacturing, Inc. Two wire dual sensor differential locking state detection system
EP2002155A4 (en) * 2006-02-22 2009-07-29 American Axle & Mfg Inc Two wire dual sensor differential locking state detection system
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US7876186B2 (en) 2006-08-21 2011-01-25 American Axle & Manufacturing, Inc. Electronically actuated apparatus
US7682279B2 (en) 2006-08-21 2010-03-23 American Axle & Manufacturing, Inc. Electronically actuated apparatus using solenoid actuator with integrated sensor
US7764154B2 (en) 2006-08-21 2010-07-27 American Axle & Manufacturing, Inc. Electronically actuated apparatus using solenoid actuator with integrated sensor
US7785224B2 (en) 2006-08-21 2010-08-31 American Axle & Manufacturing, Inc. Annular solenoid with axially overlapping electromagnet and armature
US7825759B2 (en) 2006-08-21 2010-11-02 American Axle & Manufacturing, Inc. Annular actuator having plunger configured to translate through a viscous liquid
US7837585B2 (en) 2006-11-27 2010-11-23 American Axle & Manufacturing, Inc. Linear actuator with position sensing system
US8057345B2 (en) 2006-11-27 2011-11-15 American Axle & Manufacturing, Inc. Linear actuator with position sensing system
US7744500B2 (en) 2007-01-31 2010-06-29 American Axle & Manufacturing, Inc. Electronic locking differential with direct locking state detection system
US7942780B2 (en) 2007-01-31 2011-05-17 American Axle & Manufacturing, Inc. Electronic locking differential with direct locking state detection system
CN105034796A (en) * 2014-04-23 2015-11-11 沃恩工业有限公司 Electromagnetic pulse disconnect system and methods
CN105034796B (en) * 2014-04-23 2018-06-15 沃恩自动化有限责任公司 Electromagnetic pulse disconnects system and method

Also Published As

Publication number Publication date
DE4333205A1 (en) 1994-03-31
GB9318739D0 (en) 1993-10-27
GB2270958B (en) 1996-02-14
JPH06200958A (en) 1994-07-19
KR940006832A (en) 1994-04-25
KR100285140B1 (en) 2001-03-15

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Effective date: 20020909