US2757550A

US2757550A - Motor driven clutch mechanism

Info

Publication number: US2757550A
Application number: US367139A
Authority: US
Inventors: Edward J Weinfurt
Original assignee: McGraw Electric Co
Current assignee: McGraw Electric Co
Priority date: 1953-07-10
Filing date: 1953-07-10
Publication date: 1956-08-07
Anticipated expiration: 1973-08-07

Description

INVENTOR.

Eda w 6 C/ A1 20 E. .J. WEINFURT MOTOR DRIVEN CLUTCH MECHANISM Filed July 10, 1953 Aug. 7, 1956 Unite States Patent 2,757,550 MOTOR DRIVEN CLUTCH MECHANISM Edward J. Weinfurt, West Allis, Wis assignor to McGraw Electric Company, Milwaukee, Wis., a corporation of Delaware Application July 10, 1953, Serial No. 367,139 r cratin (11. 74-472 This invention relates to hydraulically operating rotating clutching devices.

This application is a continuation-in-part of my prior application, Serial No. 216,287, filed March 19, 1951, for Motor Driven Clutch Mechanism, now abandoned.

It is a primary object of this invention to provide a hydraulic clutch mechanism adapted to alternatively reversibly translate the rotational motion supplied thereto.

It is a further object of this invention to provide a hydraulic rotational clutch mechanism which may be most expeditiously utilized in conjunction with automatic control devices for regulating an electrical quantity.

It is a specific object of this invention to provide a hydraulic clutch mechanism including a driving disk and at least one driven disk, the driving disk being operatively associated with the armature of an electric motor, said armature arranged to move longitudinally of its axis responsive to variations in electrical energy supplied to the energizing coil of said motor.

In the drawing:

Fig. 1 is a fragmentary elevational view, partly in section, showing the novel hydraulic clutching mechanism operatively associated with the rotor of a voltage sensitive electric motor.

Fig. 2 is a sectional view taken along lines 2-2 of Fig. 1.

Fig. 3 is a view in cross-section of the upper driven disk of the novel clutching mechanism.

Fig. 4 is a side elevational view of the driving disk of the clutching mechanism.

Fig. 5 is a top plan view of the driving disk illustrated in Fig. 4.

In the drawing, the reference character M generally identifies a novel shaded pole motor which is more fully described and specifically claimed in the copending application, Serial No. 216,050, filed on March 16, 1951, by Anthony Van Ryan and assigned to the same assignee as the present invention, now Patent No. 2,730,671 dated January 10, l956. The shaded pole motor M comprises an energizing coil 1, a field structure 2, shading windings 3 and an armature or rotor 4. i

The rotor 4 is secured to a bushing sleeve 5, both being arranged to normally rotate as a unit about a spindle 6. The spindle is positioned between spaced upper and lower supporting structures 7 and 8. The upper and lower supporting structures are spaced from one another and retained in place by means of laterally spaced thrupins or rivets 9 in combination with spacer members 10 and 11 circumjacent therewith. The bushing sleeve 5 is preferably made shorter than the space between the upper and lower supporting structures 7 and 8 to permit a predetermined free movement along its longitudinal axis as will hereinafter be described.

The novel clutch mechanism is designated generally by the reference character C, and includes a driving disk 12, which is fixedly attached to the bushing sleeve 2,757,550 Patented Aug. 7, 1956 'ice 5. The sleeve 5, the driving disk 12 of the clutch and the rotor of the motor 4 thereby move as a unit both rotationally and longitudinally of the axis of the spindle 6. In addition to the driving disk, the clutch comprises upper and lower driven

disks

13 and 14 respectively, and a flow control cylinder plate 15 encircling the driving disk 12.

The plate 15 is stationarily supported from the rivets 9 and is laterally spaced from the supports 7 and 8 by means of the spacer members 10 and 11 engaging either side of the plate. The support arrangement is clearly shown in Fig. 2, wherein the upper spacer member 10 contacts the marginal surface defining an opening extending through the plate 15 and arranged to receive the rivet 9. Additional supporting rivets are located oppositely of those shown, but parts have been broken away and eliminating the additional members to provide a clear showing. of the operating structure.

The driven

disks

13 and 14 are freely slidable longitudinally and rotationally of the bushing sleeve 5, and are each provided with

integral pinion gears

16 and 17. The pinion gears 36 and 1.7 are arranged to supply rotational motionto a power take-oft" countershaft 1S positioned between the supporting structures 7 and 8. The upper pinion gear to inashes with an upper driven gear 20 fixedly positioned on the countershaft 18 providing a direct drive. The lower pinion gear 17 meshes with an idler pinion gear 21, which in turn meshes with a lower driven gear 22, fixedly positioned on the countershaft 13, to provide rotational motion in a reverse direction from that of the upper driven gear 29.

In order to provide adequate clearance between moving parts, it is deemed preferable to provide a sleeve 23, which is freely slidable rota'tively and axially relative to the portion of the bushing sleeve extending below the pinion gear 17, as shown in Fig. l. The sleeve merely acts to space the lower driven disk 14 and its gear portion 17 from the lower supporting structure 3 when positioned as shown in Fig. 1, and as will hereinafter be described.

The novel motor M, with which the novel clutch mechanism C is preferably operatively associated, is made responsive to electrical quantity variations impressed thereon. For instance, if voltage greater than a predetermined norm is supplied to the energizing coil 1, the rotor 4 will be caused to be drawn upwardly. Accordingly, if the voltage is reduced below the norm, the rotor 4 will move downwardly from the vertical operating position shown in the drawing. If the device is operated in a position other than as shown, it will be obvious that any of well-knowirbiasing means may be used as a substitute for gravitational forces. It will be apparent that the novel device is especially beneficial when used in conjunction with distribution transformer voltage regulation.

Since the driving disk 12 of the clutch mechanism is rigidly attached to the bushing sleeve 5, it will move as a unit along with the rotor 4. A predetermined nominal voltage will permit the driving disk 12 to normally operate centrally of the flow control cylinder plate 15. Both of the opposed sides of the driving disk 12 are preferably provided with a series of circumferentially spaced radial oil exit grooves 25 along the outer periphery. Each of the driven

disks

13 and 14 are pro vided with an annularly recessed portion 26 and a plurality of annularly spaced oil intake ports 2? which arepreferably positioned to over-lap the radial oil exit grooves 25 in the driving disk 12. An oil exit port 28 is provided on either side of the driving disk 12 and consists merely of the circumferential space normally exisan between the driven

disks

13 and 14 and the flow control cylinder plate 15'.

The novel clutch mechanism operates as follows: Assuming that the device is operatively associated with the voltage sensitive motor disclosed in Fig. l of the drawing, the clutching mechanism C is immersed in some hydraulic medium, such as oil. It will be obvious that the motor M will function with equal effectiveness, whether it is immersed in the hydraulic medium or without as shown in Fig.1. For automatic operation, it is preferable to permit the rotor 4 to normally continually revolve, drawing off a working load from the clutch mechanism alternatively on demand.

During normal operation, the driving disk 12 will be caused to continually revolve, and will normally be positioned centrally of the flow control cylinder plate 15, as shown in Fig. 1. While operating in this position, the oil adjacent the driving disk will be set in rapid circular motion. The resultant centrifugal force will cause this oil to escape through the oil escape ports 28 between each of the driven

disks

13 and 14 and the corresponding side of the driving disk 12. This oil is replaced by oil entering through the oil intake ports 27 in each of the driven

disks

13 and 14. The oil flow causes the driven

disks

13 and 14 to normally float away from the cylinder plate 15. Under normal operating condition, the rotational forces imparted to the driven disks will be at a minimum, tending to equally oppose one another, thereby preventing either of the driven disks from rotating.

During normal operating conditions the driving disk 12 continually revolves at the position shown in Fig. 1; that is, within the confines of the wall thickness of the opening in the flow control cylinder plate 15. Since the unit is operating under oil, or other hydraulic medium, the revolving disk 12 will tend to create a slight pressure on either of its opposed sides, thereby maintaining a spaced relationship between the disk 12 and driven

disks

13 and 14. This spacing is adequately maintained to provide a balanced condition wherein neither of the driven

disks

13 or 14 will be caused to rotate.

Assuming a condition that causes the rotor 4 of the motor M to be drawn upwardly, such as an over-voltage When the motor is used as a regulator, the bushing sleeve 5 and the driving disk 12 of the clutch mechanism will accordingly be caused to rise. When the rotor 4 and bushing sleeve 5 are caused to move upwardly, the driving disk 12, attached to the bushing sleeve will rise, causing any oil retained in the oil exit grooves 25 to be centrifugally forced out of the grooves radially of. the disk 12. With the exit port open, oil can no longer be supplied through the intake ports 27 of the upper driven disk 13 at the same rate that it escapes. This results in a decreased pressure between the driving disk and the upper driven disk, forcing them to be drawn towards one another into close engagement. Each of the

disks

13 and 14 are undercut to provide annular recessed portions 26 which distribute the torque towards the outer surface of the. inner face of the respective driven disks where it is most effective. The engaged

disks

12 and 13 will now rotate as a unit, which rotational motion will be transferred to the upper driven gear 20 through the driving pinion gear 16. The countershaft 18 will now be caused to rotate. This rotational motion may be translated to a tap changer where the combined devices M and C are used for regulation of an electrical quantity.

When normal operating conditions are again restored, the rotor 4 of the motor M will be permitted to settle downwardly responsive to gravitational forces. The driving disk 12 of the hydraulic clutching mechanism C will correspondingly move downwardly. As the driving disk settles centrally of the cylinder plate 15, the exit port 28 between the upper driven disk 13 and the driving disk 12 will be restricted, providing increased oil pressure between the disks, which pressure acts to separate them. In addition, the driven

disks

13 and 14 each preferably have a diameter slightly larger than the diameter of the cylindrical opening in the plate 15. This will prevent the driven disk from entering the plate opening as the driving disk settles, further aiding separation of both disks.

It will be apparent that similar action takes place when conditions develop permitting the rotor 4 to settle in a direction downwardly from the normal operating position shown in Fig. 1. Thus, the lower driven disk 14 will be engaged by the lower side of the driving disk 12, thereby being caused to rotate. Since the rotational motion of both the upper and lower driven

disks

13 and 14 is in the same direction, the pinion gear 17 of the lower driven disk 14 preferably meshes with an idler pinion 21. Engagement of the idler pinion gear teeth and the lower driven gear 22, which is positioned on the countershaft 18, will cause this countershaft to rotate in an opposite direction than when driven by the upper pinion gear 16 on the upper driven disk 13.

It will be apparent that as the driven disks are being alternatively driven by the driving disk 12, the disk not in driving engagement will also be caused to revolve because of intermeshing engagement with its cooperating driven gear. This is merely an idling revolution, however, and will have little or no effect on the torsional forces supplied by the working disk as all parts are freely slidable relative to one another on the spindle 6 and are further immersed in the hydraulic medium.

The expression oil used throughout this specification is intended to be broadly construed to cover any of the commonly used hydraulic operating fluids, in ad dition to electrical dielectric cooling fluids.

The novel control device including both the motor M and the clutch mechanism C is an entirely self-contained unit, and may be suitably mounted in a separate container with its own source of hydraulic fluid, or may be placed within the tank of an electrical induction apparatus, using the dielectric fluid as a hydraulic medium.

From the foregoing description, it will be apparent that a novel hydraulic rotational clutch mechanism has been provided, which is conveniently adaptable for automatically alternatively translating rotational motion supplied thereto, and which may be used in conjunction with an electrical quantity regulating device responsive to variations in electrical quantities supplied thereto.

I claim:.

1. A motor driven clutch mechanism arranged to opcrate in a hydraulic medium including a normally disengaged uni-directionally rotating driving disk movable axially responsive to quantity variations in electrical energy supplied to said motor, opposed driven disks coaxially adjacent either side of said driving disk and normally stationary relative to said driving disk, said driven disks each having a plurality of annularly spaced openings concentric with the axis of revolution, said driven disks each being freely movable rotationally and slidable axially relative to said driving disk, each side of said driving disk having a plurality of circumferentially spaced radial grooves, and reversible power take-01f means arranged to be alternatively rotationally driven by said driven disks on engagement of said driven disks with said driving disk responsive to longitudinal movement of said driving disk.

2. A motor driven clutch mechanism arranged to operate in a hydraulic medium including a normally disengaged uni-directionally rotating driving disk movable axially responsive to quantity variations in electrical energy supplied to said motor, a flow control cylinder encircling said driving disk and normally stationary relative to said driving disk, opposed driven disks co-axially adjacent either side of said driving disk, said driven disks each having a plurality of annularly spaced openings concentric with the axis of revolution, said driven disks each being freely movable rotationally and slidable axially relative to said driving disk, each side of said driving disk F having a plurality of circumferentially spaced radial grooves, and reversible power take-off means arranged to be alternatively rotationally driven by said driven disks on engagement of said driven disks with said driving disk responsive to longitudinal movement of said driving disk.

3. A motor driven clutch mechanism arranged to operate in a hydraulic medium including a normally disengaged uni-directionally rotating driving disk movable axially responsive to quantity variations in electrical energy supplied to said motor, a driven disk co-axially adjacent said driving disk and normally stationary relative to said driving disk, said driven disk having a plurality of annularly spaced openings concentric with the axis of revolution and being freely movable rotationally and slidable axially relative to said driving disk, said driving disk having a plurality of circumferentially spaced radial grooves on the side adjacent said driven disk, and power take-off means arranged to be rotationally driven by said driven disk on engagement of said driven disk with said driving disk responsive to longitudinal movement of said driving disk.

4. In combination with an electric motor including an armature arranged to normally uni-directionally rotate and being freely movable longitudinally of its axis simultaneously with its rotation responsive to quantity variations of electrical energy supplied to said motor; a re versible power translating means including a rotational clutch mechanism arranged to operate in a hydraulic medium and a power take-off countershaft, said countershaft having co-axially spaced first and second driven gears aflixed thereto, said second gear intermeshed with an idler pinion gear, said clutch mechanism comprising a driving disk operatively associated with said armature, opposed driven disks co-axially adjacent either side of said driving disk and normally stationary relative to said driving disk, said driven disks each being freely movable rotationally and slidable axially relative to said driving disk, said driven disks each having a plurality of annularly spaced openings concentric with the axis of revolution, each side of said driving disk having a plurality of circumferentially spaced radial grooves, one of said disks arranged to mesh with the first of said driven gears and the other of said disks arranged to mesh with said pinion gear on alternative engagement of said driven disks with said driving disk responsive to longitudinal movement of said driving disk.

5. A rotary clutch mechanism arranged to operate in a fluid medium including a normally disengaged unidirectionally rotating driving disk movable longitudinally of its axis, opposed driven disks co-axially adjacent either side of said driving disk and normally stationary relative to said driving disk, said driven disks each having a plurality of annularly spaced openings: concentric with the axis of revolution, said driven disks each being freely movable rotationally and slidable axially relative to said driving disk, each side of said driving disk having a plurality of circumferentially spaced radial grooves, and reversible power take-off means arranged to be alternatively rotationally driven by said driven disks on engagement of said driven disks with said driving disk responsive to longitudinal movement of said driving disk.

6. A rotary clutch mechanism arranged to operate in a fluid medium including a normally disengaged unidirectionally rotating driving disk movable longitudinally of its axis, a driven disk co-axially adjacent said driving disk and normally stationary relative to said driving disk, said driven disk having a plurality of annularly spaced openings concentric with the axis of revolution and being freely movable rotationally and slidable axially relative to said driving disk, said driving disk having a plurality of circumferentially spaced radial grooves on the side adjacent said driving disk, and power take-01f means arranged to be rotationally driven by said driven disk on engagement of said driven disk with said driving disk responsive to longitudinal movement of said driving disk.

References Cited in the file of this patent UNITED STATES PATENTS 1,132,478 Johnson Mar. 16, 1915 2,385,630 Lear Sept. 25, 1945 2,392,097 Meunier Jan. 1, 1946 2,461,261 Drisko Feb. 8, 1949 2,484,616 Dulaney Oct. 11, 1949 2,488,540 Hollingsworth Nov. 22, 1949 FOREIGN PATENTS 925,656 France Mar. 31, 1947