CA1047280A - Speed and torque sensitive clutch assembly - Google Patents

Abstract

ABSTRACT OF THE DISCLOSURE
A clutch assembly for use with a V-belt drive which includes a pair of sheave plates, and centrifugal weight means that tends to change the V-belt drive sheave setting to maintain a selected speed. That weight means are on pivoting arms driven by a drive shaft that have ends acting through pivoting sliding shoes against one of the sheave plates. The clutch assembly includes ramps or cams which are effective between the sheave plates to tend to vary the spacing of the plates as a function of the torque transmitted by the clutch assembly.

Description

1047~0 The present invention relates to a centrifugal clutch drive sheave for a V-belt drive used for powering vehicles or other devices through a V-belt. The clutch of the present invention includes centrifugal force or speed responsive means for adjusting the sizeof the drive sheave and also cam operators that are responsive to torque. The drive sheave has one side plate that is movable in respect to the other side plate to effect the size adjustment.
The speed response devices include weights on the ends of pivoting arms that tend to move the V-belt drive sheave to position wherein the effective driving diameter will increase as speed increases. Suitable wear shoes are provided on the arm to form shoes to reduce excessive wear at the area of contact of the arms and the movable plate of the sheave.
~!Reducing wear increases the reliability of the clutches and reduces tendency of the actuators to "hang up". The movable portion of the sheave is axially slidable on a hub to which the stationary side plate is attached and also the movable plate is connected to the hub by a coil spring so it may rotate with respect to the stationary side plate, but is restrained by the spring.
~,Separate camming members are provided between the ;movable plate portion of the sheave and the hub, and these camming members are positioned so that as the torque increases and there is a tendency of the movable plate to rotate relative to the other side plate, the camming members will tend to change the size of the V-belt sheave as the relative rotation occurs. The torsion spring will resist the relative rotation.

In this way the clutch is both speed and torque sensitive to -1- ~

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give smooth efficient operation.
The device is made primarily for operation in ve-hi~s, such as snowmob es or the like but can be used for other applications where a V-b~t drive is utilized, and a desire to get the maximum available power from the engine '.~ across a set speed range.
Reference is made to the accompanying drawings wherein:
Figure 1 is an end elevational view of a clutch made according to the present invention;
Figure 2 is a side elevational view of the device of Figure l;
Figure 3 is a sectional view taken as on line 3--3 in Figure l; `
Figure 4 is an exploded view of the device with a ~
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clutch cover shown folded open and illustrating inner working details of the clutch;

; Figure 5 is a sectional view t~eken as on line 5--5 `~ in Figure 4; and ~. ., i Figure 6 is a view substantially the same as Figure 3 showing the clutch in a high speed position.
` Referring to the drawings, the clutch assembly illus- `
trated generally at 10 is of the type used with a V-belt drive, and wherein the clutch assembly is mounted directly onto an engine output shaft 12. This type of a clutch is primarily used ; at the present time in snowmobiles and other similar vehicles, but can of course be used with any desired unit. The clutch generally drives a driven member which then is connected to the output drive for the vehicle. The clutch is of the ` type that is speed sensitive to the extent that it will permit : '.

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the sheave to open and let the belt drop down onto the center portions of the hub in an engine idle position when the engine speed drops. As the engine speed ~icks up, the sheave side plates tend to move together, to first drive the belt with a smaLl effective diameter sheave, and as the speed increases, the movable sheave side plates move toward the other plate to position wherein the effective drive diameter is increased to a maximum. This type of clutch is quite well known in the art, but has some limitations in previous devices in that wear has been a problem.
The clutch assembly 10 includes a main mounting hub illustrated generally at 11 that mounts onto the drive shaft 12 of an engine that is powered. The hub itself is drivably mounted relative to the drive shaft 12, and as can be seen, it can be mounted onto the drive shaft 12 with a suitable tapered surface 13. The shaft 12 has a taper as well that can be held against the inner taper by the use of a cap screw 14 acting through the clutch assembly pushing the tapered surfaces together. The hub 11 includes the stationary sheave side plate or portion 15. The stationary sheave plate comprises one half of a V-belt sheave and it is fixed to the hub, thus it is called herein the statrnary side plate. The hub 12 itself also includes a center belt idler support section 16, which is of sufficient axially length in direction of the axis of rotation of the clutch to provide a support surface 16A not only for the V-belt 17 when the V-belt is in its lower-most position, but also provides a support of sufficient stabil-:,,.
ity for a movable sheave side plate 20 that comprises the other half of the drive sheave and which engages the other side surface .

10472t30of the belt 17 from the stationary ~ate 15. The movable plate 20, as shown, includes an in~ernal bushing 21 that mounts over the surface 16A of the hub portion 16. ~.e movable sheave plate 20 i.s the movable part of the clutch, and it also includes a hub portion 22 that is concentric with the hub 11, and the hub 22 has an opening of size to fit over the hub 11. -At the outer end of the hub 11, that is the end opposite from the fixed sheave portion 15 the hub is turned ~
down to form a smaller diameter portion indicated at 23. The ~-hub 22 surrounds this outer end portion 23. The portion 23 ; joins the hub portion 16 at a shoulder 24, and a coil spring 25 is mounted over the hub portion 23. The coil spring 25 has an integral end projection or retainer 26 formed thereon at the end adjacent hub portion 16. The projection extends in axial direction of the hub, and protrudes into an opening defined in ~ the shoulder 24 of the hub portion 16 so that the coil spring ~ 25 is restrained from rotation with respect to the hub ~ at this end of the spring. In other words, the end of the spring adjacent theshoulder 24 is held from rotation by the pro-jection 26 that enters ~provided opening in the hub portion16 at the shoulder.
The opposite end of the coil spring 25 has a radially extending projection or finger 27 that extends outwardly from the coils of the spring 25 and projects up into an axially extending slot or groove 28 which is defined in the interior of the hub 22. Th:is slot 28 is positioned under one of three axially extending exterior ribs or lugs 22A formed and r~sed from the outer surface of the hub 22. These lugs 22A are seen in Figure 4 on the right hand side of the drawing, and .,.~

,, 1047280 the general diameter of the hub 22 is shown in the lower portionof E'igure 3. Thus, the radial finger 27 prevents the movable portion of the sheave from rotating with respect to the hub 11 unless a force is exerted on the spring 25. The movable portion, ~, inc]uding the plate 20 can "wind" the spring up and rotate with respect to the fixed sheave plate 15, but it must overcome the resistance of the spring for such rotation.
The finger 27 of spring 25 will slide along the slot 28 and thus will permit the movable sheave 20 to move in and out in axial direction under axial forces, without substantially hindering this in and out movement. ~ - -However, the spring 25 does resist inward movement , of the movable portion through different thrust carrying means as will be definedO The internal diameter of the bore , through the hub 22 is of size to clear the coils of the spring 25, as shown. A thrust bearing assembly 31 is pressed into the interior bore of the hub 22 at the outer end thereof, and ;' forms a backing member against which the spring 25 operates.
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A spring retainer and spacer washer 32 is also used. This spring retainer washer has a short sleeve section 32A that fits inside the inner surface of the coils of the spring 25 ;~ adjacent the outer end of the spring ~here the finger 27 is ;.
` provided. The sleeve 32A prevents the coils of the spring 25 from tightening down onto the outer surface of hub portion 23 when the movable sheave 20 rotates with respect to the fixed .;,; .
` sheave 15 which loads the spring in torsion. As was explained, . .
;, the spring retainer 32 and sleeve 32A fit over the hub portion 23, and the sleeve extends inside the coils of the spring 25 a short distanceO The spring end projection 26 at the opposite end of ..;, .~. . .
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the spring merely slips into place in the provided opening in `
the shoulder 24 during assembly. -`
The outer end surfaces of the ribs 22A, as shown at -~
33, generally, in Figure 5, and also as seen in Figure 4, have :~
a surface portion that is perpendicular to the axis of rotation of the hub, and also have a second cam surface portion indicated -~
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generally at 34 that is inclined at an angle to the axis of ~
rotation to form a ramping or cam surface that will provide -axial movement for any surface moved rotationally relative to!' '~' the hub and engaging on the surfaces 34. A co-operating cam - --surface is provided as part of a clutch cover. The clutch cover is as will be explained, held stationary relative to the hub 11 and thus relative rotation between the hub 22 and the clutch cover causes a change in axial position of the movable sheave plate. It is the surfaces 34 on the ends of the ribs 22A cooperating with the other cam surface that provides for adjustment of the movable sheave plate when the m~v able sheave plate tends to rotate with respect to the stationary sheave plate under differing loads on the belt.
At the outer end of the thrust bearing 31, a thrust washer 35 is also provided and this is a wear washer that can be replaced if desired. The washer 35 is merely pressed onto the small shoulder or lip defined on the outer end of the thrust -bearing 31. This thrust washer 35 is a hardened wear washer, while the thrust bearing itself can be made out of other suit-` able materials. It should also be noted that wear shoes indi-cated at 36 are provided at the ends of the ribs 22A and have surfaces 33 and 34 defined thereon, and these wear shoes 36 can be replaced if they tend to wear out.

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The spring 25 resists a compression in axial direction of the clutch from the outer end toward the sheave plate 15, and therefore ~ends to bear against the washer 32 and bearing 31 l;o urge the movable sheave plate away from the stationary sheave plate. The bearing 31 and washer 32 will slide on the outer surface of the hub portion 230 Thus, when the clutch is not rotating, the sheave will ve to position as shown in Figure 3 with the belt 17 down against the surface 16A and there will be no driving of the belt 17.
lOAny movement axially of the movable sheave 20 toward stationary sheave 15 will be resisted by compression of the spring 25 acting against the bearing 31 and washer 32. The axial movement of the movable sheave plate 20 is controlled by pivoting arms that are responsive to centrifugal force. As -shown, a clutch cover assembly illustrated generally at 40 is triangular sha~d, and has a tapered recess 41 that unts on the outer surface of the end of hub portion 23. The end ....
of hub 23 and the inner surface of the recess 41, have matching tapers, so tha~ the clutchcover 40 is held in place with a cap screw 42 that is threaded into the interior of the end portion of the hub 23 as shown. The cap screw 42 has a center opening , ~.
through which the cap screw 14 slidably extends. The cap screw , .
14 then is threadably mounted onto the end of the engine shaft 12. The clutch cover is thus held fixed in axial position with respect to the hub 11 and is driven with the hub. The clutch cover therefore, will rotate with the stationary sheave plate 15, and will not twist or rotate with respect thereto. The clutch cover moves with the hub 11 because of the tapered connection.

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- 104~280 The clutch cover has three bosses 43 which extend radially from the center thereof, and each of these bosses 43 has an interior slot indicated at 44 on the inside thereof.
The slots 44 are each of size to receive an arm 45 that is pivotally mounted on a suitable bolt or pin 46. The pivot axes of the arms are at right angles to the rotational axis of the clutch assembly. Suitable weight members 47 are attached A to the armsl~Ladjacent first ends thereof. The weights 47 are at the ends of the arms adjacent sheave plate 20, and the actuator ends of the arms indicated at 48 carry pivotally mounted wear shoes 49 which have flat surfaces engaging the thrust washer 35. These pivotal shoes 49 provide a flat surface that rides against the thrust washer. The shoes are free to pivot at the mounting to the arms and the arms 45 are free to pivot about pins 46.
In addition, the clutch cover 40 is provided with spiral ramps or cams indicated at 50 on the interior thereof.
These ramps or cams 50 comprise part annular walls that commence ; adjacent the inner surface of the hub cover as at 51, and then taper out in axial direction as they extend annularly to form cams extending toward the stationary sheave portion 15 when the clutch cover is mounted in place. Referring to Figure 4, it can be seen the spiral or cam walls 50 extend from the lines 51 where they join the inner surface of the clutch cover, and extending counter clockwise in Figure 4, terminate at , .
;~ end lines 52, each of which is adjacent one of the arms 45.
The cams or ramps extend axially to the end lines at 52 shown in Figure 5 wherein it can be seen that the lines 52 are slightly outside of a plane defined by the outer peripheral :

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1()4~0 edge 56 of the clutch cover 40. Also, in the sectional view of Figure 5, the starting lines 51 o f one of the cams 50 can be seen. The cams are shown in Figure 5 and in position against surfaces 34 on ribs 22A and are shown actuating the movable sheave portion approximately one half of the total travel of the cams. The cams 50 engage the ends of the ribs 22A. When the clutch is in rest position, the ends of the ribs 22A would be positioned back adjacent the line 51 of each of the cams (there are three ribs and three cams). Any differential ro- -10 tational movement in the proper direction between the movable sheave plate 20 and the stationary sheave portion 15, (which is resisted by the spring 25) will result in a tendency to force the vable sheave plate 20 toward the stationary sheave plate 15, because the end ramp or cam surfaces 34 of the ribs 22A would tend to ride up on the mating edge surfaces of the cams or ramps 50. This would tend to wedge the movable sheave plate in toward the statmary sheave 15, and increase the effective driving diameter of the clutch sheave. The differ-ential in rotation;between the sheave plate 15 and plate 20 is , 20 caused by torque supplied by the engine. The spring 25 ` drives from hub to plate 16, and when the engine is initially started the belt is not driving, but rather rides down on the surface 16A. As the engine is accelerated the arms 45 start to act on the washer 35 to move the hub 22 and sheave plate 20 toward the stationary plate 15 because of the cen-trifugal force on the weights 47 acting through the arm pivot pin 46. The "pick up" speed is determined by the tension of spring 25 resisting compression of the spring as well as the configuration or geometry of arms 45 and the mass of weights 47.
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As the belt 17 starts ~ pick up load, there will be a tendency of the sheave plate 15 to rotate farther than the plate 20.
The differential in movement will also tend to force the movable --plate 20 toward the stationary plate 15. The ends of spring 25 will be twisted so the spring 25 will be loaded in torsion. The axial force on the hub 22 and sheave plate 20 will force the belt outwardly. Desirably the axial force on the movable plate 20 `~ `
at full governed rpm will be about evenly divided between the arms 45 and the ramps 50.
The centrifugal force actuation of the clutch is - achieved by pivoting of the arms 45 about the axis 46, under the centrifugal force developed by the weights 47. The ends 48 of the arms 45 and the shoes 49 bear against the thrust , . .
washer 35 and as the force increases from a speed increase, the shoes push the movable sheave plate 20 axially toward the fixed i. sheave plate 15. The faster the clutch is rotating, which is also the engine shaft speed,the greater the centrifugal force on the weights 47 tend to pivot the arms 45, and, therefore, the greater the output speed will also be because the clutch sheave will have a larger effective driving diameter.
By using the ramps, the weights 47 can be made lighter.
At full governed rpm the weights will be developing their full axial force and the weights will tend to control the engine speed at a set speed. If the load on the belt 17 increases the sheave plates tend to separate. The separating load is resisted ; by the ramps and by the arms 45, in a co-operative effort. The increase in tension of belt 17 tends to cause a downshift and , ~
the ramps will permit the movable sheave plate to back off even if the force from the arms 45 does not decrease. ~his action . -10 -'"

10~ 0 aids in keeping the engine speed at a governed or constant rpm - and thus operation at maximum power even during increased loading of t:he belt 17. The angle of the ramp surfaces 34 also should be selected to achieve desired division of carrying of the axial -- -load on the movable sheaveO The lower angle of the ramp sur-faces 34 with respect to a plane normal to the axis of the clutch, the more influence the ramps and spring will have on the position of the movable sheave plate, and thus the more torque responsive the clutch becomes, and the less speed responsive. The higher the angle of the surfaces 34 (the closer the surfaces 34 become to being parallel to the axis of rotation of the shaft) the less influence the ramps have, and the clutch starts to act like an ordinary centrifugal clutch and less and less torque sensitive.

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The tension and rate of spring 25 can also be selected to provide the pick up speed and the response desired. The spring 25 is loaded both in torsion and compression.
Therefore, a combination of a torque sensitive and speed sensitive clutch is achieved. The centrifugal force ' actuator further includes wear shoes that can be adapted to any centrifugal clutch that uses arms bearing against a surface to provide for a greater wearing surface and prevent the wearing of grooves or depressions in the thrust surfaces from the ends of the arms. In ordinary clutches the arms will tend to flatten when a conventional curved arm end surface is used. The primary purpose of a clutch of this type is to permit the reliable operation of the engine at its peak horsepower. When the power peak of the engine reduces, for example from running at an increased elevation, the power peak is at approximately the same rpm. With the present clutch the ramps will permit the sheave to ,;' -11-~ 04'^~ 0 bac~ off slightly because of lower torque being carried, while the engine will operate at its desired rpm without changing the weights 47. In conventional governor or speed sensitive clutches the larger weights used at lower elevation will force the drive sheave to its maximum drive diameter and with normal torque converters will not work because the power being produced by the engine will drop and the clutch will not back off enough when the engine is loaded for satisfactory operation. In most ~
conventional centrifugal V-belt sheave clutches, the centrifugal ~ -weights have less mass for higher elevations~ -~
In the device as shown, the surfaces 34 form an included angle of about 37 with respect to a plane perpen-; dicular to the axis of the clutch and passing through washer 35O The clutch disclosed works well with an engine having a fairly "peaky" torque curve. Also the power curve of an engine used with the clutch as shown comes at a speed greater than the speed at which maximum torque is developed. Thus, if the speed of the engine drops, its developed torque goes up slightly and this will tend to affect the position of the hub ~ 20 on ramp 50.
; In engines with fairly flat torque curves, a higher angle of ramp surface is generally better so that the c lutch is less torque responsive, but still the clutch has some torque response as well as speed response.
The clutch parameters can be varied quite widelyto suit different engines and load conditions. However, the force necessary to hold the movable sheave in its driving position will be shared by the centrifugal force generating ; mea~s and the torque responsive ramp surfaces.

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Claims (4)

The embodiments of the invention in which an exclu-sive property or privilege is claimed are defined as follows:

1. A clutch having a mounting hub rotatable about an axis of rotation, a first sheave side portion fixed to said mounting hub, a second movable sheave side portion axially slidably mounted on said mounting hub and having a surface portion substantially perpendicular to said axis of rotation, centrifugal force responsive means to actuate said second movable sheave side portion in a direction along said axis of rotation with respect to said first sheave side portion to create an axial force on said second movable sheave side portion tending to move it toward said first sheave side portion at a selected rotational speed, said centrifugal force responsive means comprising an arm having one end biased to move in a direction toward and engage said surface portion from centri-fugal force developed by rotation of said hub, and sliding shoe means pivotally mounted to said one end of said arm about an axis substantially perpendicular to the axis of rotation, said shoe means having a surface area engaging and mating with said surface portion of said second sheave side portion to provide a substantial contact area between said shoe means and said surface portion.

2. The combination as specified in Claim 1 wherein said arm comprises a pivotally mounted arm mounted for pivoting movement relative to said second movable sheave side portion about a pivot axis generally parallel to the pivot axis of said shoe means to the end of said arm.

3. The combination as specified in Claim 2 wherein said weight actuated portion of said arm comprises a weight on an opposite end of said arm from said shoe means and tending to move said arm about the pivot of said arm to bias said end of said arm during said shoe means toward the surface portion.

4. A clutch having a mounting hub rotatably about an axis of rotation, a first sheave side portion fixed to said mounting hub, a second movable sheave side portion axially slidably mounted on said mounting hub and having an annular surface substantially perpendicular to said axis of rotation, centrifugal force responsive means to actuate said second movable side portion in a direction along said axis of rotation with respect to said first sheave side portion to create an axial force on said second movable sheave side portion tending to move it toward said first sheave portion at a selected rotational speed, said centrifugal force responsive means comprising an arm having first and second ends, said arm being pivotally mounted with respect to said hub between said first and second ends, said arm tending to pivot to move said second end of said arm in a direction axially along said hub from centrifugal force on said arm developed by rotation of said hub, and sliding shoe means pivotally mounted to said second end of said arm about an axis substantially parallel to the axis of pivot between the arm and hub and substantially perpendicular to said axis of rotation, said shoe means having a flat surface area engaging said annular surface of said second sheave side portion to provide a flat substantial contact area between said shoe means and said annular surface.