Horton Manufacturing Company Inc.

Horton Industries, Inc.

James V Hanks

Leonid Dayen

Charles D Raines

Edward D Brooks

Ruth A Litterick

Device (200) for releasing fluid pressure from the pressure chamber of an overload clutch (A) is disclosed including a valve (210) captured in a radial cavity (202) in the cylinder (10) of the overload clutch (A) between a shoulder (204) and a valve cover (212) held by a snap ring (226). The valve cover (212) includes an aperture (228) for receiving a ball (230) and allowing the ball (230) to move radially inwardly to push against the spool member (220) of the valve (210) to unseat its head (221) from a seat (218) but preventing the ball (230) from moving out of the valve cover (212). The ball (230) rolls on a valve actuator (232) mounted to the piston (22). When the cylinder (10) and piston (22) are axially separated by fluid pressure, the ball (230) is located in a dent (234) formed in the valve actuator (232) such that the head (221) of the spool member (220) seals with the seat (218) and prevents release of fluid pressure from the pressure chamber. When the cylinder (10) and the piston (22) move axially against the normal bias direction of the fluid pressure, the ball (230) rolls out of the detent (234) and pushes against the spool member (220) to unseat the head (221) from the valve seat (218). In the most preferred form, the valve actuator (232) is adjustably mounted to the piston (22) by a turnbuckle (238), with the valve actuator (232) and the turnbuckle (238) formed of hexagonal stock for receipt in a wrench.

Fluid pressure releasing device for overload apparatus

An overload apparatus is shown as an overload single position clutch having a drive ring which is reciprocated by springs and by a cylinder slideable on a piston by fluid pressure. The drive ring includes a multiplicity of ball receiving cavities. A sheave mount is further provided including an integral interface disc having a multiplicity of ball carrying cavities. Balls are captured within the ball carrying cavities by a ball cage secured to the mount. The ball cavities have diameters less than the balls and a shape and size such that the balls do not touch the closed ends or sidewalls of the cavities but rather the open ends form seats for the balls. The ball carrying cavities have diameters greater than the diameters of the ball receiving cavities to predispose the balls to cam out of the ball receiving cavities in the event of reaching a torque overload level. In another embodiment the balls are captured in the ball carrying cavities by constant diameter apertures formed in a carrier ring and a retaining plate, with the aperture diameters of the carrier ring being generally equal to that of the balls and with the aperture diameters of the retaining ring being less than that of the balls.

Overload apparatus

A coupling clutch according to the teachings of the present invention is shown in its most preferred form as including first and second hubs having first and second splined interface discs received thereon. The first interface disc is biased away from the second interface disc and is movable towards the second interface disc by a piston reciprocally mounted to a housing and rotatably mounted to the first interface disc by a bearing mounted therebetween. The splines between the second interface disc and the second hub allow the second interface disc to cant to compensate for axial angular misalignment of the first and second hubs. The housing is further rotatably mounted to the second interface disc. A radially extending, annular lip is provided on the housing which is axially captured between a shoulder and a retaining ring provided on the first hub. Bushing bumpers are provided between the lip and the shoulder and between the retaining ring and the lip. Thus, axial movement of the housing is prevented with respect to the hub. In its most preferred form, the first disc includes a multiplicity of ball-receiving cavities and the second disc includes a carrier member having a multiplicity of balls allowing the same degrees of registry of the first and second discs during clutch activation.

Coupling clutch

A two-speed clutch is shown according to the preferred embodiment of the teachings of the present invention for the selective rotational relation of an input shaft with a first or second sheeve unit having different diameters. The first sheeve unit is rotatably mounted to the input shaft. The second sheeve unit is mounted to a housing in turn rotatably mounted to the input shaft. The clutch includes a friction disc which is located between and frictionally interrelates with the first sheeve unit or the housing. The housing includes a single, reciprocally mounted piston for moving the friction disc. Utilizing a two-speed clutch of the present invention eliminates the requirement of two separate and complete drive units as in prior techniques. Furthermore, since the housing performs multiple functions, i.e., rotatably mounts the second sheeve unit to the input, slidably mounts the piston, acts as the interface for the second sheeve unit with the friction disc, and other functions, the two-speed clutch of the present invention greatly reduces the number of parts and results in a simplicity of construction. Furthermore, the two-speed clutch of the present invention provides a relatively dust and other element free environment for the piston and splined interconnection of the interfacing friction disc with the input.

Two-speed clutch

A fail-safe device for preventing undesired rotation of the output as the result of bearing failure and seizure is shown according to the teachings of the present invention in its most preferred form for use with a clutch engagable in a single driving position. In its most preferred form, the output includes a hub portion which is rotatably mounted to the input of the clutch by a bearing. The output of the clutch further includes a collar portion for receipt upon the hub portion and forming a break away connection therebetween. The driven portion of selectively rotationally interrelating members of the clutch, i.e., teeth in the preferred embodiment shown, is located on the collar portion of the output. Under normal operation and without bearing failure, the collar and hub portions of the output have the same relative rotational position and rotate as a single unit. However, in the event of bearing failure and seizure and assuming the output is not clutched in with the input, relative rotation is allowed between the hub portion and the collar portion of the output to prevent undesired rotation of the machinery or other apparatus connected to the output of the clutch.

Clutch having an output with break away connection

A coupling clutch is shown in its most preferred form as including first and second hubs having first and second splined interface discs received thereon. The first interface disc is biased away from the second interface disc and is movable towards the second interface disc by a piston reciprocally mounted to a housing and rotatably mounted to the first interface disc by a bearing mounted therebetween. The splines between the second interface disc and the second hub allow the second interface disc to cant to compensate for axial angular misalignment of the first and second hubs. The housing is further rotatably mounted to the second interface disc. A radially extending, annular lip is provided on the housing which is axially captured between a shoulder and a retaining ring provided on the first hub. Bushing bumpers are provided between the lip and the shoulder and between the retaining ring and the lip. Thus, axial movement of the housing is prevented with respect to the hub. In its most preferred form, the first disc includes a multiplicity of ball-receiving cavities and the second disc includes a carrier member having a multiplicity of balls allowing the same degrees of registry of the first and second discs during clutch activation.

Coupling clutch having axially captured, rotatable housing

A coupling clutch/brake is shown in its most preferred form as including first and second hubs having first and second splined friction discs received thereon. The first friction disc is movable between the second friction disc and a stationary friction surface mounted to a housing by a piston reciprocally mounted to the housing and rotatably mounted to the first friction disc by a bearing mounted therebetween. The second friction disc is substantially prevented from sliding on the splines with the second hub. The splines between the second friction disc and the second hub allow the second friction disc to cant to compensate for axial angular misalignment of the first and second hubs. In its most preferred form, the housing has a unique construction and specifically includes three generally hemispherical components. The open ends of the first and second shells abut together to form a volume for the first and second friction discs. The open end of the third shell is received on an axially extending flange integral with the second shell. The piston is slidably received on the flange of the second shell and on the third shell.

Coupling clutch/brake and housing

A clutch where the output always comes to the same degrees of registry with the input is shown as including coaxial drive and driven members including a hub for mounting on a drive shaft. The drive member is slidably mounted on the hub and rotatable thereby. The drive member is formed with a multiplicity of ball-receiving cavities which are located radially inward of the periphery of the drive member. The driven member includes a carrier member having a multiplicity of balls mounted thereon for engagement with the cavities. The carrier member includes a flat, radial ring portion and an inner annular flange which provides a first degree of safety by tending to prevent any dislodged balls from the carrier member from travelling inwardly between the drive and driven members and tending to allow the dislodged balls to travel radially outward of the clutch. The carrier and drive members have intermeshing interface teeth. The drive member is moved axially on the hub for engagement of the cavities thereof with the balls of the carrier member as the teeth of the drive member engage the teeth of the ball carrier to thereby rotate the driven member. In its most preferred form, a second degree of safety is provided by having the maximum interface gap between the drive and driven members greater than the diameter of the balls to prevent any dislodged balls from jamming between the drive and driven members.

Fluid pressure operated, axially-engaging clutch

A dual-rotary union, rotational isolation adapter according to the teachings of the present invention is disclosed bridging between a rotary union in fluid communication with a source of fluid pressure and a rotation control apparatus portion rotatable with respect to a shaft. In the present invention, an adapter body is rotatably and removeably secured to the end of the shaft. In its most preferred form, the adapter body is rotatably mounted by a pin threadably received in the end of the shaft and rotatably mounted by a bearing received within a first cavity formed in the adapter body. In its most preferred form, the rotary union is received within a second cavity formed in the adapter body opposite the first cavity. Thus, the adapter body is rotatable with respect to and rotatably isolated from the source of fluid pressure by the rotary union. Additionally, the adapter body is simultaneously rotatable with respect to and rotatably isolated from the shaft by the bearing rotatably mounting the shaft securement pin. Fluid communication can then be provided between the rotational control apparatus portion and the rotary union for activating the rotational control apparatus portion. Thus, the body portion rotates with the rotational control apparatus portion and is rotatably independent from the shaft and the source of fluid pressure.

Dual-rotary union, rotational isolation adapter

A modular unit for use with a fluid engaged spring released and a spring engaged fluid released fan clutch including an outer hollow hub which terminates in a radially extending annular friction flange with an annular flange connected to the outer hollow hub for connection with a live shaft. Also provided is an inner central hub mounted internally of said outer hub by means of a pair of bearings. The inner central hub terminates in an enlarged central portion which in turn terminates in a radially disposed circular wall portion terminating in a series of right angular flanges. An annular piston is provided which is slideably mounted on the enlarged central portion of the inner hub. A ring is provided having a series of fan blades extending therefrom and connected to the circular wall. The piston has a friction facing carried thereby. A rotary air union is carried by the circular wall with the enlarged central portion of the inner hub having a conduit leading from the air union to one side of the piston for causing the piston to move axially on the hub. Spring means is carried by the unit for urging the piston axially on the inner central hub.

Modular unit for use with a fluid engaged spring released and a spring

A self-contained fan clutch including a housing in which is contained a rotatable drive disc driven by a source of power connected to the housing and the drive disc. Also mounted within the housing is an annular piston having an annular piston portion reciprocable within a cylinder member, the piston portion carrying a friction facing engageable with the driven drive disc when the piston is actuated within the cylinder. The piston divides the cylinder into a high pressure side and a low pressure side with the piston, piston portion and cylinder carried by the housing with the housing having a series of fan blades mounted thereon. The cylinder member mounts a reciprocal pump plunger actuated by a cam mounted on the driven drive disc for pressurizing the high pressure side of the cylinder which causes the friction facing of the piston portion to engage the drive disc and be rotated together with the housing and fans thereon. The pump plunger is actuated by a thermal sensor pill. Also included is apparatus for relieving pressure in the high pressure side of the cylinder and shunting it to the low pressure side of the cylinder thereby causing the piston to shift to the high pressure side by reason of springs carried by the housing and piston whereby the friction facing is relieved from the drive disc and the housing and fan thereon ceases to rotate.

Self-contained fan clutch

A combination friction ring and mount therefor for clutches, brakes and the like is shown according to the teachings of the present invention as including a circular friction disc member having a substantially flat face. The face has a shoulder thereon at the outer periphery thereof and a substantially flat ring friction lining secured upon the flat face of the circular member and the shoulder.

Combination friction ring and mount therefor for clutches, brakes and

A fluid disengaged and spring urged brake including a hub having a friction ring mounted thereon with a spring housing in which the hub is rotatably mounted. The spring housing has formed therein a multiplicity of cavities in each of which is mounted a coil spring. A friction facing mounting plate with friction facing thereon is secured to torque pins extended freely through holes slidably mounted on a piston secured to the spring housing. The friction facing mounting plate has a hole extending radially therethrough and the friction facing has grooves formed in the face thereof whereby air pressure supplied through from the hole of the mounting plate passes from the same through the grooves of the friction facing to thereby cool the friction interfaces of the engaging surfaces of the friction ring and the friction facing of the mounting plate. Further the friction ring has at least opening therethrough through which bolts securing friction facing in two pieces may be removed without dismantling any portion of the brake.

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Robbinsdale, MN, United States of America

James V Hanks