# Patent

## Title
Clutch system

## Abstract

A clutch system may include in certain embodiments a clutch body attached to a drive member such as a drive pulley, wherein the clutch body may be removed from the drive member without disassembling the clutch body. In various embodiments, the clutch body may include two clutch plates which enclose a spring-loaded pneumatic reciprocating assembly that in operation causes the plates to selectively separate and engage one another. In certain embodiments, the clutch body may be readily attached to a associated drive pulley in a single step by installation of a single set of fasteners.

## Background
CROSS-REFERENCE TO RELATED APPLICATION(S)
This application is a continuation-in-part of U.S. application Ser. No. 10/970,356 filed on Oct. 21, 2004 now U.S. Pat No. 7,104,382 and entitled “Clutch System,” the entire contents of which are incorporated herein by reference.


TECHNICAL FIELD
This document relates to a rotational control apparatus, and certain embodiments relate more particularly to a clutch apparatus.
BACKGROUND
Vehicle transmission systems, cooling systems, and braking systems often use clutches or like devices to selectively transmit rotational forces from a drive shaft to an output member. Conventional clutch devices include an opposing pair of engagement surfaces that can be compelled toward or away from one another using an electrical, mechanical, pneumatic, or hydraulic actuation system. In general, the actuation system causes some relative axial shifting within the clutch device. Such axial movement is used engage (or disengage) the opposing engagement surfaces, which rotationally interconnects (or rotationally disconnects) the drive shaft and the output member.
In clutch devices using pneumatic or hydraulic actuated systems, a piston may be acted upon by a set of springs to bias the piston toward one of the engaged or disengaged positions. Fluid pressure may act upon the piston, in a direction opposite to that of the spring force, to cause the piston portion to be axially shifted. Such axial movement is used engage (or disengage) the opposing engagement surfaces, thus selectively controlling the rotation between the drive shaft and the output member.
Clutch devices may require repair or replacement if the engagement surfaces have worn beyond their useful life or if a component is not properly functioning. For instance, seals and clutch engagement surfaces may wear over time and require replacement.
The design of the clutch device can have a significant effect on the time and cost of repair or replacement of component parts. If a clutch device has multiple pieces that must be disassembled before the clutch device can be removed from the drive shaft, the labor costs associated with the repair or replacement of the clutch device may increase. In addition, if a clutch device includes components that are spring biased, extra tooling may be required to clamp those components in place as clutch device is disassembled or removed.
The location and number of seals such as O-rings in the clutch device may also affect the time and cost associated with repairing or replacing clutch devices. If a seal fails and starts to leak, the time required to locate which particular seal is broken may increase if the clutch device has a larger number of seals. Furthermore, the location of the seals may affect the likelihood of contaminants entering the fluid space. If a seal is disposed between two surfaces that move both axially and rotationally relative to one another, the seal may be more susceptible to leakage.
The longevity of the clutch device, and thus the repair interval, may be increased by reducing wear factors such as vibration. Clutch designs built with more liberal tolerances and clutch designs that allow greater degrees of inter-part vibration may have a shorter useful life.
SUMMARY
A clutch system may include in certain embodiments a clutch body attached to a drive member such as a drive pulley, wherein the clutch body may be removed from the drive member without disassembling the clutch body. In various embodiments, the clutch body may include two clutch plates which enclose a spring-loaded pneumatic reciprocating assembly that in operation causes the plates to selectively separate and engage one another. In certain embodiments, the clutch body may be readily attached to a associated drive pulley in a single step by installation of a single set of fasteners.
In some embodiments, a rotation control apparatus may include a clutch member removably mounted to a drive pulley. The clutch member may have a hub portion and a piston portion. The hub portion may be selectively movable in a rotational direction relative to the drive pulley and substantially stationary in an axial direction relative to the drive pulley. The piston portion may be selectively movable in the axial direction relative to the hub portion and substantially stationary in the rotational direction relative to the hub portion. The clutch member may be removable from the drive pulley while the hub portion remains assembled with the piston portion.
In another embodiment, a rotational control apparatus includes a drive member rotatably mounted on a support shaft. The drive member may have a first engagement surface. A clutch member may be removably mounted to the drive member. The clutch member may comprise a piston portion assembled with a hub portion. The piston portion may be selectively movable in an axial direction relative to the hub portion and substantially stationary in a rotational direction relative. The piston portion may have a second engagement surface to selectively contact the first engagement surface. The clutch member may further include a channel in fluid communication with the piston portion, and a biasing member to urge the second engagement surface against the first engagement surface. The clutch member may be removable from the drive member while the hub portion remains assembled with the piston portion.
In some embodiments, a clutch member may include an engagement surface that at least partially extends in a nonradial direction. For example, the clutch member may include a frusto-conical engagement surface to selectively interface with clutch material. Particular embodiments may include a clutch device for removably mounting to a drive member. The clutch device may include a frusto-conical clutch ring, which may have an increasingly larger radius as the engagement surface extends away the driver member when the clutch device is mounted to the drive member.
These and other embodiments may be configured to provide one or more of the following advantages. First, the clutch member may be readily removed from the drive member upon removal of a single set of fasteners. Second, the clutch member may have a self-contained configuration that eliminates the need for additional clamps or tooling when removing the clutch member from the drive member. Third, the clutch member may have a reduced number of seals and leakage paths; thus reducing the number of seals along the periphery of the fluid-receiving chamber. Fourth, the seal member along the periphery of the fluid-receiving chamber may not rotate relative to an adjacent part, which may in turn improve seal quality and reduce the likelihood of contamination in the fluid system. Fifth, the clutch member may have a fluid-receiving chamber that is wholly within the removable clutch member, which may also reduce the likelihood of contamination in the fluid system. Sixth, a spline connection in the clutch member may reduce vibration between internal components of the clutch member. Seventh, the clutch member may use a single spring to urge the piston portion toward an engaged (or disengaged) position, which may simplify the assembly process during manufacture and repair. Some or all of these and other advantages may be provided by the clutch systems described herein.
The details of one or more embodiments of the invention are set forth in the accompanying drawings and the description below. Other features, objects, and advantages of the invention will be apparent from the description and drawings, and from the claims.



DESCRIPTION OF DRAWINGS
FIG. 1 is an exploded cross-sectional view of a rotational control apparatus in accordance with certain embodiments of the invention.
FIG. 2 is another exploded cross-sectional view of a rotational control apparatus of FIG. 1.
FIG. 3 is a cross-sectional side view of the rotational control apparatus FIG. 1.
FIG. 4 is another cross-sectional side view of the rotational control apparatus of FIG. 1.
FIG. 5 is an exploded cross-sectional view of a rotational control apparatus in accordance with certain embodiments of the invention.
FIG. 6 is a cross-sectional side view of the rotational control apparatus FIG. 5.
FIG. 7 is another cross-sectional side view of the rotational control apparatus of FIG. 5.



Like reference symbols in the various drawings indicate like elements.
DETAILED DESCRIPTION
A number of embodiments of the invention include a rotational control apparatus that provides simplified repair or replacement. A rotation control apparatus may include a clutch member that is removably mounted to a drive member. In some embodiments, the clutch member may be removed from the drive member without disassembly of the clutch member's component parts.
Referring to FIGS. 1-2, a drive member 100 is rotatably coupled to a support member 115 by one or more bearings 120. A nut or collar device 116 is secured to the support member 115 and is abutted to the bearing 120 so that the bearings 120 remain substantially fixed in the axial direction relative to the support member 115. The drive member 100 receives one or more drive inputs, such as belts, chains, gears or the like, to force the drive member 100 to rotate in a particular direction about an axis 105. In this embodiment, the support member 115 is a substantially stationary shaft, and the drive member 100 is illustrated as a drive pulley that includes an input portion 102. Rotational power from a motor or the like may be transmitted through one or more drive inputs (not shown in FIGS. 1-2) to the input portion 102, thus causing the drive pulley 100 to rotate about the central axis 105 of the support shaft 115.
A fluid supply input 150 extends into the support member 115 for connection to a fluid supply reservoir (not shown in FIGS. 1-2). A supply channel 152 extends from the fluid supply input 150 in a substantially axial direction along the central axis 105. In this embodiment, the supply channel 152 extends through a cylindrical outlet 160, which has a mating end 162 to mate with a face seal 260 of the clutch member 200. The outlet 160 may also include a spacer 164 that fits into a shoulder 117 of the support member 115, thereby aligning the outlet 160 with the central axis 105.
Still referring to FIGS. 1-2, the outlet 160 has an insert end 161 that is fit into a biasing member 163. The biasing member 163 of the outlet 160 is fit into an axial cavity 116 of the support member 115. The biasing member 163 may be a spring or block of elastic material that biases the mating end 162 in a substantially axial direction toward the face seal 260. As such, when the clutch member 200 is mounted to the drive member 100 (see, for example, FIG. 3), the mating end 162 is pressed against the face seal 260 to form a mechanical seal. Accordingly, the fluid may be transmitted from the fluid supply input 150 through the outlet 160 and the face seal 260 to the fluid-receiving chamber 264 of the clutch member 200. In some embodiments, the mating end 162, the face seal 260, or both may comprise metals, polymers, or composite materials that can substantially maintain the mechanical seal therebetween while the clutch member 200 is selectively rotated relative to the support member 115. In one example, the mating end 162 and the face seal 260 comprise a hardened, polished steel material. This configuration of the mechanical seal between the mating end 162 and the face seal 260 may eliminate the need for a cap member that is fit over the mating end 162 and extends to the inner circumference of the drive pulley 100 so as to seal the radial area inside the drive pulley 100 and retain a face seal 260.
The fluid transmitted to the fluid-receiving chamber 264 of the clutch member 200 may be any suitable liquid or gas, as described in more detail below. Such fluids may be received, for example, from a pneumatic air supply system or a hydraulic oil supply system.
Referring more closely to FIG. 1, the clutch member 200 is removably mounted to the drive pulley 100. A fluid channel 262 extending axially through the face seal 260 is substantially axially aligned with the central axis 105. In this embodiment, the clutch member 200 is removably mounted to the drive pulley 100 using bolts 110 that screw into threaded cavities 112 in the drive pulley 112. Alternatively, clamps may be used to removably couple the clutch member 200 to the drive member 100.
Such a configuration of the clutch member 200 may permit the clutch member 200 to be readily removed from the drive pulley 100. The clutch member 200 may be removed and/or replaced in a single operation by removing a single set of bolts 110. This configuration may obviate the need to disassemble parts of the clutch member 200 during a replacement or repair operation. Moreover, the clutch member 200 in certain configurations may lessens or eliminates the need for additional clamps or tooling when removing the clutch member 200 from the drive member 100, as described in more detail below. Accordingly, the time and costs associated with the repair or replacement of the clutch member 200 may be significantly reduced.
Referring again to FIGS. 1-2, the clutch member 200 includes a piston portion 220 that is movably assembled with a hub portion 240. The piston portion 220 is movable in an axial direction relative to the hub portion 240 and is substantially stationary in a rotation direction relative to the hub portion 240. In this embodiment, the motion of the piston portion 220 relative to the hub portion 240 is accomplished by way of a spline connection. The piston portion 220 includes a first spline member 224 that is substantially mated with a second spline member 244 of the hub portion 240. The splines 226 of the first spline member 224 are complimentary to the splines 246 of the second spline member 244 such that the spline members 224 and 244 are slidable relative to one another in an axial direction and are substantially stationary relative to one another in a rotational direction. In other embodiments, the motion of the piston portion 220 relative to the hub portion 240 may be accomplished using one or more bushings that permit relative axial movement and anti-rotation dowels that substantially prevent relative rotation between the piston portion 220 and the hub 240.
In the embodiment depicted in FIGS. 1-2, the piston portion 220 includes an output member 222, the first spline member 224, and a spring-engaging member 226. The spring-engaging member 226 has a radially extending surface 227 that abuts with a spring 280. The spring-engaging member 226 is fixedly coupled to the output member 222, for example, by bolts 228 screwed into threaded cavities 223 in the output member 223. The first spline member 224 is fixedly coupled to an output member 222, for example, by threads on an external surface 225 of the first spline member 224 that are mated into a threaded cavity 221 of the output member 222. Alternatively, the first spline member 224 may be fixedly coupled to an output member 222, for example, by bolts screwed into threaded cavities in the output member 222. The output member 222 includes studs 230 that are configured to receive an output device, such as fan blades (not shown in FIGS. 1-2). Accordingly, the clutch member 200 may engage the drive pulley 100 so that the output member 222 rotates with the drive pulley 200 to spin the fan blades. In such embodiments, the piston portion 220 of the clutch member 200 may have a dual function to selectively engage the drive pulley 100 and to act as the output for the rotational motion. The studs 230 may be mounted into cavities 231 in the output member 222. In the presently preferred embodiment, the cavities 231 do not extend completely through the output member 222, thereby obviating the need for additional seals between the studs 230 and the fluid-receiving chamber 264. In other embodiments, the studs 230 may be threaded bolts that are inserted through threaded apertures in the output member 222 and extend forward of the output member 222.
Still referring to FIGS. 1-2, the hub portion 240 includes a hub 242 and the second spline member 244. The second spline member 244 is fixedly coupled to the hub 242, for example, by threads on an external surface 245 of the second spline member 244 that are mated into a threaded cavity 243 of the hub 242. Alternatively, the second spline member 244 may be fixedly coupled to the hub 242, for example, by bolts screwed into threaded cavities in the hub 242. The hub 242 includes a cavity 248 configured to receive at least a portion of the face seal 260, and the fluid channel 262 extends axially along the central axis 105 through both the hub 242 and the second spline member 244. The face seal 260 may include threads on an external surface 261 that mate with the cavity 248 of the hub 242. In an alternative embodiment, the threaded cavity 243 may extend completely through the hub 242 such that the second spline member 244 mates with the face seal 260. In such an embodiment, the face seal 260 may mate with a cavity in the second spline member 244 similar to the cavity 248 in the hub 242.
At least one bearing 270 is disposed between the hub 242 and a fixed plate 275. The fixed plate 275 is mounted to the drive pulley 100 using the bolts 110 that are positioned through apertures 276 and screwed into cavities 112. As such, the fixed plate 275 is secured to the drive pulley 100 and rotates along with the drive pulley. The bearing 270 permits the hub portion 240 (including the hub 242) to rotate independently of the fixed plate 275 and the drive pulley 100. In this embodiment, the bearing 270 is disposed along an outer circumferential surface 241 of the hub 242. The bearing 270 may be secured to the hub 242 and the fixed plate 275 using any number of securing means, such as collar devices, locking nuts, locking rings, tongue and groove arrangements, or the like. In this embodiment, the bearing 270 is secured to the hub 242 using a locking nut 271 so that the bearing 270 remains substantially stationary relative to the hub 242 in the axial direction. The bearing 270 is secured to the fixed plate 275 using a locking ring 271 such that the bearing 270 remains substantially stationary relative to the fixed plate 275 in the axial direction. As such, the hub portion 240 may rotate independently of the fixed plate 275 and drive pulley 100, but the hub portion 240 remains substantially stationary in the axial direction relative to the fixed plate 275 and drive pulley 100.
Still referring to FIGS. 1-2, the hub 242 includes a spring-engaging surface 247 that abuts with the spring 280. In this embodiment, the spring 280 is a single, coiled spring that has an inner and outer diameter to fit securely within the spring-engaging member 226 of the piston portion 220. Using only a single spring may simplify assembly and disassembly of the clutch member 200 during manufacture or repair. Because only one spring must be placed in the spring-engaging member 226, less time is required to properly align the spring 280 during assembly. Alternatively, other embodiments may use a more complex arrangement having a greater number of smaller springs that are positioned adjacent one another within the spring-engaging member 226 of the piston portion 220.
When the clutch member 200 is assembled as shown in FIG. 1, the spring 280 is compressed between the spring-engaging surface 227 of the piston portion 220 and the spring engaging surface 247 of the hub portion 240. Such an arrangement urges the piston portion 220 in an axial direction toward the drive pulley 100. Thus, in this embodiment, the spring 280 biases the piston portion 220 such that an engagement surface 237 of the piston portion 220 is urged against a clutch material 277, which is mounted to the drive pulley 100 using the bolts 110. When the engagement surface 237 presses against the clutch material 277, the clutch member 200 engages the drive pulley 100, and the piston portion 220 and the hub portion 240 rotate with the drive pulley 100.
Still referring to FIGS. 1-2, the clutch member 200 may disengage the drive pulley 100 when fluid is introduced into the chamber 264 under sufficient pressure to axially shift the piston portion 220 relative to the hub portion 240. When the engagement surface 237 is shifted away from the clutch material 277 (see, for example, FIG. 4), the piston portion 220 and the hub portion 240 are no longer driven by the rotation of the drive pulley 100 and are free to independently rotate (or stop rotating) via the bearing connection 270. As previously described, fluid may enter the chamber 264 through the fluid channel 262. In this embodiment, the fluid-receiving chamber 264 is at least partially defined by the space between the output member 222 and the hub 242. The fluid may pass through small gaps in the spline connection between the first spline member 224 and the second spline member 244. When a predetermined amount of fluid pressure has built up in the chamber 264, the output member 222 is forced in an axial forward direction away from the drive pulley 100, thus overcoming the bias of the spring 280 to urge the piston portion 220 toward the drive pulley 100.
Still referring to FIGS. 1-2, the fluid-receiving chamber 264 is disposed internally in the clutch member 200. In this embodiment, the fluid in the chamber 264 may have only one possible leak path, which is along the circumferential surface 249 of the hub 242. A seal 290 is disposed along the periphery of the leak path between the circumferential surface 249 of the hub 242 and the output member 220. The seal 290 is positioned as such to prevent fluid leakage through the leak path. Thus, a fluid leak may be quickly detected and repaired by checking the seal 290 at the circumferential surface 249 and by checking the mechanical seal at the face seal 260. By reducing the number of seals in the clutch member design, the time and cost associated with detecting which seal is faulty may be significantly reduced.
In this embodiment, the seal 290 for the fluid-receiving chamber 264 is internal to the clutch member 220 and is disposed between two surfaces that do not rotate relative to one another about the central axis 105. As previously described, the piston portion 220 may shift in the axial direction relative to the hub portion 240, so the seal may endure a sliding motion between the circumferential surface 249 and the output member 222. The piston portion 220 remains substantially stationary relative to the hub portion 240 in the rotational direction, so the seal 290 does not endure a rotational motion. When the seal 290 is internal to the clutch member 200 and is limited to such minimal sliding motion, the possibility of contaminants entering the chamber 264 through the seal 290 may be significantly reduced. Such a reduction is contamination may increase the longevity the clutch member 200 and may reduce the need for repair or replacement.
Referring to FIGS. 1-2, a wiper seal 291 may also be disposed between the circumferential surface 249 of the hub portion 240 and the output member 222 of the piston portion 220. In this embodiment, the wiper 291 may slide in an axial direction when the piston portion 220 shifts relative to the hub portion 240. The wiper 291 is positioned against the circumferential surface 249 so as to prevent or limit any contaminants that may pass into the fluid-receiving chamber. The wiper 291, the seal 290, or both may comprise a material that is suitable to endure the sliding motion while limiting the flow of fluid or contaminants. Such suitable materials may include polymers, rubber materials, composite materials, or the like. Depending on the manufacturing tolerances of the piston portion 220 and the hub portion 240, a guide band (not shown in FIGS. 1-2) may be disposed between the circumferential surface 249 and the output member 222 to prevent excess metal-on-metal contact between the circumferential surface 249 and the output member 222. If such a guide band is implemented, the guide band is preferably disposed between the seal 290 and the wiper 291.
Referring more specifically now to FIG. 1, the clutch member 200 may have a self-contained construction such that the components of clutch member 200 (e.g., the piston portion 220, the hub portion 240, the spring 280, and so forth) remain in an assembled state even after the clutch member is removed from the drive pulley 100. In the embodiment shown in FIG. 1, the clutch member 200 may be removed from the drive pulley 100 by removing the bolts 110 from the mounting cavities 112. Removing these bolts 110, however, does not permit the internal spring to move the components of the clutch member 200 apart from another and thereby cause disassembly of the clutch member 200 (e.g., the spring 280 is not be free to unexpectedly expand and separate the components when a worker attempts to remove the clutch member 200 from the drive pulley 100). The locking nut 272, locking ring 271, and other such devices may be subsequently removed to disassemble the clutch member 200 at the appropriate time. Accordingly, the clutch member 200 may be removed from the drive pulley 100 without the use of clamps or extra tooling to retain the clutch member 200 in its assembled position.
In operation, the clutch member 200 may selectively engage the drive member 100 so that the rotation of the output member 222 is controlled. As previously described, the depicted embodiment of the clutch member 200 may disengage the drive pulley 100 when fluid is introduced into the chamber 264 under sufficient pressure to axially shift the piston portion 220 relative to the hub portion 240. When the engagement surface 237 is shifted away from the clutch material 277, the piston portion 220 and the hub portion 240 are no longer driven by the rotation of the drive pulley 100 and are free to independently rotate (or stop rotating) via the bearing connection 270.
Referring now to FIG. 3, the clutch member 200 is mounted to the drive pulley 100 and the piston portion 220 is shown in an engaged position. In this embodiment, the spring 280 is disposed between the hub portion 240 and the piston portion 220 such that the spring 280 urges the piston portion 220 in a rearward axial direction toward the drive pulley 100. The engagement surface 237 of the piston portion 220 is pressed against the clutch material 277, which is mounted to the drive pulley 100. The engagement surface 237 is urged against the clutch material 277 with sufficient force so that the piston portion 220 rotates along with the clutch material 277, which is mounted to the drive pulley 100. As such, the output member 222 of the piston portion 220 rotates substantially synchronously with the rotation of the drive pulley 100 about the central axis 105. When the piston portion 220 is in the engaged position, the output device (such as a fan) that is mounted to the studs 230 of the output member 222 also rotates with the drive pulley 100. Although the hub portion 240 is not directly engaged with the drive pulley 100 or the clutch material 277, the hub portion 240 rotates with the piston portion 220 due to the spline connection between first and second spline members 224 and 244. Such a configuration limits the wear on the seal 290 because the seal 290 does not endure rotational motion between the hub 242 and the output member 222.
Referring now to FIG. 4, the piston portion 220 is shifted forward in the axial direction away from the drive pulley 100 such that the piston is in a disengaged position. In this embodiment, the engagement surface 237 of the piston portion 220 is spaced from the clutch material 277 by an offset 300. This offset 300 causes the piston portion 220 to disengage with the clutch material 277 so that the rotational motion from the drive pulley 100 is not transferred to the output member 222. When the piston portion 220 is in the disengaged position, the piston portion 220 and hub portion 240 are free to rotate independently from the drive pulley 100 due to the bearing connection 270. Accordingly, the piston portion 220 and the hub portion 240 may stop rotating even though the drive pulley 100 continues to rotate.
Referring to FIGS. 3-4, the offset 300 of the piston portion 220 occurs when a fluid under sufficient pressure is received in the chamber 264. If force from the fluid pressure in the chamber 264 is sufficient to overcome the force of the spring 280, the output member 220 (and the entire piston portion 220) is shifted forward in the axial direction. In some embodiments, the fluid pressure that is required to overcome the spring force may be approximately predetermined from the spring constant, the desired offset 300, the dimensions of the chamber 264, and other such factors. As previously described, the fluid supply input 150 receives the fluid from the reservoir (not shown in FIGS. 3-4). The fluid passes through the fluid supply channel 152, through the outlet 160 and the face seal 260, through the fluid channel 262, and into the chamber 264. The mechanical seal at the face seal 260 assures that the fluid properly reaches the chamber 264, and when the fluid is in the chamber 264, the seal 290 prevents the fluid from passing through the potential leak path along the circumferential surface 249 (FIG. 2).
In this embodiment of the clutch member 200 depicted in FIGS. 3-4, the piston portion 220 serves as both the portion that engages the drive pulley 100 (via the clutch material 277) and the portion that receives an output device (such as a fan). The output device mounted to the studs 230 of the piston portion 220 may also be shifted in the axial direction as the piston portion 220 is shifted, but the offset 300 in the axial direction may be relatively small such that this shifting motion has little or no impact on the output device. Similarly, the offset 300 in the axial direction may be relatively small such that the shifting motion of the output member 222 relative to the hub 242 has little or no impact on the longevity and performance of the seal 190 and the wiper 191. It should be understood that the displacement between the clutch material 277 and the engagement surface 237 may change slightly as the clutch material 277 is worn away through normal use.
In another embodiment of the invention, the drive member 100 may have a configuration other than a drive pulley shown in FIGS. 1-4. For example, the drive member 100 may be a shaft or gear that is powered by a motor. In such embodiments, the clutch member 200 may have a mounting configuration to removably attach to the shaft or gear or may have an adapter member connected therebetween.
In other embodiments, the output member 222 of the clutch member 200 may be configured to receive an output device other than fan blades. For example, the output member 222 may be configured to connect with other components that are to be selectively rotated, such as output shafts, gears, brake systems, and the like.
In yet another embodiment, the spring 280 that biases the piston portion 220 in an axial direction is not limited to a single, coiled spring shown in FIGS. 1-4. Rather, the spring 280 can be any biasing member that can urge the piston portion 220 in the axial direction. A suitable biasing member may comprise one or more coil springs, leaf springs, gas springs, solid materials having appropriate elasticity properties, or the like.
Furthermore, some embodiments of the invention may include a clutch member configuration such that spring 280 urges the piston portion 220 to disengaged position (where the engagement surface 237 is offset from the clutch material 277). In such embodiments, the chamber 264 may be configured such that fluid pressure therein causes the piston portion 220 to shift toward engaged position (where the engagement surface 237 is pressed against the clutch material 277).
In other embodiments, the clutch material 277 may be integral with the fixed plate 275 or the drive member 100. In these embodiments, the engagement surface 237 of the piston portion 220 would engage with an opposing surface on the fixed plate 275 of the drive member 100.
In another embodiment, the clutch material may be mounted to the piston portion 220 such that the clutch material selectively engages with an opposing surface (e.g., the clutch material 277, the fixed plate 275 or the drive member 100). In such an embodiment, an engagement surface on the clutch material would contact the opposing surface.
Referring to FIGS. 5-7, some embodiments of a clutch member 600 may include an engagement surface 637 that at least partially extends in a nonradial direction. For example, a clutch member 600 may include a frusto-conical interface between the clutch material and the engagement surface. In this embodiment, a frusto-conical clutch ring 677 may selectively engage a frusto-conical surface 637. The frusto-conical engagement surface 637 has a first radius 639 and a second radius 641, with the first radius 639 being axially closer to drive member 500. In this embodiment, the first radius 639 is smaller than the second radius 641. As such, the frusto-conical clutch ring 677 may have an increasingly larger radius as the engagement surface extends away from the drive member 500 when the clutch member 600 is mounted to the drive member 500.
Similar to some previously described embodiments, the drive member 500 can be rotatably coupled to a support member 515 by one or more bearings 520. The drive member 500 receives one or more drive inputs, such as belts, chains, gears or the like, to force the drive member 500 to rotate in a particular direction about an axis 505. In this embodiment, the support member 515 is a substantially stationary shaft, and the drive member 500 is illustrated as a drive pulley that includes an input portion 502.
A fluid supply input 550 extends into the support member 515 for connection to a fluid supply reservoir (not shown in FIGS. 5-7). A supply channel 552 may extend from the fluid supply input 550 in a substantially axial direction along the central axis 505. In this embodiment, the supply channel 552 mates with a face seal 660 of the clutch member 600. When the clutch member 600 is mounted to the drive member 500 (see, for example, FIG. 6), the supply channel 552 is pressed against the face seal 660 to form a mechanical seal. Accordingly, the fluid may be transmitted from the fluid supply input 550, through a fluid channel 662, and to the fluid-receiving chamber 664 of the clutch member 600.
Referring to FIG. 5, the clutch member 600 may be removably mounted to the drive member 500. In this embodiment, the clutch member 600 is removably mounted to the drive member 500 using bolts 510 that screw into threaded cavities 512 in the drive member 500. In another embodiment, clamps may be used to removably couple the clutch member 600 to the drive member 500.
Such a configuration of the clutch member 600 may permit the clutch member 600 to be readily removed from the drive member 500. The clutch member 600 may be removed and/or replaced in a single operation by removing a single set of bolts 510. Similar to some previously described embodiments, this configuration may obviate the need to disassemble parts of the clutch member 600 during a replacement or repair operation.
Still referring to FIG. 5, the clutch member 600 includes a piston portion 620 that is movably assembled with a hub portion 640. The piston portion 620 is movable in an axial direction relative to the hub portion 640 and is substantially stationary in a rotation direction relative to the hub portion 640. Similar to some previously described embodiments, the motion of the piston portion 620 relative to the hub portion 640 may be accomplished by way of a spline connection. The piston portion 620 includes a first spline member 624 that may be substantially mated with a second spline member 644 of the hub portion 640.
The piston portion 620 includes studs 630 that are configured to receive an output device, such as fan blades (not shown in FIGS. 5-7). Accordingly, the clutch member 600 may engage the drive member 500 so that the piston portion 620 rotates with the drive member 500 to spin the fan blades. In such embodiments, the piston portion 620 of the clutch member 600 may have a dual function to selectively engage the drive member 500 and to act as the output for the rotational motion.
In this embodiment, the hub portion 640 includes a hub 642 and the second spline member 644. The hub 642 includes a cavity 648 configured to receive at least a portion of the face seal 660, and the fluid channel 662 extends axially along the central axis 505 through both the hub 642 and the second spline member 644. Similar to some previously described embodiments, a seal 690 may be disposed along the periphery of the leak path between hub 642 and the output member 620. The seal 690 is positioned as such to prevent fluid leakage through the leak path. Thus, a fluid leak may be quickly detected and repaired by checking the seal 690 at the circumferential surface and by checking the mechanical seal at the face seal 660. By reducing the number of seals in the clutch member design, the time and cost associated with detecting which seal is faulty may be significantly reduced. Similar to some previously described embodiments, the clutch member 600 may optionally include a wiper seal 691. The wiper seal 691 may prevent migration of contaminants toward the seal 690 that actually borders the fluid receiving chamber 664.
At least one bearing 670 may be disposed between the hub 642 and a fixed plate 675. The fixed plate 675 may be removably mounted to the drive member 500 using the bolts 510 that are positioned through apertures 676 and screwed into cavities 512. As such, the fixed plate 675 can be secured to the drive member 500 and rotates along with the drive member 500. The bearing 670 permits the hub 642 to rotate independently of the fixed plate 675 and independently of the drive member 500. In this embodiment, the bearing 670 may be secured to the hub 642 using a locking nut 672 so that the bearing 670 remains substantially stationary relative to the hub 642 in the axial direction. The bearing 670 may be secured to the fixed plate 675 using a locking ring 671 such that the bearing 670 remains substantially stationary relative to the fixed plate 675 in the axial direction. As such, the hub 642 may rotate independently of the fixed plate 675 and independently of the drive member 500, but the hub 642 remains substantially stationary in the axial direction relative to the fixed plate 675 and drive member 500.
Still referring to FIG. 5, the hub 642 includes a spring-engaging surface 647 that abuts with a biasing member, such as a spring 680. In this embodiment, the spring 680 is a single, coiled spring that has an inner and outer diameter to fit securely within the spring-engaging member 626 of the piston portion 620.
When the clutch member 600 is assembled as shown in FIG. 5, the spring 680 may be compressed between the spring-engaging surface 627 of the piston portion 620 and the spring engaging surface 647 of the hub 642. Such an arrangement urges the piston portion 620 in an axial direction toward the drive member 500. Thus, in this embodiment, the spring 680 biases the piston portion 620 such that the frusto-conical clutch ring 677 (mounted to the piston portion 620 in this embodiment) is urged against the frusto-conical engagement surface 637 of the fixed plate 675, which is mounted to the drive member 500 using the bolts 510. When the frusto-conical clutch ring 677 of the piston portion 620 presses against the frusto-conical engagement surface 637 of the fixed plate 675, the piston portion 620 engages the fixed plate 675, and the piston portion 620 rotates with the drive member 500. The clutch ring 677 may comprises a metallic, ceramic or other material that is capable of providing frictional engagement and is capable of dissipating heat generated at the frictional interface. For example, some embodiments of the clutch ring 677 may comprise a material having a static coefficient or friction in the range of approximately 0.2 to approximately 0.6 and, in particular embodiments, may comprises a material having a static coefficient of friction in the range of approximately 0.4 to approximately 0.5.
Still referring to FIG. 5, the piston portion 620 may disengage the hub 642 when fluid is introduced into the chamber 664 under sufficient pressure to axially shift the piston portion 620 relative to the hub portion 640. Such an axial shift of the piston portion 620 may cause the frusto-conical clutch ring 677 to disengage the opposing engagement surface (e.g., the engagement surface 637 of the fixed plate 675 in this embodiment). In such circumstances, the piston portion 620 may not be driven by the rotation of the drive member 500 so that the piston portion 620 is free to independently rotate (or stop rotating) due to the bearing connection 670.
In this embodiment, the fluid-receiving chamber 664 is at least partially defined by the space between the output member 622 and the hub 642. In some embodiments, the fluid may pass through small gaps in the spline connection between the first spline member 624 and the second spline member 644. When a predetermined amount of fluid pressure has built up in the chamber 664, the output member 622 is forced in an axial forward direction away from the hub 642, thus overcoming the bias of the spring 680 to urge the piston portion 620 in the axial forward direction.
Similar to some previously described embodiments, the clutch member 600 may have a self-contained construction such that the components of clutch member 600 (e.g., the piston portion 620, the hub portion 640, the spring 680, the frusto-conical clutch ring 677, and so forth) remain in an assembled state even after the clutch member 600 is removed from the drive member 500. In the embodiment shown in FIG. 5, the clutch member 600 may be removed from the drive member 500 by removing the bolts 510 from the mounting cavities 512.
Referring now to FIGS. 6-7, the clutch member 600 may be operated to selectively engage the drive member 500 so that the rotation of the output member 622 is controlled. As previously described, the depicted embodiment of the clutch member 600 may disengage the drive member 500 when fluid is introduced into the chamber 664 under sufficient pressure to axially shift the piston portion 620 relative to the hub portion 640. When the frusto-conical clutch ring 677 is shifted away from the frusto-conical engagement surface 637, the piston portion 620 is no longer driven by the rotation of the drive member 500 (and the fixed plate 675) and is thereby free to independently rotate (or stop rotating) via the bearing connection 670.
As shown in FIG. 6, the clutch member 600 is mounted to the drive member 500, and the piston portion 620 is in an engaged position. In this embodiment, the spring 680 is disposed between the hub portion 640 and the piston portion 620 such that the spring 680 urges the piston portion 620 in a rearward axial direction (toward the drive member 500). The frusto-conical clutch ring 677 of the piston portion 620 is pressed against the frusto-conical engagement surface 637 of the fixed plate 675, which is mounted to the drive member 500. The frusto-conical clutch ring 677 is urged against frusto-conical engagement surface 637 with sufficient force so that the piston portion 620 rotates along with the fixed plate 675, which is mounted to the drive member 500. As such, the output member 622 of the piston portion 620 rotates substantially synchronously with the rotation of the drive member 500 about the central axis 505. When the piston portion 620 is in the engaged position, the output device (such as a fan or fan blades) that is mounted to the studs 630 of the output member 622 also rotates with the drive member 500. Although the hub 642 is not directly engaged with the drive member 500 or the frusto-conical engagement surface 637 of the fixed plate 675, the hub 642 rotates with the piston portion 620 due to the spline connection between the first and second spline members 624 and 644. Such a configuration may limit the wear on the seal 690 because the seal 690 does not endure rotational motion between the hub 642 and the output member 622.
Referring now to FIG. 7, the piston portion 620 may be shifted forward in the axial direction away from the drive member 500 such that the piston portion 620 is in a disengaged position. In this embodiment, the frusto-conical clutch ring 677 may be mounted to the piston portion 620 so it is axially shifted away from the frusto-conical engagement surface 637 by an offset 700. This offset 700 causes the piston portion 620 to disengage with the fixed plate 675 so that the rotational motion from the drive member 500 is not transferred to the output member 622. When the piston portion 620 is in the disengaged position, the piston portion 620 and hub portion 640 are free to rotate independently from the drive member 500 due to the bearing connection 670. Accordingly, the piston portion 620 and the hub 642 may stop rotating even though the drive member 500 and the fixed plate 675 continue to rotate. It should be understood that, in other embodiments, the clutch ring 677 may be mounted to the fixed plate 675, in which case the clutch ring 677 may selectively engage a frusto-conical surface 628 of the piston portion 620. In such circumstances, the piston portion 620 may be axially shifted to cause an offset between the clutch ring 677 and the frusto-conical surface 628.
Referring to FIGS. 6-7, the offset 700 of the piston portion 620 may occur when a fluid under sufficient pressure is received in the chamber 664. If force from the fluid pressure in the chamber 664 is sufficient to overcome the force of the spring 680, the output member 622 (and, in this embodiment, the entire piston portion 620) is shifted forward in the axial direction. In some embodiments, the fluid pressure that is required to overcome the spring force may be approximately predetermined from the spring constant, the desired offset 700, the dimensions of the chamber 664, and other such factors. As previously described, the fluid supply input 550 may receive the fluid, such as air, from the reservoir (not shown in FIGS. 6-7). The fluid passes through the fluid supply channel 552, through the fluid channel 662, and into the chamber 664. The mechanical seal at the face seal 660 assures that the fluid properly reaches the chamber 664, and when the fluid is in the chamber 664, the seal 690 may prevent the fluid from passing through a potential leak path along the circumferential surface 649 of the hub 642.
Some embodiments of a clutch member 600 having a frusto-conical engagement surface 637, such as those embodiments described in connection with FIGS. 5-7, may provide substantial torque transfer capabilities between the drive member 500 and the output device. For example, some embodiments of the clutch member 600 may provide torque ratings of approximately 2700 in-lbs, 2800 in-lbs, 2900 in-lbs, 3000 in-lbs, or more, and particular embodiments may provide torque ratings in the range of approximately 3000 in-lbs to approximately 5000 in-lbs. As described in more detail below, the coefficient of friction of the clutch ring 577, the conical angle of the clutch ring 677, the force of the spring 680, and other factors affect the torque rating of the clutch member 600.
These substantial torque transfer capabilities may be caused by a number of factors. For example, the shape and orientation of the frusto-conical engagement surface 637 and the frusto-conical clutch ring 677 may provide the clutch member 600 with a conical wedging action. This conical wedging action may improve the engagement friction, thereby providing an increase in the torque transfer capabilities.
In another example, the shape and orientation of the frusto-conical engagement surface 637 and the frusto-conical clutch ring 677 may provide the clutch member 600 with a reduced rotational moment of inertia. Because some embodiments of the frusto-conical clutch ring 677 do not necessarily extend as far in an outward radial direction, the piston portion 620 may have less radial mass (in the form of metallic portions or other components extending generally in an outward direction away from the rotational axis). As such, the overall rotational moment of inertia of the piston portion 620 may be reduced, which may increase the torque transfer capabilities of the clutch member 600.
Torque capability testing may be conducted on clutch members 600 to determine the torque ratings. For example, a torque capability test method may include mounting the clutch member 600 to a drive member 500, as shown, for example, in FIG. 6. The torque capability testing method may also include securing the drive member 500 in a fixed position (e.g., in a vice or a similar device), which in turn secures the position of the engagement surface 637 (e.g., disposed on the fixed plate 675 in the depicted embodiments). In this example, a torque measuring device (e.g., a torque meter or the like) may be secured to the output member 622. In accordance with this implementation of the torque capability test method, the clutch member may be in an engaged condition so that the frusto-conical clutch ring 677 is in frictional contact with the engagement surface 637. The torque measuring device may be used to measure a torque applied to the output member 622 relative to the drive member 500 (e.g., applying a force in an attempt to rotate the output member 622) and may be monitored to determine the torque level required to cause slippage between the output member 622 and the drive member 500. This implementation of the torque capability test method may be used to determine the torque rating of the clutch member 600 (e.g., the level of torque required to cause slippage between the output member 622 and the drive member 500 when the clutch member 600 was in an engaged condition).
Certain factors of the clutch member's configuration may affect the torque transfer capabilities and the torque rating of the clutch member 600. For example, the conical angle of the clutch ring 677 (refer, for example, to angle A in FIG. 7) may be selected to optimize the torque rating of the clutch member 600. In some embodiments, the conical angle A may be approximately 10 degrees to approximately 60 degrees, approximately 15 degrees to approximately 45 degrees, or approximately 20 to approximately 40 degrees. In the embodiment depicted in FIGS. 5-7, the conical angle A is approximately 30 degrees.
In another example of a factor that can affect the torque transfer capabilities, the material of the clutch ring 677 and/or the engagement surface 637 may be selected to provide a particular coefficient of friction. In some embodiments, the clutch member 600 may include clutch ring material having a static coefficient of friction in the range of approximately 0.3 to approximately 0.6, approximately 0.35 to approximately 0.55, or approximately 0.4 to approximately 0.55. Suitable materials for the clutch ring 677 may be provided, for example, by Trimat Ltd. of Brierley Hill, England or by Scan Pac Mfg., Inc. of Menomonee Falls, Wis.
In a further example of a factor that can affect the torque transfer capabilities, the force of the spring 680 (or the force from the fluid pressure in the chamber 664 used to overcome the spring 680) may be selected to provide a particular compression force between the clutch ring 677 and the engagement surface 637. In some embodiments, the spring 680 may provide a force (to bias the clutch ring 677 and the engagement surface 637 toward one another) of approximately 700 lbs, 800 lbs, 900 lbs, 1000 lbs, 1100 lbs, 1200 lbs, 1300 lbs, 1400 lbs, 1500 lbs, or greater. The displacement of the spring 680 may be different depending upon the wear of the clutch ring 677, so in some embodiments, the force from the spring 680 may be in the range of approximately 800 lbs to approximately 1400 lbs. For example, the spring 680 may provide a force of approximately 1100 lbs to approximately 1400 lbs when a substantially unworn clutch ring 677 is pressed against the engagement surface 637. In the embodiment depicted in FIGS. 5-7, the spring 680 may provide a force of approximately 1250 lbs when a substantially unworn clutch ring 677 is pressed against the engagement surface 637. When the clutch ring 677 becomes substantially worn after repeated use, the displacement of the spring 680 may be different so that the compression force provide from the spring is lower. For example, the spring 680 may provide a force of approximately 800 lbs to approximately 1100 lbs when a substantially worn clutch ring 677 is pressed against the engagement surface 637. In the embodiment depicted in FIGS. 5-7, the spring 680 may provide a force of approximately 1000 lbs when a substantially worn clutch ring 677 is pressed against the engagement surface 637.
Accordingly, by making appropriate selections from (i) the conical angle A, (ii) the coefficient of friction at the interface between the clutch ring 677 and the engagement surface 637, (iii) the force from the spring 680, and (iv) other such factors, the clutch member 600 may have a torque rating of approximately 2700 in-lbs, 2800 in-lbs, 2900 in-lbs, 3000 in-lbs, or more, and particular embodiments may provide torque ratings in the range of approximately 3000 in-lbs to approximately 5000 in-lbs-including torque ratings in the ranges of approximately 3200 in-lbs to approximately 4000 in-lbs and approximately 4000 in-lbs to approximately 5000 in-lbs. In some embodiments of a clutch member 600 having a conical angle A of approximately 30 degrees, having a clutch ring 677 having a static coefficient of friction of approximately 0.4, and having a spring force of approximately 1250 lbs when the clutch ring 677 is substantially unworn, the clutch member 600 may have torque ratings in the range of approximately 3200 in-lbs to approximately 4000 in-lbs. For example, a clutch member 600 that had a clutch ring 677 comprising Trimat MR8728 material (supplied by Trimat Ltd.) with a static coefficient of friction of approximately 0.4, had a conical angle A of approximately 30 degrees, and had a spring force of approximately 1250 lbs (when the clutch ring 677 was substantially unworn) provided torque ratings of approximately 3540 in-lbs, 3648 in-lbs, 3780 in-lbs, 3444 in-lbs, 3576 in-lbs, and 3636 in-lbs.
In other embodiments, a clutch member 600 having a clutch ring material with a greater static coefficient of friction (e.g., comprising Aramid materials supplied by either Trimat Ltd. or Scan Pac Mfg., Inc., Trimat TF100 material, or the like) may provide greater torque ratings. For example, some embodiments of a clutch member 600 may have a clutch ring 677 with a static coefficient of friction of approximately 0.5 (e.g., comprising Trimat TF100 material), may have a conical angle A of approximately 30 degrees, and may have a spring force of approximately 1250 lbs when the clutch ring 677 is substantially unworn, and such a clutch member 600 may have torque ratings in the range of approximately 4000 in-lbs to approximately 5000 in-lbs. Because a greater coefficient of friction may increase the frictional interface between the clutch ring 677 and the engagement surface 637, some embodiments of the clutch member 600 may have a torque rating greater than 5000 in-lbs.
Thus, some embodiments of the clutch member 600 may provide torque ratings of approximately 2700 in-lbs, 2800 in-lbs, 2900 in-lbs, 3000 in-lbs, or more. Particular embodiments may provide torque ratings in the range of approximately 3000 in-lbs to approximately 5000 in-lbs—including torque ratings in the ranges of approximately 3200 in-lbs to approximately 4000 in-lbs and approximately 4000 in-lbs to approximately 5000 in-lbs.
It should be understood that the drive member 500 may have a configuration other than a drive pulley shown in FIGS. 5-7. For example, the drive member 500 may be a shaft or gear that is powered by a motor. In such embodiments, the clutch member 600 may have a mounting configuration to removably attach to the shaft or gear or may have an adapter member connected therebetween.
In other embodiments, the output member 622 of the clutch member 600 may be configured to receive an output device other than fan blades. For example, the output member 622 may be configured to connect with other components that are to be selectively rotated, such as output shafts, gears, brake systems, and the like.
In yet another embodiment, the spring 680 that biases the piston portion 620 in an axial direction is not limited to a single, coiled spring shown in FIGS. 5-7. Rather, the spring 680 can be any biasing member that can urge the piston portion 620 in the axial direction. A suitable biasing member may comprise one or more coil springs, leaf springs, gas springs, solid materials having appropriate elasticity properties, or the like.
Furthermore, some embodiments may include a clutch member configuration such that the spring 680 urges the piston portion 620 into the disengaged position (where the frusto-conical engagement surface 637 is offset from the frusto-conical clutch material 677). In such embodiments, the chamber 664 may be configured such that fluid pressure therein causes the piston portion 620 to shift toward engaged position (where the frusto-conical engagement surface 637 is pressed against the clutch material 677).
A number of embodiments of the invention have been described. Nevertheless, it will be understood that various modifications may be made without departing from the spirit and scope of the invention. Accordingly, other embodiments are within the scope of the following claims.

## Claims

1. A fan clutch device for removably mounting to a drive member, the fan clutch device comprising:
an output member to selectively rotate with a drive member when the fan clutch device is mounted to the drive member, the output member having one or more mounting members to receive one or more fan blades, wherein the output member comprises: a hub portion being selectively movable in a rotational direction relative to a drive member and substantially stationary in an axial direction relative to the drive member, and a piston portion being selectively movable in the axial direction relative to the drive member, the piston portion being adjustable between a first operative position and a second operative position; and
a clutch ring arranged radially outward of the output member having the one or more mounting members to receive the one or more fan blades, the clutch ring including an engagement surface to selectively engage an opposing surface so that, when the clutch ring engages the opposing surface and the fan clutch device is mounted to the drive member, the output member rotates with the drive member,
wherein, when the clutch ring engages the opposing surface and the fan clutch device is mounted to the drive member, the torque required to cause slippage between the output member and the drive member is about 3000 in-lbs or greater.

2. The fan clutch device of claim 1, wherein the torque required to cause slippage between the output member and the drive member is in the range of about 3000 in-lbs to about 5000 in-lbs.

3. The fan clutch device of claim 2, wherein the torque required to cause slippage between the output member and the drive member is in the range of about 3200 in-lbs to about 4000 in-lbs.

4. The fan clutch device of claim 2, wherein the torque required to cause slippage between the output member and the drive member is in the range of about 4000 in-lbs to about 5000 in-lbs.

5. The fan clutch device of claim 1, wherein the clutch ring is a frusto-conical clutch ring.

6. The fan clutch device of claim 5, wherein the engagement surface of the frusto-conical clutch ring has an increasingly larger radius as the engagement surface extends away from the drive member when the fan clutch device is mounted to the drive member.

7. The fan clutch device of claim 5, wherein the frusto-conical clutch ring has a conical angle of about 10 degrees to about 60 degrees.

8. The fan clutch device of claim 7, wherein the frusto-conical clutch ring has a conical angle of about 20 to about 40 degrees.

9. The fan clutch device of claim 1, wherein the engagement surface of the clutch ring has a static coefficient of friction of about 0.3 to about 0.6 .

10. The fan clutch device of claim 9, wherein the static coefficient of friction of about 0.4 to about 0.55 .

11. The fan clutch device of claim 1, further comprising a biasing member to urge the engagement surface of the clutch ring toward the opposing surface, the biasing member providing a spring force of about 1100 lbs to about 1400 lbs when the clutch ring is substantially unworn and engages the opposing surface.

12. The fan clutch device of claim 1, wherein the piston portion includes the one or more mounting members to receive the one or more fan blades, the clutch ring being arranged radially outward of the piston portion.

13. A fan clutch device that is removably mountable to a drive member, the fan clutch device comprising:
an input member mountable to the drive member so as to rotate with the drive member;
an output member to selectively engage with the input member when the fan clutch device is mounted to the drive member, the output member having one or more mounting members to receive one or more fan blade devices, wherein the output member comprises:
a hub portion selectively movable in a rotational direction relative to the input member and substantially stationary in an axial direction relative to the input member, and
a piston portion slidably coupled to the hub portion, the piston portion being selectively movable in the axial direction relative to the input member; and

a frusto-conical clutch ring arranged radially outward of the output member and radially inward of the input member, the frusto-conical clutch ring including an engagement surface that is at least partially defined by one of an inner frusto-conical face and an outer frusto-conical face, wherein each of the inner frusto-conical face and the outer frusto-conical face has an increasingly larger radius as the engagement surface extends away from the drive member when the fan clutch device is mounted to the drive member.

14. The fan clutch device of claim 13, wherein the piston portion comprises a frusto-conical surface to contact the inner frusto-conical face of the clutch ring, the frusto-conical clutch ring being arranged radially outward of the piston portion.

15. The fan clutch device of claim 14, wherein the input member comprises a frusto-conical surface to contact the outer frusto-conical face of the clutch ring.

16. The fan clutch device of claim 15, wherein the clutch ring is mounted to the frusto-conical surface of the piston portion and the clutch ring selectively engages the frusto-conical surface of the input member as piston portion is selectively moved in the axial direction.

17. The fan clutch device of claim 13, wherein the inner frusto-conical face of the clutch ring extends generally parallel to the outer frusto-conical face.

18. The fan clutch device of claim 13, further comprising a biasing member disposed between the hub portion and the piston portion so as to urge the piston portion toward the input member.

19. The fan clutch device of claim 18, wherein when the piston portion shifts toward the input member, the clutch ring is engaged by the input member and the output member.

20. The fan clutch device of claim 19, further comprising a channel in fluid communication with a fluid-receiving space defined at least partially by surfaces of the hub portion and the piston portion.

21. The fan clutch device of claim 20, wherein the piston portion selectively moves relative to the hub portion when a predetermined fluid pressure is applied in the fluid-receiving space.

22. The fan clutch device of claim 20, wherein when a predetermined fluid pressure is applied in the fluid-receiving space, the piston portion moves away from the input member so that the clutch ring is disengaged from one of the input member and the output member.

23. The fan clutch device of claim 13, wherein when the clutch ring is in an engaged condition and the fan clutch device is mounted to the drive member, the torque required to cause slippage between the output member and the drive member is about 3000 in-lbs to about 5000 in-lbs.