Patent Publication Number: US-9890519-B2

Title: Tiltable tool assembly

Description:
BACKGROUND OF THE INVENTION 
     Field of the Invention 
     The present invention relates generally to backhoes and excavators and, more particularly, to buckets and other tools which are laterally tiltable. 
     Description of the Related Art 
     Backhoes, excavators and similar type vehicles have an extendable or articulated arm with a tool such as a bucket attached at an end thereof remote from the operator. Generally, a rotation link is associated with the arm. The bucket is pivotally attached to the arm by a clevis which serves as a pivot point for the bucket. The rotation link is also pivotally attached to the bucket so that movement of the rotation link causes the bucket to rotate about the arm pivot point. With such an arrangement, the bucket can be rotated relative to the arm in a generally vertical, forwardly extending plane defined by the arm and the rotation link, but lateral tilting of the bucket is not possible, at least without tilting of the vehicle. The arm and rotation link are usually not laterally tiltable relative to the vehicle to which they are attached. 
     There are occasions, however, when it would be very desirable to work with the bucket tilted to the left or right, such as when necessary to adjust for slope requirements or to do side-angle grading. It is, of course, undesirable and often not possible to laterally tilt the entire vehicle to achieve tilting of the bucket. This problem has been overcome with the advent of laterally tiltable buckets. Such buckets generally include a hinge adaptor which is attached to the arm and the rotation link, much in the same way buckets were directly attached in the past. The adaptor serves as a hinge and pivotally supports a bucket for lateral rotation of the bucket about a hinge axis which is generally aligned with the forward rotation plane through which the bucket is conventionally rotated. This allows the bucket to be laterally tilted from side to side. Control of the amount of lateral tilting is accomplished using a double-acting cylinder which extends laterally between the hinge adaptor and the bucket to selectively cause the bucket to rotate about the hinge axis. Extension of the double-acting cylinder causes the bucket to rotate to one side, and retraction of the cylinder causes it to rotate to the other side. 
     To achieve the desirable range of tilting, such an arrangement has required a relatively long, double-acting cylinder. As such, only relatively wide buckets could accommodate the amount of extension and retraction of the double-acting cylinder required to laterally tilt the bucket to the extent desired. The more tilting required, the greater the space required to handle the double-acting cylinder to be used, because greater extension is needed. Of course, space limitations not only limit the length of the double-acting cylinder which can be used, but also the torque output achievable with the cylinder. The use of a bucket that is wide enough to accommodate the elongated double-acting cylinders does not always solve these problems, because certain type jobs can best be done only with relatively narrow buckets. Typically, it is desired to have tiltable buckets tilt 45 degrees to the left and to the right relative to the vertical. 
     The need for a laterally tiltable bucket assembly which uses a relatively narrow width bucket has been largely met by the Tiltable Bucket Assembly described in U.S. Pat. No. 4,906,161. That bucket assembly can transmit large torque to the bucket and firmly hold the bucket at the desired tilt angle. That bucket assembly does not, however, provide means for quickly disconnecting the bucket or other tool from the vehicle arm and rotation link, but rather requires the operator to remove the pins which hold the bucket in place and re-insert them for the next tool to be attached. This is a slow and sometimes difficult process. 
     One solution to the need for a quick disconnect of a bucket or other tool from the vehicle arm and rotation link was provided by U.S. Pat. No. 5,145,313 and U.S. Pat. No. 5,242,258. However, there has been determined to exist a need for a stronger, lighter and more versatile design. 
     It will, therefore, be appreciated that there has been a significant need for a laterally tiltable tool assembly which can quickly and easily disconnect and re-connect the bucket or another tool, and will provides improvements over prior art assemblies. The present invention fulfills this need and further provides other related advantages. 
    
    
     
       BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING(S) 
         FIG. 1  is a front right side perspective view of an excavator shown with one version of a laterally tiltable tool assembly embodying the present invention with a bucket attached and showing other attachable tools on the ground. 
         FIG. 2  is an enlarged, fragmentary, right side, cross-sectional view of a first embodiment of the tool assembly of  FIG. 1 . 
         FIG. 2A  is a partial rear end view of the actuator of  FIG. 2 , shown taken substantially along the line A-A of  FIG. 2 . 
         FIG. 2B  is an enlarged portion of the actuator of  FIG. 2  shown substantially within the oval  2 B of  FIG. 2 . 
         FIG. 2C  is an enlarged portion of the actuator of  FIG. 2  showing first and second wall portions of the actuator body and third and fourth wall portions of the actuator shaft. 
         FIG. 3  is an enlarged, fragmentary, right side, cross-sectional view of a second embodiment of the tool assembly of  FIG. 1 . 
         FIG. 3A  is a partial cross-sectional view of the actuator of  FIG. 3 , shown taken substantially along the line B-B of  FIG. 3 . 
         FIG. 4  is an enlarged, fragmentary, right side, cross-sectional view of a third embodiment of the tool assembly of  FIG. 1 . 
         FIG. 5  is an enlarged, fragmentary, right side, cross-sectional view of a fourth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 6  is an enlarged, fragmentary, right side, cross-sectional view of a fifth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 7  is an enlarged, fragmentary, right side, cross-sectional view of a sixth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 7A  is a partial cross-sectional view of the actuator of  FIG. 7 , shown taken substantially along the line A-A of  FIG. 7 . 
         FIG. 8  is an enlarged, fragmentary, right side, cross-sectional view of a seventh embodiment of the tool assembly of  FIG. 1 , shown taken substantially along the line A-A of  FIG. 8A . 
         FIG. 8A  is a fragmentary end view of the actuator of  FIG. 8 . 
         FIG. 8B  is a partial cross-sectional view of the actuator of  FIG. 8 , shown taken substantially along the line B-B of  FIG. 8 . 
         FIG. 9  is an enlarged, fragmentary, right side, cross-sectional view of a eighth embodiment of the tool assembly of  FIG. 1  also providing rotation of a tool in addition to lateral tilting, shown taken substantially along the line B-B of  FIG. 9A . 
         FIG. 9A  is an end view of the tool assembly of  FIG. 9 . 
         FIG. 9B  is a partial cross-sectional view of the actuator of  FIG. 9 , shown taken substantially along the line C-C of  FIG. 9 . 
         FIG. 10  is an enlarged, fragmentary, right side, cross-sectional view of a ninth embodiment of the tool assembly of  FIG. 1  also providing rotation of a tool in addition to lateral tilting, shown taken substantially along the line A-A of  FIG. 10A . 
         FIG. 10A  is an end view of the tool assembly of  FIG. 10 . 
         FIG. 11  is an enlarged, fragmentary, right side, cross-sectional view of a tenth embodiment of the tool assembly of  FIG. 1  also providing rotation of a tool in addition to lateral tilting. 
         FIG. 12  is an enlarged, fragmentary, right side, cross-sectional view of an eleventh embodiment of the tool assembly of  FIG. 1  with a rotatable grapple assembly attached. 
         FIG. 12A  is a reduced, partial end view taken substantially along the line A-A of  FIG. 12 . 
         FIG. 12B  is an enlarged cross-sectional view taken substantially along the line B-B of  FIG. 12  without the grapple assembly attached. 
         FIG. 13  is an enlarged, fragmentary, right side, cross-sectional view of a twelfth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 14  is an enlarged, fragmentary, right side, cross-sectional view of a thirteenth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 15  is an enlarged, fragmentary, right side, cross-sectional view of a fourteenth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 15A  is a partial end view taken substantially along the line A-A of  FIG. 15 . 
         FIG. 16  is an enlarged, fragmentary, right side, cross-sectional view of a fifteenth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 17  is an enlarged, fragmentary, right side, cross-sectional view of a sixteenth embodiment of the tool assembly of  FIG. 1 . 
         FIG. 17A  is a partial cross-sectional view taken substantially along the line B-B of  FIG. 17 . 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     As shown in the drawings for purposes of illustration, the present invention is embodied in a fluid-powered, laterally tiltable tool assembly, indicated generally by reference numeral  10 . As shown in  FIG. 1 , the tool assembly is usable with a vehicle  12 , such as the illustrated excavator or any other suitable type vehicle such as a backhoe that might use a bucket or other tool as a work implement. The vehicle  12  has a first arm  14  which is pivotally connected by one end to a base member (not shown) forming a part of the platform  12 A of the vehicle. A pair of hydraulic cylinders  16  and  18  are provided for raising and lowering the first arm in a generally forwardly extending vertical plane with respect to the base member. A second arm  20  is pivotally connected by one end to an end of the first arm  14  remote from the base member. A hydraulic cylinder  22  is provided for rotation of the second arm  20  relative to the first arm  14  in the same vertical forward rotation plane as the first arm operates. 
     The platform  12 A of the vehicle  12  is pivotally mounted and supported by a track drive undercarriage  12 B and is pivotally movable about a vertical axis so as to permit movement of the first and second arms  14  and  20  in unison to the left or right, with the first and second arms always being maintained in the forward rotation plane. It is noted that while the forward rotation plane is referred to as being forwardly extending for convenience of description, as the platform  12 A is pivoted relative to the track drive, the forward rotation plane turns about the vertical pivot axis of the track drive and thus to a certain extent loses its forward-to-rearward orientation, with the plane actually extending laterally relative to the undercarriage  12 B should the platform be sufficiently rotated. 
     A rotation link  24  is pivotally connected through a pair of interconnecting links  26  to an end portion  28  of the second arm  20  remote from the point of attachment of the second arm to the first arm  14 . A hydraulic cylinder  30  is provided for selective movement of the rotation link  24  relative to the second arm  20 . 
     As is conventional, a free end portion  31  of the second arm  20  and a free end portion  32  of the rotation link  24  each has a transverse aperture therethrough for connection of the second arm and the rotation link to a conventional tool such as a bucket using a pair of selectively removable attachment pins  33 . The attachment pins  33  are insertable in the apertures to pivotally connect the conventional tool directly to the second arm and the rotation link. When using the conventional tool, this permits the tool to be rotated about the attachment pin of the second arm  20  upon movement of the rotation link  24  relative to the second arm as a result of extension or retraction of the hydraulic cylinder  30  to rotate the conventional tool in the forward rotation plane defined by the first and second arms  14  and  20 . 
     In the embodiment of the invention shown in  FIG. 1 , a conventional bucket  34  of relatively narrow width is utilized. The bucket has a toothed working edge  35  extending laterally, generally transverse to the forward rotation plane of the bucket. The bucket  34  further includes a first and second bucket clevises  36  and  38 , with the first bucket clevis located toward the bucket working edge  35  and second bucket clevis  38  located forwardwardly of the first bucket clevis and away from the bucket working edge. The first and second bucket clevises are in general parallel alignment with the forward rotation plane of the bucket. It should be understood that the present invention may be practiced using other tools as work implements, and is not limited to just operation with buckets. 
     The tool assembly  10  of the present invention includes a hydraulic rotary actuator  40 . One version of the rotary actuator  40  is shown in  FIG. 2 . The second arm  20  of the vehicle  12  is shown tucked under the first arm  14  to position the bucket  34  or other tool attached to the tool assembly  10  for better visibility by the operator in the vehicle  12  when attaching or detaching the tool. The rotary actuator  40  has an elongated housing or body  42  with a sidewall  44  and first and second body ends  46  and  48 , respectively. An elongated rotary drive or output shaft  50  is coaxially positioned within the body  42  and supported for rotation relative to the body about a longitudinal axis. 
     The shaft  50  extends the full length of the body  42 , and has a flange portion  52  at the first body end  46 . The shaft has a shaft first end portion  53 A at the first body end  46  and a shaft second end portion  53 B at the second body end  48 . The shaft  50  has an annular carrier or shaft nut  54  threadably attached thereto at the second body end  48 . The shaft nut  54  has a threaded interior portion threadably attached to a correspondingly threaded perimeter portion  55  of the shaft  50 , and the shaft nut rotates with the shaft. The shaft nut  54  is locked in place against rotation relative to the shaft  50  as the shaft rotates during operation of the rotary actuator  40 . 
     A seal is disposed between the shaft nut  54  and the shaft  50  to provide a fluid-tight seal therebetween. Seals  52 A are disposed between the shaft flange portion  52  and the body sidewall  44  at the first body end  46  to provide a fluid-tight seal therebetween. Radial bearing may also be disposed between the shaft flange portion  52  and the body sidewall  44  to support the shaft  50  against radial thrust loads. 
     A first attachment flange  56  is positioned outward of the body  42  at the first body end  46  and is rigidly attached to the shaft first end portion  53 A at the first body end for rotation with the shaft  50  relative to the body  42 . The first attachment flange  56  abuts against the outward end face of the shaft first end portion  53 A for support and is bolted thereto by a plurality of circumferentially arranged bolts  53 C (only one being illustrated in  FIG. 2 ). The first attachment flange  56  has the rotational drive of the shaft  50  transmitted thereto so as to provide the torque needed for tilting the bucket  34  to the desired lateral tilt angle and for holding the bucket in that position while the bucket performs the desired work. The first attachment flange  56  does not move axially relative to the body  42 . The first attachment flange  56  extends radially beyond the body sidewall  44  downwardly toward the bucket  34 , and is rigidly attached to a tool attachment assembly  58  spaced below and away from the rotary actuator  40 , and provided to achieve releasable attachment thereto of a tool such as the bucket  34  shown in  FIG. 1 . 
     A retainer member  60  is positioned outward of the body  42  at the second body end  48  and is rigidly attached to the shaft second end portion  53 B at the second body end for rotation with the shaft  50  relative to the body  42 . The retainer member  60  retains a second attachment flange  62  outward of the body  42  at the second body end  48 . 
     The retainer member  60  has a rearward end abutting against the outward end face of the shaft second end portion  53 B for support and is bolted thereto by a plurality of circumferentially arranged bolts  53 D, with five bolts  53 D being illustrated by way of example in  FIG. 2A . The rearward end portion of the retainer member  60  is received in a recess in a forward end face of the shaft nut  54 . The retainer member  60  has a cylindrical body portion  60 A with a radially outward extending flange  60 B at a forward end thereof. The body portion  60 A extends through a cylindrical aperture  60 C of the second attachment flange  62 . The second attachment flange  62  is rotatably retained on the body portion  60 A in position between the shaft second end portion  53 B and the retainer member flange  60 B. The second attachment flange  62  does not move axially relative to the body  42 . The second attachment flange  62  extends radially beyond the body sidewall  44  downwardly toward the bucket  34 , and is rigidly attached to the tool attachment assembly  58 . The first and second attachment flanges  56  and  62  hold the tool attachment assembly  58  suspended below and space away from the rotary actuator  40 . 
     The tool attachment assembly  58  has a support frame  64  with a rearward end portion  66  to which the first attachment flange  56  is rigidly attached, and a forward end portion  68  to which the second attachment flange  62  is rigidly attached. A pair of laterally spaced-apart rear forks  70  which each have a rearward facing opening  70 A (only one fork being visible in  FIG. 2 ) are rigidly attached to the support frame  64  at the rearward end portion  66  thereof and project downward to a position for releasable attachment to a tool such as the bucket  34  shown in  FIG. 1 . Positioned forward of the rear forks  70  are a pair of laterally spaced-apart front forks  72  which each have a forward facing opening  72 A (again only one fork being visible in  FIG. 2 ) and project downward to a position for releasable attachment to a tool. The front forks  72  are retained against significant lateral movement relative to the support frame  64 , but are movably supported by the support frame for reciprocal forward and rearward longitudinal movement of the front forks relative thereto and to the rear forks  70  to allow adjustable spacing between the front and rear forks to facilitate their releasable attachment to a tool. The longitudinal movement of the front forks  72  is guided by left and right side longitudinally extending guide slots  73  (only the left side guide slot being visible in  FIG. 2 ) to maintain a linear movement of the front forks. 
     The tool attachment assembly  58  further includes a hydraulic linear actuator  74  supported by the support frame  64 . The linear actuator  74  has an elongated housing or body  76  with a sidewall  78 , and rearward and forward body ends  80  and  82 , respectively. A piston  84  is disposed within the body  76  for linear reciprocating movement therein between the rearward and forward body ends  80  and  82  along a longitudinal axis. An elongated shaft  86  is coaxially positioned within the body  76  and supported for linear longitudinal movement relative thereto. A rearward end  86 A of the shaft  86  is attached to the piston  84  for movement therewith. The shaft  86  extends forwardly out to the forward body end  82  and a forward end  86 B of the shaft  86  is attached to the front forks  72  to move the front forks forward and rearward in response to movement of the piston  84  for selectively adjusting the spacing between the rear and front forks  70  and  72  to facilitate their releasable attachment to a tool. In the illustrated embodiment, the linear actuator  74  is a hydraulic cylinder. 
     The first and second attachment flanges  56  and  62  support the tool attachment assembly  58  with the linear actuator  74  spaced below and away from the rotary actuator  40  and in general parallel longitudinal alignment with the rotary actuator  40 . The longitudinal axis of the rotary actuator  40  and the longitudinal axis of the linear actuator  74  are offset from each other in a generally parallel arrangement. The support frame  64  and hence the rear and front forks  70  and  72  rotate with the first and second attachment flanges  56  and  62  in response to rotation of the shaft  50  of the rotary actuator  40  about the same axis of rotation as the shaft  50  of the rotary actuator  40  when the rotary actuator is operated to tilt right or left the bucket  34  or other tool attached to the tool attachment assembly  58 . By the hydraulic operation of the rotary actuator  40 , the shaft  50  can be selectively rotated clockwise and counterclockwise (when viewed from rearward of the first body end  46  of the body  42 ) to selectively rotate the first and second attachment flanges  56  and  62  clockwise (i.e., tilt to the left) and counterclockwise (i.e., tilt to the right), and though their attachment to the tool attachment assembly  58 , to rotate the linear actuator  74  clockwise and counterclockwise as a unit with the shaft  50 . 
     While the retainer member  60  is securely attached to the shaft  50 , and the second attachment flange  62  is mounted on the retainer member  60  for rotation with the shaft  50  relative to the body  42 , as does the first attachment flange  56 , the second attachment flange is not constructed to transmit rotational drive to the bucket  34  to provide the torque needed to tilt the bucket, as is the case with the first attachment flange  56 . Nevertheless, the second attachment flange  62  will rotate with the shaft  50  as a result of the rotational drive transmitted thereto through the first attachment flange  56  via the tool attachment assembly  58 . The second attachment flange  62  primarily serves to transmit the rotational force to the bucket  34  produced by the movement of the rotation link  24  relative to the second arm  20  in order to cause the bucket to be selectively rotated through the forward rotation plane. The entire bucket assembly  10 , and hence the bucket  34  comprising a part thereof, rotates about the attachment pin  33  of the second arm  20  as the rotation link  24  is moved relative to the second arm by the hydraulic cylinder  30 . 
     As will be described below, the body  42  of the rotary actuator  40  is pivotally attached to the second arm  20  and the rotation link  24 , much in the same manner as a conventional bucket would be attached. 
     The attachment of the bucket  34  to the tool assembly  10  will be described for the bucket being attached with its working edge  35  located toward the vehicle  12 , but it should be understood that the bucket and most any other tool used with the tool assembly  40  can be reversed. The two rear forks  70  of the tool attachment assembly  58  are laterally spaced apart and have the openings  70 A sized for mating with a laterally extending pin  36 A of the corresponding first bucket clevis  36 , and the two front forks  72  of the tool attachment assembly are spaced apart and have the openings  72 A sized for mating with a laterally extending pin  38 A of the corresponding second bucket clevis  38  for releasable attachment of the bucket  34  to the tool assembly  10  at a position below the rotary actuator  40  and also below the linear actuator  74 . The openings  70 A and  72 A of the rear and front forks  70  and  72  face in opposite directions and are sized and oriented to receive and securely hold the pins  36 A and  38 A of the first and second clevises  36  and  38  securely therein for performing work with the bucket  34  or other tool connected to the tool assembly, but permit quick attachment and release of the bucket or other tool when desired. 
     With the tool assembly  10  moved to position the pin  36 A of the first bucket clevis  36  within the openings  70 A of the rear forks  70 , and the front forks between the pins of the first and second bucket clevis  36  and  38 , the piston  84  of the linear actuator  74  is moved toward the forward body end  82  of the body  76  of the linear actuator to extend the shaft  86  further out of the body sufficiently to place the pin  38 A of the second bucket clevis  38  securely in the openings  72 A of the front forks  72 . In this locking position, the bucket  34  or other tool is securely attached to the tool assembly  10  and ready to be used to perform work. To detach the bucket  34  or other tool from the tool assembly  10 , the piston  84  of the linear actuator  74  is moved toward the rearward body end  80  of the body  76  of the linear actuator to retract the shaft  86  further into the body sufficiently to move the front forks  72  rearward into a release position where free of the pin  38 A of the second bucket clevis  38  and the distance between the rear and front forks  70  and  72  is sufficiently less than the distance between the pins  36 A and  38 A of the first and second clevis  36  and  38  so that the tool assembly  10  can be moved to release the pins from both the rear and front forks, and hence the bucket  34  or other tool can be removed and replaced with another tool. By the selective extension and retraction of the linear actuator  74 , one tool can be quickly and conveniently removed from the tool assembly  10  for attachment of another tool, or for reversal of the tool. This allows for quick and easy attachment of a different size or style bucket or other tools as a job demands. Also, the linear actuator  74  can be adjusted to move the rear and front forks  70  and  72  apart by selected distances of varying amounts to accommodate buckets and other tools with clevis pins having different inter-pin spacing, and thereby still securely clamp the pins between the rear and front forks. 
     It should be noted that while the rear and front forks  70  and  72  are shown and described as being outwardly facing, the orientation of the rear and front forks can be reversed. With such an arrangement, the shaft  86  of the linear actuator  74  would be retracted further into the body  76  to move the rear and front forks  70  and  72  closer together to securely clamp the pins  36 A and  38 A of the first and second clevis  36  and  38  between the rear and front forks. Further, it is understood that this invention applies broadly to tool attachment assemblies differing in construction from the described tool attachment assembly  58 . For example, it applies to tool attachment assemblies which are operated by other means than fluid, or engage with working tools such as buckets which do not have pins  36 A and  38 A but another means for connecting with and disconnecting from the attachment assembly. 
     The tool assembly  10  includes a pair of attachment brackets  88  rigidly attached to the body  42  of the rotary actuator  40  to detachably connect the tool assembly to the second arm  20  and the rotation link  24  in a position therebelow in general alignment with the forward rotation plane. The attachment brackets  88  form first and second attachment clevis with apertures therein each sized to receive one of the attachment pins  33  to pivotally connect the tool assembly  10  to the vehicle second arm  20  at its free end portion  31 , and to pivotally connect the tool assembly to the rotation link  24  at its free end portion  32 . By the use of selectively removable attachment pins  33 , the tool assembly  10  can be removed from the second arm  20  and the rotation link  24  when use of the tool assembly is not desired. 
     With the tool assembly  10  of the present invention, a compact, fluid-powered rotary actuator  40  is used with a design which requires far less space, particularly with respect to the size in the lateral direction compared to when using double-acting cylinders to rotate a tilt bucket. This allows the construction of a tiltable bucket assembly with a very narrow width bucket. Furthermore, the bucket assembly can be used with conventional buckets and thus can be retrofitted onto vehicles with existing buckets without requiring purchase of a new bucket. 
     The rotary actuator  40  uses an annular piston sleeve  90  coaxially and reciprocally mounted within the body  42  coaxially about the shaft  50 . The piston sleeve  90  has a piston head  96  and a splined sleeve portion  97  with outer straight splines over a portion of its length which mesh with inner straight splines  92  of a splined intermediate interior portion of the body sidewall  44 . Alternatively, the outer splines of the splined sleeve portion  97  and the inner splines  92  of the splined intermediate interior portion of the body sidewall  44  may be helical splines. The sleeve portion  97  is also provided with inner helical splines which mesh with outer helical splines  94  provided on a splined end portion of the shaft  50  toward the first body end  46 . It should be understood that while splines are shown in the drawings and described herein, the principle of the invention is equally applicable to any form of linear-to-rotary motion conversion means, such as balls or rollers, or other means such as where the body and the piston sleeve have non-circular cross-sectional shapes, as will be described with another illustrated embodiment of the invention. 
     In the embodiment of the invention illustrated in  FIG. 2 , the piston head  96  of the piston sleeve  90  is annular in shape and positioned toward the second body end  48  with the shaft  50  extending therethrough. The piston head  96  is slidably maintained within the body  42  for reciprocal movement, and undergoes longitudinal and rotational movement relative to the body sidewall  44 . 
     Seals are disposed between the piston head  96  of the piston sleeve  90  and a smooth interior wall portion of the body sidewall  44  to provide a fluid-tight seal therebetween. Seals are disposed between the piston head  96  and a smooth exterior wall surface  102  of the shaft  50  to provide a fluid-tight seal therebetween. 
     As will be readily understood, reciprocation of the piston head  96  within the body  42  of the rotary actuator occurs when hydraulic fluid, such as oil, air or any other suitable fluid, under pressure selectively enters through one or the other of a first port P 1  which is in fluid communication with a fluid-tight compartment within the body to a side of the piston head toward the first body end  46  or through a second port P 2  which is in fluid communication with a fluid-tight compartment within the body to a side of the piston head toward the second body end  48 . As the piston head  96  and the piston sleeve  90 , of which the piston head is a part, linearly reciprocates in an axial direction within the body  40 , the outer helical splines of the sleeve portion  97  engage or mesh with the inner helical splines  92  of the body sidewall  44  to cause rotation of the piston sleeve. The linear and rotational movement of the piston sleeve  90  is transmitted through the inner helical splines of the sleeve portion  97  to the outer helical splines  94  of the shaft  50  to cause the shaft  50  to rotate. The smooth wall surface of the shaft  50  and the smooth wall surface of the body sidewall  44  have sufficient axial length to accommodate the full end-to-end reciprocating stroke travel of the piston sleeve  90  within the body  42 . Longitudinal movement of the shaft  50  is restricted, thus all movement of the piston sleeve  90  is converted into rotational movement of the shaft  50 . Depending on the slope and direction of turn of the various helical splines, there may be provided a summing of the rotary output of the shaft  50 . 
     The application of fluid pressure to the first port P 1  produces axial movement of the piston sleeve  90  toward the second body end  48 . The application of fluid pressure to the second port P 2  produces axial movement of the piston sleeve  90  toward the first body end  46 . The rotary actuator  40  provides relative rotational movement between the body  42  and shaft  50  through the conversion of linear movement of the piston sleeve  90  into rotational movement of the shaft, in a manner well known in the art. The shaft  50  is selectively rotated by the application of fluid pressure, and the rotation is transmitted to the bucket  34  or other tool through the first attachment flange  56  to selectively tilt the attached bucket or other tool laterally, left and right. 
     The shaft  50  has an axially extending central aperture  50 A which extends between the first body end  46  partially to the second body end  48 . A relief valve  51  is positioned within the central aperture  50 A and threadably attached to a threaded portion of the interior wall of the central aperture  50 A of the shaft  50 . A fluid passageway  50 B communicates between the relief valve  51  and the fluid-tight compartment within the body  42  to the side of the piston head toward the first body end  46  and a fluid passageway  50 C communicates between the relief valve and the fluid-tight compartment within the body to the side of the piston head toward the second body end  48 . The positioning of the relief valve  51  within the central aperture avoids its interference with operation of the tool assembly  10 . 
     As will also be readily understood, linear reciprocation of the piston  84  within the body  76  of the linear actuator  74  occurs when hydraulic oil, air or any other suitable fluid under pressure selectively enters through one or the other of a third port P 3  which is in fluid communication with a fluid-tight compartment within the body to a side of the piston toward the rearward body end  80  or through a fourth port P 4  which is in fluid communication with a fluid-tight compartment within the body to a side of the piston toward the forward body end  82 . As the piston  84  linearly reciprocates in an axial direction forward and rearward within the body  76 , the piston applies a linear force on the forward end of the shaft  86  which the shaft delivers to the front forks  72  to move the front forks forward and rearward, respectively, to adjust the spacing between the rear and front forks  70  and  72 . The application of fluid pressure to the third port P 3  produces axial movement of the piston  84  toward the forward body end  82  and hence forward movement of the front forks  72 . The application of fluid pressure to the fourth port P 4  produces axial movement of the piston  84  toward the rearward body end  80  and hence rearward movement of the front forks  72 . 
     Hydraulic fluid is communicated to the first and second ports P 1  and P 2  of the rotary actuator  40  by hydraulic lines L 1  and L 2 , respectively, connected directly to the first and second ports P 1  and P 2  to control operation of the rotary actuator. While hydraulic fluid could be connected directly to the third and fourth ports P 3  and P 4  of the linear actuator  74 , the lines would by necessity be in locations where they could contact or become entangled with objects in the work environment and be damaged, and take up space. To avoid this, hydraulic fluid is communicated to the third and fourth ports P 3  and P 4  of the linear actuator  74  by hydraulic lines L 3  and L 4 , respectively, using various passageways interior to the rotary actuator, the first attachment flange  56  and the support frame  64  without using additional exterior hydraulic lines. The hydraulic line L 3  is directly connected to a fifth port P 5  provided in a circumferentially extending first wall portion WP 1  of the body sidewall  44  of the rotary actuator  40  toward the first body end  46  of the body  42  at a location toward an upper side of the body, and the hydraulic line L 4  is directly connected to a sixth port P 6  provided in a circumferentially extending second wall portion WP 2  of the body sidewall  44  of the rotary actuator  40  toward the first body end  46  of the body  42  also at a location toward an upper side of the body and adjacent to the fifth port P 5 . The shaft flange portion  52  of the shaft  50  in combination with the correspondingly located portion of the sidewall  44  of the body  42  form an oil gland used to communicate the hydraulic fluid from hydraulic lines L 3  and L 4  to the third and fourth ports P 3  and P 4  of the linear actuator  74 . The periphery of the shaft flange portion  52  of the shaft  50  of the rotary actuator  40 , at a location radially inward from the fifth port P 5 , has a first circumferential channel C 1 , located between the first wall portion WP 1  of the body  42  and a circumferentially extending third wall portion WP 3  of the shaft flange portion  52  which is in fluid communication with the fifth port P 5 . Similarly, periphery of the shaft flange portion  52  of the shaft  50  of the rotary actuator  40 , at a location radially inward from the sixth port P 6 , has a second circumferential channel C 2 , located between the second wall portion WP 2  of the body  42  and a circumferentially extending fourth wall portion WP 4  of the shaft flange portion  52  which is in fluid communication with the sixth port P 6 . The first, second, third and fourth wall portions WP 1 , WP 2 , WP 3  and WP 4  are illustrated in  FIG. 2C . 
     Fluid communication between the first and second circumferential channels C 1  and C 2  and the third and fourth ports P 3  and P 4  of the linear actuator  74  is accomplished by first and second internal passageways IP 1  and IP 2  in the shaft flange portion  52 , third and fourth internal passageways IP 3  and IP 4  in the first attachment flange  56 , and a fifth internal passageway IP 5  in the form of an interiorly located tube welded in position. The first internal passageway IP 1  of the shaft flange portion  52  has one end in communication with the first circumferential channel C 1  at a location toward a lower side of the shaft  50  of the rotary actuator  40 , and another end in communication with one end of the third internal passageway IP 3  of the first attachment flange  56  at a location at the interface of the outward end face of the shaft first end portion  53 A with the forward surface of the first attachment flange  56 . The other end of the third internal passageway IP 3  of the first attachment flange  56  is in communication with the third port P 3  of the linear actuator  74 . Somewhat similarly, the second internal passageway IP 2  of the shaft flange portion  52  has one end in communication with the second circumferential channel C 2  at a location toward a lower side of the shaft  50  of the rotary actuator  40 , and another end in communication with one end of the fourth internal passageway IP 4  of the first attachment flange  56  at a location at the interface of the outward end face of the shaft first end portion  53 A with the forward surface of the first attachment flange  56 . The other end of the fourth internal passageway IP 4  of the first attachment flange  56  is in communication with one end of the fifth internal passageway IP 5 . The other end of the fifth internal passageway IP 5  is in communication with the fourth port P 4  of the linear actuator  74 . 
     Circumferential seals are disposed between the first and second circumferential channels C 1  and C 2 , and longitudinally outward of each channel. Additional seals are provided at the interfaces of the various component parts of the tool assembly to avoid fluid leakage at the junctions of the various internal passageways IP 1  through IP 5  with each other and with the third and fourth ports P 3  and P 4  of the linear actuator  74 . 
     With the hydraulic system of the tool assembly  10  described above, the rotation of the tool assembly about the free end portion  31  of the second arm  20 , the rotation of the tool attachment assembly  58  about the axis of the shaft  50  of the rotary actuator  40 , and the linear movement of the front forks  72  relative to the rear forks  70  by the linear actuator  74  is controlled by the operator from within the cab of the vehicle  12 . 
     As described above, the first attachment flange  56  is bolted to the shaft first end portion  53 A by a plurality of circumferentially arranged bolts  53 C, and the retainer member  60  is bolted to the shaft second end portion  53 B by a plurality of circumferentially arranged bolts  53 D, as illustrated in  FIG. 2A . The bolts  53 D have sufficient length to extend axially into the shaft  50  well beyond the distance necessary merely to secure the first attachment flange  56  and the retainer member  60  to the shaft. This distance is sufficient to significantly pre-stress/pre-load the shaft  50  when the bolts are tightened by placing the areas of the shaft which are threaded to receive the bolts  53 D in compression and thereby help prevent fatigue failure and improve fatigue life. In the illustrated embodiment the distance is sufficient to create a pre-loading that is at least 50% of all axial forces the rotary actuator  40  is designed to experience during use, and preferably greater than all the axial forces applied to the end area of the shaft  50  where the bolts are located during operation of the rotary actuator, including forces created by the application of fluid pressure to the rotary actuator  40 . This pre-stressing of the shaft  50  allows a shaft that would otherwise be limited to use with lower hydraulic pressures to operate at pressures above 3,000 psi and use a smaller shaft. With this arrangement, the shaft  50  of the rotary actuator  40  has improved resilience to cyclical loading. 
     The described pre-loaded design overcomes failures of the shaft  50  which typically occur at regions of stress concentrations such as threads or shaft to flange transitions under cyclical loading. The pre-loaded design has two mechanisms for improving fatigue life. It places the would be area of crack initiation and propagation under a compressive stress. It also reduces the magnitude of stress fluctuation in the member taking the tensile loads. To further explain reference is made to  FIG. 2B . The location “A” is the location of the first loaded thread of the threaded attachment between the shaft  50  and the shaft nut  54  at the second body end  48 . This is the typical failure point. The location “B” is the location of the start of threaded engagement of the bolt  53 D to the shaft second end portion  53 B for attaching the retainer member  60  to the shaft second end portion  53 B. Location “C” is the location of the other point of pre-load where the retainer member  60  is positioned at the outward end of the shaft second end portion  53 B. It should be noted that location “A” is well between locations “B” and “C”, that is, in the compressive zone created by the tightly bolting the retainer member  60  to the shaft second end portion  53 B at the second body end  48  with bolts  53 D, which puts the portion of the shaft second end portion between locations “B” and “C” under a significant amount of compression. This is accomplished by drilling a plurality of recesses or holes “D” in the shaft second end portion  53 B, each having an unthreaded portion and a threaded portion, with the threaded portion having its first thread to be threadably engaged by the threads of one of the bolts  53 D at location “B,” with the location “A” and the threads of the shaft  50  by which the shaft nut  54  is threadably attached to the shaft located between the location “B” and the location “C”. As seen in  FIG. 2B , the threaded portion of the hole “D” extends from location “B” toward the first body end  46 . Again, this places the portion of the shaft second end portion  53 B between locations “B” and “C” under compression (i.e., in a compression zone), and significantly pre-stresses/pre-loads the shaft  50  when the bolts  53 D are tightened prior to operation of the rotary actuator  40 . 
     A second embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 3  having a similar construction to the tool assembly of  FIG. 2 , except the retainer member  60  is not used to rotatably retain the second attachment flange  62 . Instead, the second attachment flange  62  is bolted directly to the shaft nut  54  by a plurality of circumferentially arranged bolts  53 E positioned radially outward of the bolts  53 D attaching the retainer member  60  to the shaft second end portion  53 B at the second body end  48  of the body  42  of the rotary actuator  40 , as illustrated in  FIG. 3A . 
     A third embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 4  having a similar construction to the tool assembly of  FIG. 2 , except for several aspects of the rotary actuator  40  that will be described. In particular, the rotary actuator  40  shown in  FIG. 4  utilizes a shaft  50  having a stub shaft portion  100  and an end cap portion  102 . The stub shaft portion  100  extends from the first body end  46  partially toward the second body end  48  and terminates in an exteriorly threaded end portion  104 , and the end cap portion  102  extends from the second body end partially toward the first body end and terminates in an interiorly threaded end portion  106  which is threadably receives the exteriorly threaded end portion  104  of the stub shaft portion therein. Further, the rotary actuator of this embodiment eliminates the use of the shaft nut  54  at the second body end  48  and instead the end cap portion  102  includes a flange portion  108  at the second body end to which the second attachment flange  62  is directly bolted by the bolts  53 D without use of the intermediary retainer member  60 . The exterior end face of the end cap portion  102  has an exteriorly open recess  110  therein. 
     Additionally, the shaft  50  of the rotary actuator  40  in this embodiment has an enlarged axially extending central aperture  50 A which extends fully between the first body end  46  and the second body end  48 , and opens at the second body end into the recess  110  of the end cap portion  102  and defines a shoulder  112  extending about the opening. The central aperture  50 A is sized to receive a center bolt  114  therein. The center bolt  114  has a head  116  which is sufficiently large to engage the shoulder  112  within the recess  110 , and an exteriorly threaded portion  118  which is positioned within the central aperture to be threadably received by an interiorly threaded portion  120  of the stub shaft portion  100  of the shaft  50  located toward its end toward the second body end  48  and about midway between the first and second body ends  46  and  48 . Tightening of the center bolt  114  applies a significant pre-stress/pre-load on the shaft  50  by placing the length of the shaft between the head  116  of the center bolt and the interiorly threaded portion  120  of the stub shaft portion  100  of the shaft in compression. The use of the center bolt  114  helps achieve a desired pre-loading that is at least 50% of all axial forces for which the rotary actuator  40  is designed to experience during use, and preferably greater than all the axial forces applied to the shaft  50  during operation of the rotary actuator. 
     The rotary actuator  40  of this third embodiment of the tool assembly  10  shown in  FIG. 4  has the relief valve  51  threadably received in a threaded recess  122  in an inward end portion of the center bolt  114 , and a seal  124  positioned between the center bolt and the interior wall of the central aperture  50 A of the shaft  50 . A pair of fluid passageways  50 D are provided in the center bolt  114  which communicate hydraulic fluid between the relief valve  51  and the central aperture  50 A to a side of the seal  124  toward the second body end  48 . A fluid passageway  50 E is provided in the center bolt  114  which communicates hydraulic fluid between the relief valve  51  and the central aperture  50 A to a side of the seal  124  toward the first body end  46 . 
     A fourth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 5  having a similar construction to the tool assembly of  FIG. 2 , except for several aspects of the rotary actuator  40  and the tool attachment assembly  58  that will be described. In particular, the rotary actuator  40  shown in  FIG. 5  eliminates the use of the shaft nut  54  threadably attached the shaft  50  at the second body end  48  and instead uses an end cap  126  attached to the shaft by a central bolt  128 . The shaft second end portion  53 B at the second body end  48  has a threaded aperture  130  to threadably receive an exteriorly threaded portion  132  of the central bolt  128  and the end cap  126  has a central aperture  134  through which the central bolt passes. Tightening of the center bolt  128  applies a significant pre-stress/pre-load on the shaft  50  by placing the shaft second end portion  53 B in compression. As shown in  FIG. 5 , in this embodiment the second attachment flange  62  is directly bolted to the end cap  126  by the bolts  53 D without use of the intermediary retainer member  60 . The second attachment flange  62  has a central aperture  136  in which a head portion of the central bolt  128  is positioned. 
     The tool attachment assembly  58  of this fourth embodiment of the tool assembly  10  shown in  FIG. 5  has an end portion  138  of each of the front forks  72  spaced away from end thereof with the forward facing openings  72 A pivotally coupled to the support frame  64  at a location toward the rearward end portion  68  thereof. The forward end  86 B of the shaft  86  of the linear actuator  74  is pivotally coupled to a central portion  140  of each of the rear forks  72 . In such manner, the reciprocating movement of the piston  84  of the linear actuator  74  causes the shaft  86  to pivot the front forks about their point of pivotal connection to the support frame  64  and thereby move the ends of the front forks  72  with forward facing openings  72 A along a forward and rearward arcuate path. 
     The tool attachment assembly  58  of this fourth embodiment also has eliminated the fifth internal passageway IP 5  in the support frame  64 , and uses a hydraulic line  142  to connect the third internal passageway IP 3  in the first attachment flange  56  to the third fluid port P 3  of the linear actuator  74 , and a hydraulic line  144  to connect the fourth internal passageways IP 4  in the first attachment flange to the fourth fluid port P 4  of the linear actuator. 
     A fifth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 6 . In this embodiment, the shaft  50  of the rotary actuator  40  does not extend the full length of the body  42 , with the shaft first end portion  53 A ending inward of the first body end  46  and the shaft second end portion  53 B ending inward of the second body end  48 . A first end cap  146  is located at the first body end  46  partially within the body  42  and extending axially forward and outward beyond the body, and a second end cap  148  is located at the second body end  48  partially within the body  42  and extending axially rearward and outward beyond the body. The first and second end caps  146  and  148  each have a threaded central aperture  150  and  152 , respectively. A tie rod  154  extends with a threaded first end portion  156  and a threaded second end portion  158  extends between the first and second end caps  146  and  148 , with the threaded first end portion  156  threadably received in the threaded central aperture  150  of the first end cap and the threaded second end portion  158  threadably received in the threaded central aperture  152  of the second end cap. The threads of the threaded first end portion  156  of the tie rod  154  and the threaded central aperture  150  of the first end cap  146  being of an opposite hand thread than the threaded second end portion  158  of the tie rod and the threaded central aperture  152  of the second end cap  148 . In the illustrated embodiment, the threads of the threaded first end portion  156  of the tie rod  154  and the threaded central aperture  150  of the first end cap  146  are right hand threads, and the threads of the threaded second end portion  158  of the tie rod and the threaded central aperture  152  of the second end cap  148  are left hand threads. As a result, upon assembly of the rotary actuator  40 , the tie rod  154  when threaded into the first and second end caps  146  and  148  can be rotated in a single rotational direction which simultaneously draws the first and second end caps inward and into tight engagement with the shaft first and second end portions  53 A and  53 B to firmly clamp the shaft  50  between the first and second end caps to apply a significant axial pre-stress/pre-load force to shaft. Torque transmission between the shaft  50  and the end caps  146  and  148  is aided by matching radially oriented face grooves in the shaft and end caps. The tie rod  154  extends beyond the shaft first and second end portion  53 A and  53 B, and is longer than the shaft  50 . 
     In the embodiment of  FIG. 6 , the tie rod  154  is torqued, thereby preloading itself and the shaft  50 , but when the hydraulic pressure is cycled on and off the stress in the tie rod fluctuates a relatively small amount compared to the fluctuating hydraulic force but instead the force between the first and second shaft end portions  53 A and  53 B and the first and second end caps  146  and  148  fluctuates. This has to do with the different spring rates of the loaded components or in this case primarily the cross sectional difference of the tie rod  154  and the shaft  50 . 
     In this fifth embodiment of the tool assembly  10  shown in  FIG. 6  the support frame  64  of the tool attachment assembly  58  is rigidly attached to the body  42  of the rotary actuator  40  by first and second attachment members  160  and  162 , respectively, rather than being connected to the shaft  50  of the rotary actuator through the first and second attachment flanges  56  and  62  used in the embodiments described above. As will be described below, in this embodiment the shaft  50  is held stationary relative to the attachment brackets  88  by which the tool assembly  10  is detachably connected to the second arm  20  and the rotation link  24  of the vehicle  12 , and operation of the rotary actuator  40  causes the body  42  to rotate. Since the support frame  64  of the tool attachment assembly  58  is rigidly attached to the body  42  in this embodiment, operation of the rotary actuator  40  to rotate the body  42  thereof also rotates the tool attachment assembly  58  and hence any tool to which it is attached. 
     The first attachment member  160  extends between the first body end  46  of the rotary actuator  40  and the rearward end portion  66  of the support frame  64 , and the second attachment member  162  extends between the second body end  48  of the rotary actuator and the forward end portion  68  of the support frame. In the illustrated embodiment the attachment members  160  and  162  are body portions that integrally connect the body  42  of the rotary actuator  40  with the support frame  64  of the tool attachment assembly  58 . 
     In this embodiment, since the body  42  of the rotary actuator  40  is rigidly attached to the support frame  64 , the first and second attachment flanges  56  and  62  are not used to connect together the rotary actuator and the support frame  64  of the tool attachment assembly  58 . However, similar first and second attachment flanges  164  and  166  are used, although in effect to attach the shaft  50  of the rotary actuator  40  to the attachment brackets  88 . The first attachment flange  164  is positioned outward of the body  42  at the first body end  46  and the second attachment flange  166  is positioned outward of the body at the second body end  48 . The first attachment flange  164  is rigidly attached to the first end cap  146  by a plurality of circumferentially arranged bolts  168  (only two being illustrated in  FIG. 6 ), and the second attachment flange  166  is rigidly attached to the second end cap  148  by a plurality of circumferentially arranged bolts  170  (only two being illustrated in  FIG. 6 ). Both an upper end portion  172  of the first attachment flange  164  and an upper end portion  174  of the second attachment flange  166  are rigidly attached to the pair of attachment brackets  88  at spaced apart forward and rearward locations (as before described, the attachment brackets  88  detachably connect the tool assembly  10  to the second arm  20  and the rotation link  24  of the vehicle  12 ). As such, in this embodiment the shaft  50 , the end caps  146  and  148 , and the first and second flanges  164  and  166  are held stationary relative the attachment brackets  88 , rather than the body  42  of the rotary actuator  40 . Thus, during operation of the rotary actuator  40 , the shaft  50  is stationary and the body  42  of the rotary actuator rotates and laterally tilts the tool attachment assembly  58 . 
     In this fifth embodiment of the tool assembly  10  shown in  FIG. 6 , internal passageways are not used to communicate hydraulic fluid with the third and fourth ports P 3  and P 4  of the linear actuator  74 , instead the hydraulic lines L 3  and L 4  are connected directly to the third and fourth ports P 3  and P 4 , respectively. Further, the relief valve  51  is not used. 
     A sixth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 7  having a similar construction to the tool assembly of  FIG. 6 , however, without use of the tie rod  154  and with communication of hydraulic fluid more like described above for the tool assembly of  FIG. 2 . As with the embodiment of  FIG. 2 , in this sixth embodiment, the shaft  50  extends the full length of the body  42 , and has the flange portion  52  at the first body end  46  and the shaft nut  54  at the second body end  48 . As with the embodiment of  FIG. 6 , first and second attachment flanges  164  and  166  are used, with the upper end portions  172  and  174  thereof being rigidly attached to the pair of attachment brackets  88 , and with the first attachment flange rigidly attached to the flange portion  52  of the shaft  50  at the first body end  46  by a plurality of circumferentially arranged bolts  176  (only one being illustrated in  FIG. 7 ), and the second attachment flange  166  is rigidly attached to the shaft nut  54  at the second body end  48  by a plurality of circumferentially arranged bolts  178  (only two being illustrated in  FIG. 7 ). In effect, the shaft  50  of the rotary actuator  40  is attached to the attachment brackets  88  and held stationary relative the attachment brackets  88 , with the body  42  of the rotary actuator  40  being rotatable relative to the attachment brackets during operation of the rotary actuator  40  to laterally tilt the tool attachment assembly  58 . A plurality of circumferentially arranged bolts  180  (only two being illustrated in  FIG. 7 ) extend through threaded apertures in the second attachment flange  166  and extend inwardly to apply inward force on the outward end face of the shaft second end portion  53 B to apply an axial pre-stress/pre-load force to the shaft  50  and attachment brackets  88 . 
     Unlike in the embodiment of  FIG. 6 , in this sixth embodiment of  FIG. 7 , hydraulic fluid is not connected directly to the third and fourth ports P 3  and P 4  of the linear actuator  74 . Rather, hydraulic fluid is communicated to the third and fourth ports P 3  and P 4  of the linear actuator  74  by hydraulic lines L 3  and L 4 , respectively, using various passageways interior to the rotary actuator, the first attachment flange  164  and the support frame  64  without using additional exterior hydraulic lines. The hydraulic line L 3  is directly connected to a fifth port P 5  in the upper end portion  172  of the first attachment flange  164 , and the hydraulic line L 4  is directly connected to a sixth port P 6  in the upper end portion of the first attachment flange, located adjacent to the fifth port P 5 . The periphery of the shaft flange portion  52  of the shaft  50  of the rotary actuator  40  has first and second circumferential channels C 1  and C 2 . Fluid communication between the fifth and sixth ports P 5  and P 6  and the first and second circumferential channels C 1  and C 2  is accomplished by first and second internal passageways P 3  and P 4  in the first attachment flange  164 , and third and fourth internal passageways P 1  and P 2  in the shaft flange portion  52 . The first internal passageway IP 3  of the first attachment flange  164  has one end in communication with the fifth port P 5  and another end in communication with one end of the third internal passageway P 1  of the shaft flange portion  52  at a location at the interface of the outward end face of the shaft first end portion  53 A with the forward surface of the first attachment flange  164 . The other end of the third internal passageway IP 1  of the shaft flange portion  52  is in communication with the first circumferential channel C 1  at a location toward an upper side of the shaft flange portion  52 . Similarly, the second internal passageway IP 4  of the first attachment flange  164  has one end in communication with the sixth port P 6  and another end in communication with one end of the fourth internal passageway P 2  of the shaft flange portion  52  at a location at the interface of the outward end face of the shaft first end portion  53 A with the forward surface of the first attachment flange  164 . The other end of the fourth internal passageway IP 2  of the shaft flange portion  52  is in communication with the second circumferential channel C 2  at a location toward an upper side of the shaft flange portion  52 . 
     Fluid communication between the first and second circumferential channels C 1  and C 2  and the third and fourth ports P 3  and P 4  of the linear actuator  74  is accomplished by fifth and sixth internal passageways IP 5  and IP 6  in the body sidewall  44  of the rotary actuator  40  toward the first body end  46  of the body  42  located toward a lower side of the body adjacent to the rearward end portion  66  of the support frame  64  of the tool attachment assembly  58 . The sixth internal passageway IP 6  in part comprises an interiorly located tube welded in position and extending to the fourth port P 4 . The one end of the fifth internal passageway IP 5  in communication with the first circumferential channel C 1  at a location toward a lower side of the body  42  of the rotary actuator  40 , and the other end is in communication with the third port P 3  of the linear actuator  74 . The one end of the sixth internal passageway IP 6  in communication with the second circumferential channel C 2  also at a location toward a lower side of the body  42  of the rotary actuator  40 , and the other end is in communication with the fourth port P 4  of the linear actuator  74 . 
     In this sixth embodiment of the tool assembly  10  shown in  FIG. 7 , the hydraulic fluid is communicated to the first and second ports P 1  and P 2  of the rotary actuator  40  by hydraulic lines L 1  and L 2 , respectively, connected directly to the first and second ports P 1  and P 2  to control operation of the rotary actuator. The second port P 2  in this embodiment is located at the first body end  46  so a seventh internal passageways IP 7  in the shaft communicates hydraulic fluid between the second port P 2  and the fluid-tight compartment within the body  42  to a side of the piston head  96  toward the second body end  48 . The seventh internal passageways IP 7  is shown in  FIG. 7A  (the piston sleeve  90  has been deleted from  FIG. 7A ), as in the concentric arrangement of the cylindrical sidewall  44  of the body  42  of the rotary actuator  40  and the shaft  50  of the rotary actuator. 
     A seventh embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 8, 8A and 8B  having some aspects of its construction similar to the tool assembly of several previously described tool assemblies but with other differences. The sidewall  44  of the body  42  of the rotary actuator  40  of this embodiment has a first end body sidewall portion  44 A which is cylindrical in cross-section and extends from the first body end  46  to a body mid-portion, and a second end body sidewall portion  44 B which is non-cylindrical in cross-section and extends from the second body end  48  to the body mid-portion where the first and second end body sidewall portions are joined together. The interior sidewall surfaces of the first and second end body sidewall portions  44 A and  44 B are smooth. The piston head  96  of the piston sleeve  90  is disposed for reciprocation within only the non-cylindrical second end body sidewall portion  44 B and has a perimeter with a shape corresponding to the non-cylindrical second end body sidewall portion so as to be in sliding engagement therewith, in this case an oval as shown in  FIG. 8B . The sleeve portion  97  of the piston sleeve  90  is cylindrical in shape and has only outer helical splines  179  over a portion of its length. 
     The shaft  50  of the rotary actuator  40  in this seventh embodiment has an annular first end shaft portion  57  which is cylindrical in cross-section and extends from the shaft first end portion  53 A toward the second body end  48  about the same length as the first end body sidewall portion  44 A. The first end shaft portion  57  has a smooth exterior sidewall surface and is disposed in the smooth-walled, cylindrical first end body sidewall portion  44 A for rotation therewithin. The first end shaft portion  57  further has an end wall  180  toward the first body end  46  and an annular sidewall  181  defining an interior chamber  182  with an open end  183  facing toward the second body end  48 . The interior surface of the annular sidewall  181  has inner helical splines  185  which extend over a portion of its length. The sleeve portion  97  of the piston sleeve  90  extends within the interior chamber  182  of the first end shaft portion  57 , and outer helical splines  179  of the piston sleeve  90  which mesh with inner helical splines  185  of the first end shaft portion  57 . 
     The interior side of the end wall  180  has a first threaded recess  186  therein and a concentric second threaded recess  188 , with the second threaded recess being located inward of the first threaded recess and having a larger diameter. The shaft  50  further includes a reduced diameter center shaft portion  59  having a threaded first end portion  190  which is threadably received in the second threaded recess  188  of the end wall  180 , and a threaded second end portion  192  at the second body end  48  on which the shaft nut  54  is threadably attached. The center shaft portion  59  has an axially extending central aperture  194  which extends fully between the first end portion  190  and the second end portion  192  thereof. A center bolt  196  is disposed coaxially within the central aperture  194  of the center shaft portion  59 , and has a threaded end portion  198  which is threadably received in the threaded first recess  186  of the end wall  180 , and a head  200  which is sufficiently large to engage the annular outward end face of the second end portion  192  of the center shaft portion  59  at the second body end  48 . Tightening of the center bolt  196  into the threaded first recess  186  applies an axial pre-stress/pre-load force to the shaft  50 . 
     The piston sleeve  90  and the piston head  96  thereof has a circular center aperture through which the center shaft portion  59  extends. 
     The first and second attachment flanges  56  and  62  attached the tool attachment assembly  58  to the rotary actuator  40  much as described for the first embodiment of  FIG. 2 , except the bolts  53 D attach the retainer member  60  to the shaft nut  54  rather than directly to the shaft  50 . 
     With the arrangement of this seventh embodiment of  FIGS. 8, 8A and 8B , when hydraulic fluid under pressure is selectively applied to the first port P 1  or the second port P 2 , the piston head  96  will move longitudinally within the second end body sidewall portion  44 B, but the matching non-cylindrical shapes of the piston head and the second end body sidewall portion prevent the rotation of the piston head. Linear reciprocation of the piston head  96  within the second end body sidewall portion  44 B of the body  42  of the rotary actuator  40 , with the outer helical splines  179  of the sleeve portion  90  engaging and meshing with the inner helical splines  185  of the first end shaft portion  57 , causes rotation of the first end shaft portion  57  and the center shaft portion  59 . The rotational movement of the first end shaft portion  57  and the center shaft portion  59  is transmitted to the tool attachment assembly  58  which results in lateral tilting of the bucket  34  or other tool attached thereto to the right or left. 
     While the non-cylindrical piston head  96  of the piston sleeve  90  and the non-cylindrical second end body sidewall portion  44 B are only illustrated as being oval in cross-section, many other non-cylindrical shapes can be used for the piston head and second end body sidewall portion which allow linear sliding movement of the piston head within the second end body sidewall portion but yet limit rotational movement of the piston head within the second end body sidewall portion. These would include square, triangular and the like, and other non-cylindrical shapes. While matching cross-sectional shapes for the non-cylindrical piston head  96  of the piston sleeve  90  and the non-cylindrical second end body sidewall portion  44 B are described, these shapes do not have to have the same cross-sectional shape just so the shapes for each selected prevent the rotation of the piston head within the second end body sidewall portion  44 B as the piston head linearly reciprocates therein as the rotary actuator is operated under fluid power. 
     An eighth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 9, 9A and 9B  which also provides for rotation of the bucket  34  or other tool and well as lateral tilting thereof. Somewhat as in the third embodiment of  FIG. 4 , the shaft  50  of the rotary actuator  40  of this eighth embodiment has the axially extending central aperture  208  extending the full length of the shaft, and sized to receive the center bolt  114  therein to apply an axial pre-stress/pre-load force to the shaft  50 . As in the fifth embodiment of  FIG. 6 , in this eighth embodiment the shaft  50  is held stationary relative to the attachment brackets  88  by which the tool assembly  10  is detachably connected to the second arm  20  and the rotation link  24  of the vehicle  12 , and operation of the rotary actuator  40  causes the body  42  to rotate. 
     In this eighth embodiment, somewhat as with the seventh embodiment of  FIGS. 8, 8A and 8B , the sidewall  44  of the body  42  of the rotary actuator  40  has a first end body sidewall portion  44 A which is cylindrical in cross-section and extends from the first body end  46  to a body mid-portion, and a second end body sidewall portion  44 B which extends from the second body end  48  to the body mid-portion with an interior sidewall which is non-circular in cross-sectional shape and an exterior sidewall which is circular in cross-sectional shape. The shape of the interior and exterior sidewalls of the second end body sidewall portion  44 B are illustrated in  FIG. 9B . The interior sidewall surfaces of the first and second end body sidewall portions  44 A and  44 B are smooth, and the piston head  96  of the piston sleeve  90  is disposed for reciprocation within only the second end body sidewall portion  44 B and has a perimeter with a shape corresponding to the non-circular second end body sidewall portion so as to be in sliding engagement therewith, in this case an oval as shown in  FIG. 9B . The piston head  96  has a circular center aperture through which the shaft  50  extends. The sleeve portion  97  of the piston sleeve  90  is cylindrical in shape and only has inner helical splines  179 A over a portion of its length. 
     The shaft  50  of the rotary actuator  40  in this eighth embodiment is cylindrical in cross-section and extends through the piston sleeve  90  and the piston head  96  thereof. The exterior surface of the shaft  50  has outer helical splines  185 A which extend over a portion of its length and mesh with the inner helical splines  179 A of the piston sleeve  90 . 
     With the arrangement of this eighth embodiment of  FIGS. 9, 9A and 9B , when hydraulic fluid under pressure is selectively applied to the first port P 1  or the second port P 2 , the piston head  96  will move longitudinally within the second end body sidewall portion  44 B, but the matching non-circular shapes of the piston head and the second end body sidewall portion prevent the rotation of the piston head. Linear reciprocation of the piston head  96  within the second end body sidewall portion  44 B of the body  42  of the rotary actuator  40 , with the inner helical splines  179 A of the sleeve portion  90  engaging and meshing with the outer helical splines  185 A of the shaft  50 , causes rotation of the shaft  50 . The rotational movement of the shaft  50  is transmitted to the tool attachment assembly  58  which results in lateral tilting of the bucket  34  or other tool attached thereto to the right or left. 
     While the non-cylindrical piston head  96  of the piston sleeve  90  and the non-cylindrical second end body sidewall portion  44 B are illustrated as being oval in cross-section, many other non-cylindrical shapes can be used for the piston head and second end body sidewall portion which allow linear sliding movement of the piston head within the second end body sidewall portion but yet limit rotational movement of the piston head within the second end body sidewall portion. 
     In this eighth embodiment, instead of the tool attachment assembly  58  being positioned immediately below and attached to the rotary actuator  40 , the tool assembly  10  includes a turntable bearing assembly  210  positioned between the rotary actuator and the tool attachment assembly. The tool attachment assembly  58  is attached to the underside of the turntable bearing assembly  210  and moves therewith, including rotating with the turntable bearing assembly about an axis of rotation transverse to the axis of rotation of the rotary actuator  40  and being tilted laterally as the rotary actuator tilts the turntable bearing assembly laterally. With such an arrangement, the bucket  34  or other tool can be selectively laterally tilted about the axis of rotation of the rotary actuator  40 , or selectively rotated about the axis of rotation of the turntable bearing assembly  210 , or simultaneously both laterally tilted and rotated. 
     The turntable bearing assembly  210  includes a turntable bearing with a lower first member  212  to which the tool attachment assembly  58  is rigidly attached. The first turntable member  212  has teeth on its outer periphery for engaging a worm screw. An upper second turntable member  214  rotatably supports the first turntable member  212  therebelow and supports a hydraulic motor and worm screw such that the selective rotation of the hydraulic motor turns the worm screw which engages the teeth on the outer periphery of the first turntable member  212  to selectively rotate the first turntable member relative to the second turntable member  214  when the hydraulic motor is powered. This provides 360 degrees of continuous rotation. The second turntable member  214  is attached to the body  42  of the rotary actuator  40  for rotation therewith. 
     A ninth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 10 and 10A  which, as with the eighth embodiment provides for rotation of the bucket  34  or other tool as well as lateral tilting thereof. In this embodiment, a first end cap  146  is located at the first body end  46 , and a second end cap  148  is located at the second body end  48  partially within the body  42 . The first end cap  146  abuts the outward end face of the shaft first end portion  53 A. The second end cap  148  has a threaded central aperture  152  which threadably receives a threaded portion  55  of the shaft  50 . A tie rod  154  extends between and outward beyond the first and second end caps  146  and  148 , and has a threaded first end portion  156  axially outward of the first end cap  146  and a threaded second end portion  158  axially outward of the second end cap  148 . A nut  155  is threadably received on each of the threaded first and second end portions  156  and  158  of the tie rod  154 . Tightening the nuts  155  on the threaded first and second end portions  156  and  158  of the tie rod  154  applies an axial pre-stress/pre-load force to shaft. 
     As with the eighth embodiment, the ninth embodiment of  FIGS. 10 and 10A  includes a turntable bearing assembly  210  positioned between the rotary actuator  40  and the tool attachment assembly  58 , with the tool attachment assembly attached to the underside of the turntable bearing assembly  210  for movement therewith. As such, the tool attachment assembly  58  can be rotated by the turntable bearing assembly about an axis of rotation transverse to the axis of rotation of the rotary actuator  40  and tilted laterally as the rotary actuator tilts the turntable bearing assembly laterally. With such an arrangement, the bucket  34  or other tool can be selectively laterally tilted about the axis of rotation of the rotary actuator  40 , or selectively rotated about the axis of rotation of the turntable bearing assembly  210 , or simultaneously both laterally tilted and rotated. 
     A tenth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 11  which provides for rotation of a bucket or other tool as well as lateral tilting thereof. In this embodiment a hydraulically operated jaw bucket  218  is attached to and below the turntable bearing assembly  210 . The rotary actuator  40  and the tool attachment assembly  58  used in the tenth embodiment may be of the construction used in embodiment 8 or embodiment 9, or any of the other previously described embodiments or variations thereof. Similarly, the construction of the turntable bearing assembly  210  may be as described for embodiments 8 and 9, or any other suitable construction. The jaw bucket  218  is of a construction much as described in U.S. Pat. No. 6,612,051 and includes a bucket portion  220  and a jaw portion  222 , with the bucket portion supporting a jaw bucket rotary actuator  224  for pivotal movement if the jaw portion relative to the bucket portion. The body of the jaw bucket rotary actuator  224  is rigidly attached to the bucket portion  220  and the shaft of the jaw bucket rotary actuator is rigidly attached to the jaw portion  22 , allowing the jaw portion to be selectively rotated relative to the bucket portion about a transverse axis of rotation. 
     In addition to the hydraulic fluid required to operate the rotary actuator  40 , the tool attachment assembly  58  and the turntable bearing assembly  210 , hydraulic fluid must be supplied to the jaw bucket rotary actuator  224 . A plurality of hydraulic lines L 10  extending along the second arm  20  of the vehicle  12  supply the hydraulic fluid to tool assembly  10  of  FIG. 11 . Several of the hydraulic lines L 10  terminate at a first member of a conventional automatic first oil line quick connect  226 . Another plurality of hydraulic lines L 12  extend from a second member of the first oil line quick connect  226  which is separable from the first member thereof and when connected to the first member each of the hydraulic lines L 12  is in fluid communication with one of the hydraulic lines L 10 . The first oil line quick connect  226  allows for remote connection and disconnection of the first and second members thereof automatically as the tool assembly  10  is connected and disconnected from the second arm  20  and rotation link  24  of the vehicle  12 . Some of the hydraulic lines L 12  supply hydraulic fluid to the ports of the rotary actuator  40 , the tool attachment assembly  58  and the turntable bearing assembly  210 , in one of the manners described herein or a suitable alternative manner. A pair of the hydraulic lines L 12  extend to the jaw bucket  218  for controlling the jaw bucket rotary actuator  224 , and terminate at a first member of a conventional automatic second oil line quick connect  228 . A pair of hydraulic lines L 14  extend from a second member of the second oil line quick connect  228  which is separable from the first member thereof and when connected to the first member each of the hydraulic lines L 14  is in fluid communication with one of the pair of hydraulic lines L 12  for controlling the jaw bucket rotary actuator  224 . The second oil line quick connect  228  allows for remote connection and disconnection of the jaw bucket  218  or another tool automatically as the jaw bucket or other tool assembly is connected and disconnected from the tool attachment assembly  58 . 
     An eleventh embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 12, 12A and 12B . The rotary actuator  40  and the tool attachment assembly  58  used in this eleventh embodiment are very similar to those of the embodiment of  FIG. 2 . Shown attached to and below the tool attachment assembly  58  is a rotatable grapple assembly  230  having a first grapple member  232  and an opposing second grapple member  234 . The grapple assembly  230  includes a grapple rotary actuator  236  with an elongated body having at a longitudinal upper end thereof a shaft end flange  237  projecting upward beyond the end of the body. A pair of clevis pins  238 , much like the pins  36 A and  38 A of the first and second clevises  36  and  38  of the conventional bucket  34  described above, are attached to the shaft end flange  237  and provide for releasable attachment of the grapple assembly  230  to the tool attachment assembly  58  as described above for buckets and other tools. The longitudinal lower end of the elongated body of the grapple rotary actuator  236  has the first and second grapple members  232  and  234  rotatably attached thereto, each by a pivot pin  240 . Each of the first and second grapple members  232  and  234  has an extendable hydraulic cylinder  242  extending between the grapple member and the body of the grapple rotary actuator for selective rotation of the grapple member about its pivot pin  240  such that the first and second grapple members may be rotated between a fully open position as shown in  FIG. 12 , and a full closed position with the distal tips of the first and second grapple members moved together. Hydraulic fluid supplied to the grapple rotary actuator  236  results in relative rotation between the body and shaft of the grapple rotary actuator, and hence rotation of the first and second grapple members  232  and  234  pivotally attached to the body about a longitudinal axis of the grapple rotary actuator. 
     Operation of the rotary actuator  40  of the tool assembly  10  produces lateral tilting of the grapple assembly  230 , operation of the grapple rotary actuator  236  produces rotational movement of the first and second grapple members  232  and  234  about the grapple rotary actuator longitudinal axis, and operation of the hydraulic cylinders  242  produces relative movement between the first and second grapple members  232  and  234 . This requires hydraulic fluid be supplied to the rotary actuator  40 , the tool attachment assembly  58 , grapple rotary actuator  236  and the hydraulic cylinders  242 , as well as hydraulic fluid to the tool attachment assembly  58  to release and attach the grapple assembly  230  to the tool attachment assembly. 
     Fluid is supplied to the tool attachment assembly  58  much as with the embodiment of  FIG. 2 , with fluid communication between the first and second circumferential channels C 1  and C 2  and the third and fourth ports P 3  and P 4  of the linear actuator  74  accomplished by first and second internal passageways IP 1  and IP 2  in the shaft flange portion  52 , and third and fourth internal passageways IP 3  and IP 4  in the first attachment flange  56 . However, as best illustrated in  FIG. 12B , in the eleventh embodiment of the tool assembly  10 , the third and fourth internal passageways IP 3  and IP 4  communicate with seventh port P 7  and eighth port P 8 , respectively. A hydraulic line L 5  extends between the seventh port P 7  and the third port P 3  of the linear actuator  74  of the tool attachment assembly  58 , and a hydraulic line L 6  extends between the eighth port P 8  and the fourth port P 4  of the linear actuator of the tool attachment assembly. 
     To supply fluid to the grapple assembly  230 , the rotary actuator  40  of this eleventh embodiment includes an annular oil gland member  244  mounted coaxially within the body  42  at the second body end  48  for rotation with the shaft  50  which extends through a central aperture  246  of the oil gland member. The central aperture  246  of the oil gland member  244  has inner straight splines  248  which mesh with outer straight splines  250  of an end portion of the shaft  50 . The oil gland member  244  is held in axial position within the body  42  between an inner shoulder  252  of the body sidewall  44  and the shaft nut  54 . In this eleventh embodiment the second attachment flange  62  is bolted directly to the oil gland member  244  by a plurality of circumferentially arranged bolts  53 F. 
     Fluid to control the operation of the grapple rotary actuator  236  to rotate the grapple assembly  230  clockwise is supplied by a hydraulic line L 16  to a ninth port P 9  in the body sidewall  14  at the location of the oil gland member  244 , and to rotate the grapple assembly counterclockwise is supplied by a hydraulic line L 18  to a tenth port P 10  in the body sidewall at the location of the oil gland member. Fluid to control the operation of the hydraulic cylinders  242  to close the first and second grapple members  232  and  234  is supplied by a hydraulic line L 20  to an eleventh port P 11  in the body sidewall  14  at the location of the oil gland member  244 , and to open the first and second grapple members is supplied by a hydraulic line L 22  to a twelfth port P 12  in the body sidewall at the location of the oil gland member. 
     The periphery of the oil gland member  244 , at locations radially inward from the ninth and tenth ports P 9  and P 10 , has third and fourth circumferential channels C 3  and C 4 , which are in fluid communication with the ninth and tenth ports, respectively, as shown in  FIG. 12B . The interior wall of the sidewall  44  of the body  42 , at locations radially inward from the eleventh and twelfth ports P 11  and P 12 , has fifth and sixth circumferential channels C 5  and C 6 , which are in fluid communication with the eleventh and twelfth ports. 
     Fluid communication between the third, fourth, fifth and sixth circumferential channels C 3 , C 4 , C 5  and C 6  and the grapple rotary actuator  236  and the hydraulic cylinders  242  is accomplished by internal passageways and hydraulic lines. The third, fourth, fifth and sixth circumferential channels C 3 , C 4 , C 5  and C 6  are in communication with eighth, ninth, tenth and eleventh internal passageways IP 8 , IP 9 , IP 10  and IP 11  in the oil gland member  244  at a location toward a lower side of the shaft  50  of the rotary actuator  40 . The eighth, ninth, tenth and eleventh internal passageways IP 8 , IP 9 , IP 10  and IP 11  communicate through the second attachment flange  62  with a first member of a conventional automatic third oil line quick connect  254 . The first member is bolted to the second attachment flange  62  with bolt  53 G. A plurality of hydraulic lines L 24  (see  FIG. 12 ) extend from a second member of the third oil line quick connect  254  which is separable from the first member thereof and when connected to the first member each of the eighth, ninth, tenth and eleventh internal passageways IP 8 , IP 9 , IP 10  and IP 11  is in fluid communication with one of the hydraulic lines L 24  which extend to the grapple assembly  230 . The hydraulic lines L 24  communicating fluid to the hydraulic cylinders  242  are connected to a corresponding one of the hydraulic lines L 26 . One of the hydraulic lines L 24  communicating fluid to the grapple rotary actuator  236  is connected to a hydraulic line L 27 . Table  1  forming a part of  FIG. 12  outlines the fluid connections using reference numerals in circles to identify the various ports and lines shown in  FIG. 12  which control clockwise and counterclockwise rotation of the rotary actuator  40  to tilt the tool assembly of  FIG. 12 , retraction and extension of the linear actuator  74  of the tool attachment assembly  58 , clockwise and counterclockwise rotation of the grapple rotary actuator  236  of the grapple assembly  230 , and extension and retraction of the hydraulic cylinders  242  to close and open the first and second grapple members  232  and  234  of the grapple assembly  230 . The third oil line quick connect  254  allows for remote connection and disconnection of the first and second members thereof automatically as the grapple assembly  230  or another tool is connected and disconnected from the tool attachment assembly  58 . 
     A twelfth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 13  with the rotary actuator  40  similar to that of the embodiment of  FIG. 2 . In this embodiment a rotary oil gland  256  is externally mounted to the retainer member  60 . The oil gland  256  has a cylindrical inner member  258  which is securely bolted to the retainer member  60  for rotation with the shaft  50  by bolt  53 H, and an annular outer member  260  which is rotatably mounted to the inner member  258 . The hydraulic lines L 3  and L 4  which supply fluid to the third and fourth ports P 3  and P 4 , respectively, of the linear actuator  74  of the tool attachment assembly  58  are connected to a thirteenth port P 13  and a fourteenth port P 14  in the outer member  260  of the oil gland  256 . The periphery of the inner member  258 , at a location radially inward from the thirteenth and fourteenth ports P 13  and P 14 , has seventh and eighth circumferential channels C 7  and C 8  which are in fluid communication with fifteenth and sixteenth ports P 15  and P 16 , respectively, of the axially outward face of the inner member. A hydraulic line L 28  connects the fifteenth port P 15  to the third port P 3  of the linear actuator  74 , and a hydraulic line L 30  connects the sixteenth port P 16  to the fourth port P 4  of the linear actuator. 
     A thirteenth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 14  with the rotary actuator  40  similar to that of the embodiment of  FIG. 2 . Again, in embodiment a rotary oil gland  262  is externally mounted although in position between the second attachment flange  62  and the shaft nut  54 . The oil gland  262  has a cylindrical inner member  264  which is held in place for rotation with the shaft  50  by bolts  53 I which extend through the second attachment flange  62  and the inner member  264 , and are threadably received by the shaft nut  54 . The hydraulic lines L 3  and L 4  which supply fluid to the third and fourth ports P 3  and P 4 , respectively, of the linear actuator  74  of the tool attachment assembly  58  are connected respectively to a thirteenth port P 13  and a fourteenth port P 14  in the outer member  266  of the oil gland  262 . The periphery of the inner member  264 , at a location radially inward from the thirteenth and fourteenth ports P 13  and P 14 , has seventh and eighth circumferential channels C 7  and C 8  which are in fluid communication with fifteenth and sixteenth ports P 15  and P 16 , respectively, of the axially outward face of the inner member via twelfth and thirteenth internal passageways IP 12  and IP 13 , respectively, of the inner member  264  of the oil gland  262 . The twelfth and thirteenth internal passageways IP 12  and IP 13  communicate with fourteenth and fifteenth internal passageways IP 14  and IP 15  of the second attachment flange  62 , respectively. The hydraulic line L 28  connects the fourteenth internal passageway IP 14  to the third port P 3  of the linear actuator  74 , and the hydraulic line L 30  connects the fifteenth internal passageway IP 15  to the fourth port P 4  of the linear actuator. 
     A fourteenth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 15 and 15A  with the rotary actuator  40  similar to that of the twelfth embodiment of  FIG. 13 . However, in this embodiment, two rotary oil gland  268  and  270  are non-coaxially, externally mounted to the axially outward face of the second attachment flange  62  retainer member  60 . The hydraulic lines L 3  and L 4  which supply fluid to the third and fourth ports P 3  and P 4 , respectively, of the linear actuator  74  of the tool attachment assembly  58  are connected to the oil glands  268  and  270 , respectively, which communicate with the fifteenth and sixteenth ports P 15  and P 16  which pass fully between the outward face and the inward face of the second attachment flange  62  at adjacent locations below the body  42  of the rotary actuator  40 . The hydraulic line L 28  connects the fifteenth port P 15  to the third port P 3  of the linear actuator  74 , and the hydraulic line L 30  connects the sixteenth port P 16  to the fourth port P 4  of the linear actuator. 
     A fifteenth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIG. 16  with the rotary actuator  40  similar to that of the embodiment of  FIG. 2 . In this embodiment a rotary oil gland member  272  is externally mounted to the axially outward face of the second attachment member  62 , in coaxial arrangement with the shaft  50 , by a bolt  53 J which is also coaxial with the shaft. A bearing  274  is positioned between the head of the bolt  53 J and the axially outward face of the oil gland member  272  so that while the oil gland member is held firmly against the axially outward face of the second attachment member  62  its is able to rotate relative to the second attachment member as the shaft  50  rotates the second attachment member. The hydraulic lines L 3  and L 4  which supply fluid to the third and fourth ports P 3  and P 4 , respectively, of the linear actuator  74  of the tool attachment assembly  58  are connected to the thirteenth port P 13  and the fourteenth port P 14  in the sidewall of the oil gland member  272 . A sixteenth internal passageway IP 16  extends between the thirteenth port P 13  and the axially inward face of the oil gland member  272 , and a seventeenth internal passageway IP 17  extends between the fourteenth port P 14  and the axially inward face of the oil gland member. The sixteenth internal passageway IP 16  communicates with an eighteenth internal passageway IP 18  in the second attachment member  62 , which in turn communicates with the hydraulic line L 28  connected to the third port P 3  of the linear actuator  74 . The seventeenth internal passageway IP 17  communicates with a nineteenth internal passageway IP 19  in the second attachment member  62 , which in turn communicates with the hydraulic line L 30  connected to the fourth port P 4  of the linear actuator  74 . Seals are provided between the axially outward face of the second attachment member  62  and the axially inward face of the oil gland member  272  to prevent fluid leakage. 
     A sixteenth embodiment of the fluid-powered, laterally tiltable tool assembly  10  is shown in  FIGS. 17 and 17A  with the rotary actuator  40  similar to that of the embodiment of  FIG. 2 . Much as with the embodiment of  FIG. 2 , internal passageways are used to communicate the fluid supplied by the hydraulic lines L 3  and L 4  to the third and fourth ports P 3  and P 4  of the linear actuator  74  of the tool attachment assembly  58 ; however, in this sixteenth embodiment the internal passageways are not located in the first attachment flange  56 . In particular, the periphery of the shaft flange portion  52  of the shaft  50  of the rotary actuator  40 , at a location radially inward from the fifth port P 5 , has the first circumferential channel C 1  which is in fluid communication with the fifth port P 5 . Similarly, periphery of the shaft flange portion  52  of the shaft  50  of the rotary actuator  40 , at a location radially inward from the sixth port P 6 , has the second circumferential channel C 2  which is in fluid communication with the sixth port P 6 . 
     Fluid communication between the first and second circumferential channels C 1  and C 2  and the third and fourth ports P 3  and P 4  of the linear actuator  74  is accomplished by twentieth and twenty-second internal passageways IP 20  and IP 22  in the shaft flange portion  52  of the shaft  50  which communicate with fittings  276  and  278 , respectively, in the portion sidewall of the shaft flange portion  52  which extends rearwardly beyond the first body end  46  of the body  42  of the rotary actuator  40  at a location toward a lower side of the shaft. The hydraulic line L 28  connects the fitting  276  to the third port P 3  of the linear actuator  74  of the tool attachment assembly  58 , and the hydraulic line L 30  connects the fitting  278  to the fourth port P 4  of the linear actuator. 
     The piston sleeve  90  of this sixteenth embodiment uses an oval piston head  96  and a matching oval body sidewall  44  (the sidewall being shown in cross-section in  FIG. 17A ). As such, the piston sleeve  90  does not use outer splines for meshing with the inner splines of the body sidewall  44  to prevent rotation therebetween as the piston head  96  reciprocates within the body  42  when the rotary actuator  40  is operated, since engagement of the non-circular in cross-sectional shape of the piston head  96  of the piston sleeve  90  with the similarly shaped non-circular in cross-sectional interior sidewall surface of the body sidewall  44  prevents the rotation of the piston sleeve relative to the body. While the non-cylindrical piston head  96  of the piston sleeve  90  and the non-cylindrical body sidewall  44  are illustrated as being oval in cross-section, many other non-cylindrical shapes can be used for the piston head and body sidewall portion which allow linear sliding movement of the piston head within the body sidewall but yet limit rotational movement of the piston head within the body sidewall. 
     It will be appreciated that, although specific embodiments of the invention have been described herein for purposes of illustration, various modifications may be made without departing from the spirit and scope of the invention. Accordingly, the invention is not limited except as by the appended claims.