Abstract:
A pivotable arch structure (18) having an integral log bunk (30) is pivotable at one end (P) thereof relative to a main frame (15). The log bunk (30) includes several longitudinally arranged bunk webs (36) which are bolstered by laterally arranged support beams (38) connected thereto. A bumper (40) is arranged adjacent the end of the bunk webs (36) near the pivot axis (22). The longitudinal disposition of the bunk webs (36) promotes longitudinal log travel thereon while the bumper (40) guides logs initially engaged therewith in a direction to promote their subsequent engagement with the bunk webs (36). The longitudinally arranged bunk webs (36) also provide high operator visibility for various pivotal positions of the arch structure (18).
Abstract:
Des véhicules mobiles, tels que des chariots élévateurs, sont montés en général sur des paires de roues avant et arrière à des fins de locomotion. Les roues arrières sont directionnelles pour déplacer le chariot dans diverses positions de travail. Cependant, le rayon de braquage et la capacité de manoeuvre des véhicules de ce type sont limités, en particulier lorsqu'un véhicule de ce genre travaille dans des allées étroites. Le véhicule (10) de la présente invention comprend un assemblage de châssis (13), une pluralité de roues (72, 74) montées sur l'assemblage de châssis (13) avec un mouvement universel autour d'un point de pivotement (110), et un système de support et d'entraînement (70) pour entraîner les roues (72, 74) et positionner de manière infinie les roues (72, 74) par rapport à une surface de support (11) pour déplacer le véhicule (10) dans une direction quelconque choisie.
Abstract:
La présente invention permet d'éliminer les désavantages des solénoïdes de l'art antérieur, ne pouvant développer une force initiale de traction adéquate pour une taille de bobine donnée. Le solénoïde possédant une course de traction linéaire comprend un plongeur actionné par la bobine (16) possédant un couplage de perte de travail (20, 28, 32, 38, 40) pouvant être relié à une charge de manière à permettre au plongeur (16) de reculer sur une distance prédéterminée pendant la partie initiale de la course de manière à développer un niveau plus élevé de force de traction avant de transmettre une force substantielle à la charge. Le plongeur (16) comprend un corps allongé (18) possédant une liaison en forme de piston (28) montée de manière coulissante dans une cavité (20) à une extrémité du corps (18) et pouvant être couplée à la charge. Un ressort (36) emprisonné entre la liaison (28) et le corps (18) ramène la liaison (28) à sa position initiale par rapport au corps (18) avant la fin de la course de traction.
Abstract:
Earthmoving vehicles are often provided with a linkage arrangement on one end that is utilized to manipulate a work implement, such as a loader bucket. The linkage typically includes a tilting arrangement for the bucket that incorporates a tilt lever that is mounted to a lift arm that supports the bucket. The mounting between the tilt lever and the lift arm is normally of a complex nature requiring multiple bearing surfaces and lubrification means. Others may have a structure that requires exact positioning between the relative components or a failure will occur due to improper loading. The linkage arrangement (10) of the present invention provides a mounting member (82) that is attached to only one of the tilt levers (56, 58). It also includes an axial motion limiter (84) that is attached to the other tilt lever (56, 58). In doing so, a very simple and economical mounting device (62) is provided. The mounting device (62) also allows the tilt levers (56, 58) to rotate with respect to each other so that each of the levers (56, 58) function to bear a portion of the loading.
Abstract:
Turbocompound engines recover power from the exhaust exiting a turbocharger. Turbocompounding of known engines feed the power back into the flywheel at the rear of the engine requiring new and expensive regearing of the starter gear or ring gear on the flywheel. Maintenance or servicing of the compound components at the rear of the engines is difficult. The invention comprises a turbocompound engine (10) in which power is fed into the timing gears (16, 18, 20) of the engine (10). The mechanism for transmitting power (30) includes a driving mechanism (32), a fluid coupler mechanism (34) and a connecting mechanism (36) attached to the timing gears (16, 18, 20). Thus the disclosed invention uses existing timing gears (16, 18, 20) which are already machined and designed for continual load carrying capacity. The compound portion of the turbocompound engine (10) is located near the front and top of the engine allowing for excellenty maintenance and serviceability.
Abstract:
A method of forming a windowed unitary panel (10) having a peripheral edge portion (14) of a windowpane of glazing (12, 13) integrally embedded within a frame (11) of high modulus plastic material includes heating the pane to a preselected temperature prior to its being positioned within a mold. The peripheral edge portion of the windowpane protrudes into the mold cavity so that the high modulus plastic material forming the frame encapsulates the peripheral edge portion. This prevents buckling of the windowpane since the preheated windowpane contracts simultaneously with the contraction of the rigid frame as it cools from the molding temperature to ambient.
Abstract:
A countershaft transmission (10) provides at least three forward and three reverse speeds and includes a first countershaft (22) having a second gear (126) secured thereto, a third gear (130) rotatable thereon, and a first clutch (152) for connecting the third gear thereto. A second countershaft (24) has a fourth gear (196) secured thereto which is intermeshed with the second gear (126), a fifth gear (198) rotatable thereon, a sixth gear (200) rotatable thereon, a seventh gear (210) secured thereto, a second clutch (202) for connecting the fifth gear (198) thereto, and a third clutch (204) for connecting the sixth gear (200) thereto. A first gear (118) is adapted to drive one of the side-by-side third and fifth gears (130, 198), and a third countershaft (26) is disposed elevationally below them. The third countershaft (26) has an eighth gear (222) secured thereto which is intermeshed with the sixth gear (200). Ninth and tenth gears (228, 232) are rotatable on the third countershaft and are selectively connected thereto by a fourth clutch (230) and a fifth clutch (234) respectively. The five rotating clutches are of the interleaved plate type, are hydraulically engaged and mechanically disengaged, and are generally internested between the walls (46, 62) of the housing (12) for compactness. Up to eight forward and four reverse speeds can be obtained with but minor alterations.
Abstract:
A rotor balancing arrangement for use in a distribution valve (14) to ensure hydrostatic balancing of a rotor (42) located in the distribution valve (14). Some balancing arrangements provide areas equally spaced around the peripheral surface, each being exposed to the same pressure, however, they are limited to valves which rotate only through a limited arc of rotation. Other valves which rotate provide balancing grooves around portions of the peripheral surface but do not provide any control for the pressure that migrates axially in both directions along the peripheral surface of the rotor. In the subject arrangement, pressure fields (56, 57) of a predetermined size are located on a peripheral surface (52) of a rotor (42) circumscribing first and second outlet ports (45, 46) which open to opposite sides of the rotor (42). The size of the pressure fields (56, 57) is determined by the relationship of the diametrical clearance between the rotor (42) and a bore (31) with respect to the operating pressure of the system. This arrangement ensures that the differential forces acting on opposite sides of the rotor are minimized thus eliminating rotor sticking.
Abstract:
Compression relief valves are connected to compression chambers of engines and compressors. Adding a manual relief feature to known automatic compression relief valves involve increased complexity and requires high manual effort to overcome the high automatic spring force. The subject compression relief valve includes an automatic relief valve (74) which is activated by an excessive pressure within the compression chamber (12) and a manual relief valve (90) which is actuated independently of the automatic relief valve (74). The automatic valve (74) relieves the excessive pressure within the chamber (12) when the pressure within the chamber (12) overcomes the high force of the spring (88), unseating the valve element (76, 134) from the seat (42) and allowing the excess pressure to enter a bore (44) in the body and escape through a radial passage (46), an annular chamber (40) and a passage (24) to the atmosphere. The manual valve (90) is actuated by manually moving a handle (112) against a low effort spring (122) to an open position. At the open position the chamber (12) is vented through passages (50, 94, 96) or through passage (132, 138) into an annular chamber (40) and out a passage (24) to the atmosphere. The handle (112) can also be rotated and locked in the open position. Thus the chamber (12) is relieved of excessive pressure exceeding a predetermined level by the automatic valve (74) and is selectively vented with the manual valve (90). The subject compression relief valve provides a manual relief valve (90) requiring a low effort to actuate and an automatic relief valve (74) to relieve excessive pressure from a chamber (12). The manual valve (90) and the automatic valve (74) are coaxial to reduce the complexity of the compression relief valve.
Abstract:
Roller suspension apparatus are useful for example in belted vehicles. The heretofore known roller suspension apparatus impart a shear force to the spring due to the geometry and the relationship between the roller mounting arms, the walking beam, and the pivot pins to which the arms and beam are pivoted. The subject roller suspension apparatus has a pair of arms (34, 36) and a force transmitting beam (40) pivotally connected to a single pivot shaft (32). The mounting surfaces (46, 50, 51) to which a pair of springs (42) are attached are then arranged relative to the pivot shaft such that substantially only compressive forces are imparted to the springs. Thus, the full shock absorbing potential of the springs is fully utilized.