HYDRAULIC DRIVING DEVICE FOR STEERING WHEEL OF DUMP TRUCK

Abstract: A hydraulic driving device for the steering wheel of a dump truck in which a hydraulic motor can be mounted and/or dismounted therefrom after it has been assembled to thereby make the size of the hydraulic motor larger. A driving shaft (20) is rotatably supported on a supporting shaft portion (7) of a receiving seat (6) supported by a yoke (5), and a steering wheel (2) is rotatably mounted on the outer circumference of this supporting shaft portion (7). The steering wheel (2) and one end of the driving shaft (20) are coupled together via a speed reduction mechanism (27), and the motor main body (33) of a hydraulic motor (32) is mounted by means of a bolt (34) on the supporting shaft portion (7) in a position opposite to the steering wheel (2). The rotating shaft (35) of the motor is caused to protrude inside the supporting shaft portion (7) so as to be coupled to the other end of the driving shaft (20), whereby it is possible to mount or dismount the motor (32) by tightening or loosening the bolt (34).

Description: The present invention is related to a hydraulic drive system for driving a steerable wheel of a dump truck by means of a hydraulic motor. As a system for driving a steerable wheel of a traveling vehicle, a system disclosed in Japanese Examined Patent Publication (Kokoku) No. 48-42136, for example, has been known. Namely, a hollow drum shaped housing is pivotally supported on a yoke. A vehicular wheel is rotatably supported on the outer periphery of the housing. An output side of a hydraulic motor which is provided within the housing is connected to a vehicular wheel side via a reduction mechanism so that the vehicular wheel can be rotatingly driven by the hydraulic motor, and in conjunction therewith, the vehicular wheel can be rocked about the yoke together with the hydraulic motor. In such drive system for the steerable wheel, since the hydraulic motor is disposed within the hollow drum shaped housing supported on the yoke, the yoke may obstruct for removal and mounting of the hydraulic motor. Once assembled, the hydraulic motor cannot be mounted and removed. Also, the hydraulic motor necessarily becomes small. GB-A-1 239 743 discloses a fluid operable motor that is used for driving an individual propulsion wheel. A housing of the motor has a pair of trunnions which are supported in bearings at the outer end of a pair of pivotal links forming part of the front suspension of the vehicle. Moreover, an integral cylindrical extension of the housing is used for supporting an output shaft of the motor. This shaft is connected by means of a coupling to an input shaft of a reduction gear. The reduction gear is a planetary gear type reduction mechanism. A detachable cap is a part of the housing and is connected to an arm for connection to a drag link of the vehicle steering mechanism. Furthermore, the hydraulic motors may derive their motor fluid from a common pump. DE-A-3 045 250 discloses a steering circuit and a transmission hydraulic circuit connected by a shift valve. During normal operation a pump supplies hydraulic fluid via a directional-control valve to a steering cylinder. In case the pump fails an emergency supply for steering is provided by a shift valve in a first position which is connected to the hydraulic transmission circuit with a line and to back-pressure valves. The hydraulic transmission circuit comprises a second pump driven by an engine of the vehicle and a hydraulic motor which are connected by two lines. A setting pump controls the vehicle speed and supplies hydraulic fluid to the hydraulic motor via two alternative lines for driving or braking. In case of emergency the higher pressure of one line is supplied to another line via the back-pressure valves and via a further line to the directional-control valve. FR-A-2 293 638 discloses a hydraulic motor that is detachably fixed to a support element. A shaft of the motor is protruding and rotatably connected to a drive axle by a coupling connection. This connection can be braked by a brake comprising a braking member pressed against an inner surface of a drum. Further, a suspension system is disclosed which is fixed whereby a wheel supported by such suspension system is not a steerable wheel. The hydraulic motor is directly supported on a frame member which is a part of the vehicular framework. US-A-3 780 820 discloses a rotary clutch that transmits torque from a clutch shaft to a planetary shaft. Torque is transmitted by the latter shaft through a planetary gear train to a drive wheel in a direction determined by the direction of flow of fluid through the wheel motor. The rotary clutch means includes a fluid-activated and cooled disc-type friction clutch pack connected to the clutch shaft extending through the wheel motor cartridge and terminating at its rear end at a clutch piston. FR-A-2 469 296 discloses a clutch mechanism between an output site of a reduction mechanism and a steerable wheel. The clutch mechanism comprises hydraulically operable cylinders with pistons for displacing an engagement element in engagement with a fork-like element. If these two elements are in engagement the rotation of a shaft is transmitted to a wheel hub via two planetary gear type reduction mechanisms. In view of the prior art it is an object of the present invention to provide a mounting structure of a hydraulic drive system for a steerable wheel which easily facilitates assembling and disassembling of the hydraulic drive system. This object is solved according to the features of independent claim 1. The hydraulic motor is externally exposed for permitting external access. According to the invention, since the hydraulic motor is mounted on the receptacle seat at the opposite side of the steerable wheel, the hydraulic motor can be easily detached and attached even after assembling. Also, the greater hydraulic motor can be employed. Also, since the auxiliary hydraulic pump is driven at a speed synchronous with the drive wheel so that the discharge amount is proportional to the speed of the drive wheel, the steerable wheel can be driven at a speed synchronous with the drive wheel. Also, since steering operation can be performed by supplying the discharged pressurized fluid of the auxiliary hydraulic pump to the steering circuit when the discharge amount of the main hydraulic pump is small, the auxiliary hydraulic pump may function as an emergency steering pump. According to features of subclaims, by disengagement of the clutch mechanism, the steerable wheel can be placed in a state of free rotation. When a fluid flow amount in the drive circuit is large, the valve is switched so as not to supply the pressurized fluid to the clutch mechanism, the steerable wheel automatically situated into the state of the free rotation at high speed traveling. Since the rotation of the steerable wheel is not transmitted to the reduction mechanism by disconnecting the clutch mechanism, the duration of the reduction mechanism can be improved. The above-mentioned and other objects, aspects and advantages will become clear to those skilled in the art by the preferred and practical embodiment consistent with the principle of the invention, which will be discussed and illustrated in connection with the accompanying drawings. Fig. 1 is a side elevation of a dump truck to which a hydraulic drive system for a steerable wheel according to the present invention is applicable; Fig. 2 is a fragmentary perspective view of a frame work of the dump truck; Fig. 3 is a plan view of a steerable wheel mounting portion according to the present invention; Fig. 4 is a front elevation of the steerable wheel mounting portion; Fig. 5 is a section showing the first embodiment of a hydraulic motor mounting portion ; Fig. 6 is a schematic diagram of a drive system; Fig. 7 is a hydraulic circuit diagram; Fig. 8 is a section showing the second embodiment of the hydraulic motor mounting portion; Fig. 9 is a hydraulic circuit diagram; Fig. 10 is a section showing the third embodiment of the hydraulic motor mounting portion; and Fig. 11 is a section showing the fourth embodiment of the hydraulic motor mounting portion. The present invention will be discussed hereinafter in detail with reference to the drawings. As shown in Fig. 1 , a dump truck for a construction machine is constructed by providing steerable wheels 2 at the front portion of a vehicle body 1 , drive wheels 3 at the rear portion of the vehicle body, and a vessel 4 in tiltable fashion. As shown in Fig. 2 , yokes 5 of bifurcated configurations are pivotally supported on front left and front right side surfaces of the vehicle body 1 . On a support shaft portion 7 of receptacle seats 6 pivotally provided on these yokes 5 , the steerable wheels 2 are rotatably mounted. Suspension cylinders 8 are connected between the receptacle seat 6 and the vehicle body 1 . As shown in Figs. 3 and 4 , knuckle arm 9 is provided on each receptacle seat 6 . Between the knuckle arm 9 and the vehicle body 1 , a steering cylinder 10 is connected. The left and right knuckle arms 9 , 9 are connected by a link mechanisms that the receptacle seat 6 is pivoted to change the orientation of the steerable wheels 2 by the knuckle arm 9 when the steering cylinder 10 is expanded or contracted. Fig 5 shows the first embodiment of a hydraulic motor mounting portion. The receptacle seat 6 comprises a mounting base portion 21 and the laterally directed cylindrical support shaft portion 7 . Within the support shaft portion 7 , a drive axle 20 is rotatably inserted. A boss portion 23 of a flange 22 is engaged with the outer periphery of the support shaft portion 7 and fixed thereto. A wheel hub 24 is rotatably supported via a bearing 25 between the boss portion 23 and the support shaft portion 7 . A vehicular wheel 26 is mounted on the wheel hub 24 to form the steerable wheel 2 . One end of the drive axle 20 and the wheel hub 24 are connected via a planetary gear type reduction mechanism 27 . The reduction mechanism 27 includes a sun gear 28 , a planetary gear 30 provided on a carrier 29 and a ring gear 31 . The sun gear 28 is mounted on the drive axle 20 . The carrier 29 is connected to the wheel hub 24 . The ring gear 31 is connected to the flange 22 . Therefore, when the drive axle 20 is driven to rotate, the wheel hub 24 rotates at a reduced speed to drive the vehicular wheel 26 to rotate. On the end of the mounting base portion 21 of receptacle seat 6 at the side opposite to the side of the vehicular wheel 26 , a motor body 33 of a hydraulic motor 32 is connected. A rotary shaft 35 of the hydraulic motor 32 is coupled with the drive axle 20 in spline coupling by means of a coupling 36 . A brake mechanism 37 is provided between the support shaft portion 7 and the wheel hub 24 . The brake mechanism 37 includes one end plate 39 connected to an outward flange 20a of the support shaft portion 7 by means of bolts 38 . Brake discs 41 are mounted to alternately on the cylindrical body 40 fixed to the one end plate 39 and the wheel hub 24 by spline coupling. A braking force can be thus applied to the wheel hub 24 by supplying a pressurized fluid to a fluid chamber 45 to shift a piston 42 against a spring 43 for pressure engagement of the brake discs 41 and is released from the wheel hub 24 by draining the pressurized fluid from the fluid chamber 45 and to shift the piston 42 toward the opposite direction by the spring 43 for shifting the brake discs 41 away from each other. As shown in Fig. 6 , the drive wheel 3 is driven by an engine a via a torque converter b , a power transmission c , a differential mechanism d and so forth. With the engine a , a main hydraulic pump 61 is driven. An auxiliary hydraulic pump 62 is driven at the output side of the power transmission c . As shown in Fig. 7 , the pressurized fluid discharged from the main hydraulic pump 61 and the pressurized fluid discharged from the auxiliary hydraulic pump 62 are supplied to a steering circuit 64 and a drive circuit 65 under a control by means of a valve 63 . The valve 63 is held at the first position A by means of a spring 66 , and switched into the second position B when a pressure difference is provided at the both sides of an orifice 67 . The steering circuit 64 is connected to the inlet side of a steering valve 68 . The drive circuit 65 is connected to the hydraulic motor 32 . Next, operation will be discussed. While the engine a and the main hydraulic pump 61 operate in the normal state, the valve 63 is placed at the second position B so that the pressurized fluid discharged from the auxiliary hydraulic pump 62 is fed to the hydraulic motor 32 to drive an output shaft 35 to rotatingly drive the drive axle 7 through the coupling 36 and thus to drive the wheel 2 for rotation by the wheel hub 24 driven via the reduction mechanism 27 . In addition, since the auxiliary hydraulic pump 62 is driven by the output side of the power transmission c for revolution at the same speed with the drive wheel 3 so that the discharge amount is proportional to the speed of the drive wheel 3 , the steerable wheel 2 can be driven in synchronism with the drive wheel 3 by the hydraulic motor 32 . At this condition, by applying braking force on the wheel hub 24 by the brake mechanism 37 , the braking force can be applied to the steerable wheel 2 . Also, by expanding and contracting the steering cylinder 10 , the receptacle seat 6 can be pivoted via the knuckle arm 9 to pivot the steerable wheel 2 together with the hydraulic motor 32 for steering. When the discharge amount becomes short due to failure of the engine a or failure of the main hydraulic pump 61 , the valve 63 is switched into the first position A . By this, the pressurized fluid discharged from the auxiliary hydraulic pump can be supplied to the first circuit 64 to make steering possible by expanding and contracting the steering cylinder 10 by operation of the steering valve 68 . Therefore, the auxiliary hydraulic pump 62 functions as an emergency pump. Next, discussion will be given for the second embodiment. As shown in Fig. 8 , in the shown embodiment, the drive axle 20 and the rotary shaft 35 of the hydraulic motor 32 are connected via a clutch mechanism 50 . Namely, a large diameter cylindrical body 51 is formed integrally with the mounting base portion 21 of the receptacle seat 6 at the side opposite to the side of the vehicular wheel 26 . To the opening end face of the cylindrical body 51 , an end plate 52 is connected by means of bolts 53 . The motor body 33 of the hydraulic motor 32 is mounted on the end plate 52 by means of bolts 34 to inwardly extend the rotary shaft 35 through a central hole 54 of the end plate 52 . The rotary shaft 35 is coupled with a drive body 55 which is rotatably supported on the end plate 52 by the spline coupling, and the drive axle 20 is coupled with a driven body 56 which is rotatably supported at the side of the cylindrical body 51 . To the driven body 56 and the drive body 55 , clutch discs 57 are mounted with spline coupling to each other. A piston 58 is depressed by a fluid pressure in a fluid chamber 59 for pressure engagement of the clutch discs to engage the clutch. The piston 58 is returned by a spring 60 to release the clutch discs 57 to disengage the clutch. With the construction set forth above, by disengaging the clutch mechanism 50 while the steerable wheels 2 are not driven, the rotation of the wheel axle 7 will not be transmitted to the drive shaft 35 of the hydraulic motor 32 so as not to cause revolution of the hydraulic motor 32 . Upon driving the steerable wheel 3 , the clutch mechanism 50 is permitted to be placed at the intermediate position between engaging and disengaging by controlling the fluid pressure to the fluid chamber 59 , namely half clutch condition, so that the difference of the left and right steerable wheels 2 , 2 can be absorbed. Fig. 9 is a hydraulic circuit diagram. The pressurized fluid discharged from the main hydraulic pump 61 driven by the engine a and the auxiliary hydraulic pump 62 provided at the output side of the axle or the power transmission c for emergency steering is supplied to the steering circuit 64 and the drive circuit 65 by the valve 63 . The drive circuit 65 is selectively connected to the hydraulic motor 32 and the clutch mechanism 50 . The valve 69 is positioned at the first position C when a pressure difference across an orifice 70 provided in the drive circuit 65 is small for supplying the pressurized fluid of the drive circuit 65 to the hydraulic motor 32 and the hydraulic chamber 59 of the clutch mechanism 50 , and at the second position D when the pressure difference across the orifice 70 is larger for supplying the pressurized fluid of the drive circuit 65 only to the hydraulic motor 32 and for draining the pressurized fluid in the fluid chamber 59 of the clutch mechanism 50 to a tank 72 . With the construction set forth above, the auxiliary hydraulic pump 62 is provided a function as the emergency pump and, since it discharges the fluid amount proportional to the rotation speed of the drive wheel 3 , complicate speed control for the hydraulic motor 32 becomes unnecessary and accurate vehicle speed control while the steerable wheels 2 are driven. Furthermore, when the vehicle speed becomes higher than or equal to a set vehicle speed to increase the discharge amount of the main and auxiliary hydraulic pumps 61 , 62 , the valve 69 is switched into the second position D to disengage the clutch mechanism 50 to automatically terminate driving of the steerable wheels 2 resulting in free rotation of the steerable wheels 2 . Next, the third embodiment will be discussed. As shown in Fig. 10 , a gear type hydraulic motor is employed as the hydraulic motor 32 . The rotary shaft 35 of the hydraulic motor is connected to the drive axle 20 via the clutch mechanism 50 . Next, the fourth embodiment will be discussed. As shown in Fig. 11 , the receptacle seat 6 comprises the mounting base portion 21 and a laterally oriented cylindrical support shaft portion 7 . Within the support shaft portion 7 , the drive axle 20 is disposed in rotatable fashion. On the outer periphery of the support shaft portion 7 , the wheel hub 24 is rotatably supported via the bearing 25 . The vehicular wheel 26 is mounted in the wheel hub 24 . Thus, the steerable wheel 2 is formed. One end of the drive axle 20 and the wheel hub 24 are connected to the planetary gear type reduction mechanism 27 via the clutch mechanism 50 . The reduction mechanism 27 includes a first sun gear 82 integrally provided with an input shaft 81 connected to the drive axle 20 via a coupling 80 , a first planetary gear 83 meshing with the first sun gear 82 , a first carrier 84 supporting the first planetary gear 83 , a stationary ring gear 85 coupled with the end of the support shaft portion 7 of the receptacle seat 6 by spline coupling, a second sun gear 87 supported on the support shaft portion 7 , a second planetary gear 88 provided on a second carrier 86 which is splined with the stationary ring gear 85 and meshing with the second sun gear 87 , and a driving cylindrical body 89 rotatably supported on the wheel hub 24 . First and second internal gears 90 , 91 formed on the driving cylindrical body 89 are meshed with the first and second planetary gears 83 , 88 respectively. The first carrier 84 is meshed with the second sun gear 87 . Thus, two stage reduction mechanism is formed The clutch mechanism 50 includes drive clutches plates 93 and driven clutch plates 94 alternately splined to the driven cylindrical body 92 which is fixed to the wheel hub 24 by means of bolts, and the driving cylindrical body 89 . The driving clutch plates 93 is designed to be engaged onto the driven clutch plates 94 by means of a piston 95 under pressure, The piston 95 is formed into a ring-shaped configuration and engaged within an annular cavity 96 of the wheel hub 24 to define a pressure receiving chamber 97 . By supplying the pressurized fluid to the pressure receiving chamber 97 , the piston 95 is expanded to establish engagement between the driving clutch plates 93 and the driven clutch plates 94 to transmit rotation of the drive axle 20 to the wheel hub 24 . On the other hand, by draining the pressurized fluid from the pressure receiving chamber 97 , the driving clutch plates 93 and the driven clutch plate 94 are released away from each other to disconnect the reduction mechanism 27 provided on the drive axle 20 and the wheel hub 24 . As a result, during high speed travel, the reduction mechanism 27 is never rotate by the rotation of the steerable wheel, abnormal wearing of respective components of the reduction mechanism can be successfully prevented. At the side opposite to the side of the vehicular wheel 26 in the mounting base portion 21 of the receptacle seat 6 , the motor body 33 of the hydraulic motor 32 is connected by means of bolts 34 . The rotary shaft 35 of the hydraulic motor 32 is connected to the drive axle 20 via a first gear 98 and a second gear 99 . A brake mechanism 37 is disposed between the support shaft portion 7 and the wheel hub 24 . The brake mechanism 37 includes one end plate 39 connected to the outward flange 20a by means of bolts 38 . Brake discs 41 are mounted to alternately on the cylindrical body 40 fixed to the one end plate 39 and the wheel hub 24 by spline coupling. A braking force can be thus applied to the wheel hub 24 by supplying a pressurized fluid to a fluid chamber 45 to shift a piston 42 against a spring 43 for pressure engagement of the brake discs 41 . As set forth above, the hydraulic drive system for the steerable wheel of the dump truck according to the present invention permits attaching and detaching of the hydraulic motor even after assembling. Also, since the present invention permits employment of greater hydraulic motor, it is effective as the hydraulic drive system for the steerable wheel of a large size dump truck.

Claims: A hydraulic drive system for a steerable wheel of a dump truck comprising: a yoke (5) pivotally supported on a vehicle body (1) in substantially horizontal direction, a receptacle seat (6) mounted on said yoke (5) in pivotable fashion; a suspension cylinder (8) connected between the receptacle seat (6) and the vehicle body (1), a knuckle arm (9) extending from the receptacle seat (6) for changing the orientation of the steerable wheel (2), a drive axle (20) rotatably supported in a support shaft portion (7) of said receptacle seat (6), said steerable wheel (2) rotatably supported on the outer periphery of said support shaft portion (7), whereby one end of said drive axle (20) is connected to said steerable wheel (2) through a reduction mechanism (27), and a hydraulic motor (32) with its motor body (33) detachably mounted externally on said receptacle seat (6) at a side opposite to said steerable wheel (2) in such a manner that a rotary shaft (35) thereof mates with the inside of said support shaft portion (7), and is connected to the other end of said drive axle (20). A hydraulic drive system according to claim 1, characterized in that a discharge side of a main hydraulic pump (61) driven by an engine (a) is connected to a steering circuit (64), and the discharge side of an auxiliary hydraulic pump (62) driven by an output side of a power transmission (c) is connected to one of said steering circuit (64) and a drive circuit (65) through a valve (63), said valve is selectively connectable to said drive circuit (65) and to said steering circuit (64) depending on a discharge amount of said main hydraulic pump (61), whereby said drive circuit (65) is connected to said hydraulic motor (32). The hydraulic drive system according to claim 1, characterized in that the discharge side of a main hydraulic pump (61) driven by an engine (a) is connected to a steering circuit (64), a discharge side of an auxiliary hydraulic pump (62) driven at the output side of the power transmission (c) is connected to one of said steering circuit (64) and a drive circuit (65) through a valve (63), selectively connecting the auxiliary hydraulic pump (62) to said drive circuit (65) when the discharge amount of said main hydraulic pump (61) is large and to said steering circuit (64) when it is small, and said drive circuit (65) is connected to both said hydraulic motor (32) and a clutch mechanism (50) connecting said rotary shaft (35) to the other end of said drive axle (20) or only to said hydraulic motor (32) through a valve (69), said valve (69) providing the connection to only said hydraulic motor (32) when a flow rate in the drive circuit (65) is large and a connection to both said hydraulic motor (32) and said clutch mechanism (50) when said flow rate is small. The hydraulic drive system according to claim 1 or 2, characterized in that said rotary shaft (35) is connected to the other end of said drive axle (20) via a clutch mechanism (50). The hydraulic drive system according to claims 1 or 2, characterized in that the output side of said reduction mechanism (27) is connected to said steerable wheel through a clutch mechanism (50).

Inventors: HASEGAWA NOBUKI, KINOSITA YOICHI, MORI MASAKI, NAGAI TAKAO, SUGANO YUKIO, HASEGAWA, NOBUKI, KINOSITA, YOICHI, MORI, MASAKI, NAGAI, TAKAO, SUGANO, YUKIO, HASEGAWA, NOBUKI, KAWASAKI FACTORY OF K.K., KINOSITA, YOICHI, KAWASAKI FACTORY OF K.K., MORI, MASAKI, KAWASAKI FACTORY OF KABUSHIKI KAISHA, NAGAI, TAKAO, KAWASAKI FACTORY OF KABUSHIKI KAISHA, SUGANO, YUKIO KAWASAKI FACTORY OF KABUSHIKI KAISHA
Applicants: KOMATSU MFG CO LTD, KABUSHIKI KAISHA KOMATSU SEISAKUSHO
Application year: 1992
Main classification: B60K7
IPC codes: B60K17, B60G13, B60K7, B60G9, B60G3, B62D5, B60G7