US2712876A

US2712876A - Self-loading and dumping vehicle

Info

Publication number: US2712876A
Application number: US279609A
Authority: US
Inventors: Jr Christian G Kuehn
Original assignee: Individual
Current assignee: Individual
Priority date: 1952-03-31
Filing date: 1952-03-31
Publication date: 1955-07-12
Anticipated expiration: 1972-07-12

Description

y 12, 1955 c. G. KUEHN, JR

SELF-LOADING AND DUMPING VEHICLE Filed March 31, 1952 CHRISTIAN e. KUEHN Jr.

(Itto egs Fig. 4

United States Patent SELF-LQADING AND DUMPTNG VEHICLE Christian G. Kuehmln, La Paz, Bolivia Application hiarch 31, 1952, Serial No. 279,609

6 Claims. (Cl. 214-78) This invention relates to improvements in machines for loading, transporting, and dumping materials, such as ore, dirt, and the like.

One of the objects of the invention is to provide a machine of the foregoing type which eliminates gear transmissions, clutches, and other power transmission means formerly employed to transmit power from the driving motor or engine to the Wheels.

Another object is to provide hydraulic oil operated motors for driving the traction wheels of the machine, which motors are supplied by a high-pressure pump driven by a prime mover, such as an internal combustion engine or electric motor.

Another object is to provide controls for selectively driving all traction wheels of the machine, or only a part thereof.

Another object is to increase the speed of the machine when only a portion of the traction wheels are driven, with the engine and pump speed remaining substantially constant.

A further object is to provide novel hydraulic iift means for a loading scoop or bucket.

Still further objects, advantages, and salient features will become more apparent from the description to follow, the appended claims, and the accompanying drawing, in which:

Figure l is a side elevation of the machine, portions being roken away;

Figure 2 is a top plan of Figure 1, portions being broken away;

Figure 3 is a section taken on line 33, Figures 1 and 2;

Figure 4 is an enlarged section taken on line 4-4, Figure 3;

Figure 5 is an enlarged section taken on line 5-5, Figure 1;

Figure 6 is a section taken on line 66, Figure 5;

Figure 7 is an enlarged section taken on line 77, Figure 1;

Figure 8 diagrammatically illustrates the hydraulic system and its controls; and

Figures 9 and 9a illustrate two positions of a valve employed in Figure 8.

Referring in detail to the drawing, the machine comprises, in general, a suitable wheel supported frame including side members 10, Ha, which carry a body 11, having an elevating scoop or bucket 12 at the end opposite from the engine.

The body comprises

side panels

13, 13a, the lower portions 14, 14a of which slope downwardly and inwardly, as best shown in Figure 3. The side panels also have inwardly slanting

portions

14b, 14c which join a pair of parallel vertical panel portions 15, 15a, the latter being connected at their lower edges to a downwardly and rearwardly sloping floor 16. A vertical panel 17 extends between

panels

13, 13a. The panels so far described form a loading bin or hopper for receiving the material to be transported and dumped. The bottom of the bin is proice vided with a door D, hinged on transverse hinge pin 18, and retained closed by a latch 19 which may be moved to unlatched position by the machine operator in any manner well undertood in the art, such as by a release rope R connected to the latch.

The scoop comprises a pair of side plates 20, 29a between which extend, adjacent the lower end, a plate 21 forming a bottom wall for the bucket proper, a plate 22 1forming a rear wall, and a plate 23 forming a top wal Plates 20, a are joumaled on the ends of a transverse shaft 24, affixed to a floor 16 in any suitable manner, such as by clamp brackets, one of which is shown at B. The upper edges of plates 20, 26a are provided with curved flanges, one of which is shown at 25, Figure 7, which receives a cable 26 in a groove 27 in the flange. The upper end of the cable is secured at the upper end of the groove and thence extends downwardly around the flange, around an idler pulley 271, rotatably supported by frame 10, around pulley 28 to a bracket 29, aflixed to the frame, where the lower end of the cable is aflixed. Pulley 28 is rotatably carried by an end of piston rod 3%) actuated by a piston 31, disposed in actuator cylinder 32, afiixed to the frame. A similar actuating mechanism is employed on the opposite side or" the machine. It will be apparent that when the pistons in the cylinders move to the left (Figures 1, 5 and 6), the pulleys carried by the front ends of their piston rods will draw the cables around the idler pulleys and lift the scoop to the dotted position, Figure l, where it will discharge its contents into the bin. As will be apparent, an increment of rectilinear bodily movement of pulley 28 effects twice said increment of movement to the upper end of the cable.

Flanges 25, a each extend approximately 180 degrees around the axis of shaft 24. Approximately 90 degrees of the lower portion of each flange is circular and concentric with the axis of shaft 24 and the remainder is formed as an involute with the top end closer to the axis of rotation than the circular portion. With piston 31 moving at substantially constant rectilinear velocity, it will be apparent that the scoop swings at substantially constant angular velocity for approximately the first 90 degrees of its upperward swing and thereafter accelerates in angular velocity through approximately the last 90 degrees of its upward swing.

It will be apparent that the cable construction, just described, is exemplary of any type of flexible member, such as a chain, or the like.

To limit rearward motion when the scoop is in its lower position, a bar 32 is provided which extends between plates 26, Zila which abuts the forward ends of frames 10, lea. The scoop may be suitably counterweighted, or spring urged, toward the lowered position; when it is raised to its upper position, as shown in dotted lines, Figure 1, so that it will return to the lowered position when the actuator pistons are moved to the right.

The machine is supported at the engine end by a difierential housing 321 with differential mechanism therein, wheels provided with

pneumatic tires

34, 340, being connected to the outer ends of the axle shafts contained within the housing. Since devices of this kind are commonly used in automobiles and trucks, detailed description is omitted to simplify the disclosure. As shown in Figure 4, the central portion of the diiferential housing is provided with an enlarged portion which contains the conventional ring gear and its driving pinion, and the differential gears (not shown). To pinion end of this portion of the housing, a reversible hydraulic motor 35 is aifixed, its driving shaft being coupled to the pinion in any desirable manner.

The dipper end of the machine is supported by a similar differential device 36 and wheels with tires 37, 37a,

this being essentially the same as the differential assembly previously described with the exception that the wheels may be rotated about substantially vertical axes so that the machine may be steered. This dipper-end housing may be of any conventional construction such as used on Jeeps or other front wheel-drive vehicles. A reversible motor 38, like motor 35, is similarly connected to the driving pinion of the dipper-end differential.

While the steering wheels above mentioned have been illustrated as being located at the dipper end of the ma.- chine for the purpose of simplifying the disclosure, it will be understood that for mechanical reasons the preferred position for said steering wheels may be at the engine 7 end of the machine.

A prime mover 39 is disposed within the body, this being coupled to a liquid pump 40 which operates motors and 38, and actuators 32 and 32a. A coolant radiator 41 is also provided to cool the engine and supply coolant to a heat exchanger 42 for cooling the oil employed to operate the various instrumentalities.

Motors 35, 38, previously referred to, are of the type which produce substantially constant torque at constant oil supply pressure.

Their speed and horse power are substantially directly proportional to the volume of oil delivered thereto. These characteristics apply to either direction of rotation. Motors of this type are well known, one manufacturer thereof being the Sundstrand Machine Tool Co. of Rockford, Illinois.

The pump is of the vane type which delivers substantially constant volume at a given speed and pressure. At a. given speed the volume may also be varied by inversely varying the pressure, that is, to give constant horse-power output. The driving torque of the pump is substantially proportional to pressure. A manual control on the pump provides constant output pressure which may be varied at will. Pumps of this type, are also conventional. Other types of oil pumps may be substituted for the vane pump described. 7

Referring to Figures 8, 9 and 9a, it will be assumed that it is desired to move the machine into the material to be collected by the scoop. With valve 43 in the position shown in Figure 9, pump will deliver oil through conduit 44, through the valve to conduit 45, thence through motor 35, through conduit 46, through the valve to conduit 47, through oil cooler 42 and back to the pump through conduit 48. Motor 38 is also connected to

conduits

45 and 46, that is, the two motors are in parallel, hence, the oil delivered to conduit 45 will be divided between the two motors with each applying torque to the set of wheels it drives.

Assuming now, that it is desired to move the machine in a reverse direction, valve 43 is moved to the position shown in Figure 9a. Oil is then delivered through conduit 44, valve 43 to conduit 46, through motor 35 to conduit 45, through valve 43 to conduit 47, and thence back to the pump through the oil cooler 42 and conduit 48. Since the oil is now flowing through motor 35 in the reverse direction, the motor rotates in the reverse direction and moves the machine in a reverse direction. It is apparent, also, that the oil will be similarly divided between

motors

35 and 38, as previously described, and both motors will operate in the reverse direction.

While the reverse feature just described may optionally be. employed, it will sometimes be preferred to operate onlyv one of the motors in reverse direction, for example, motor 35. To attain this end, a valve '49 in conduit 45 is closed, a valve in conduit 46 is closed, and a valve 51 in a bypass conduit 52, downstream from valves 49, 5%) is opened. This shuts off the supply and return of oil to and from motor 38, and as it rotates from power supplied by wheels 37, 37a, the oil merely circulates through the motor and bypass conduit. Under these conditions the oil from conduit 44 is all delivered to motor 35. If it be assumed that motor 1 upwardly (Figure 8).

35 is the same size as motor 38, the former will now receive twice the volume of oil. This, of course, due to the characteristics of the motor, previously described, will operate motor 35 at twice its former speed and, hence, move the machine at twice the former speed. Since the load on the machine and the traction required by the wheels is maximum when the scoop is moving into the material and will normally be a minimum when the machine is being moved to or from the unloading station, it becomes apparent the utilization of this increased speed under minimum load conditions effects considerable saving of time in the overall operations of loading, transporting, clumping and return to the loading station.

A valve 143, similar to valve 43, is employed for controlling operation of actuators 32, 32a. Assuming that this valve is in a position similar to Figure 9, oil will flow from conduit 44 to conduit 144, through the valve to conduit 145, moving the pistons in actuators 32, 32a Oil trapped in the upper ends of the actuators flows through conduit 146, through the valveto conduit 147 and thence to the pump through conduit 47, oil cooler 42 and conduit 48, when the valve is moved to a position similar to Figure 90, oil will flow from conduit 144, through the valve to conduit 146 and thence to the upper ends of actuators 32, 32a and force the pistons downwardly. Oil trapped in the lower ends of the actuators flows through conduit 145, through the valve to conduit 147 and thence to the pump through conduit 47, oil cooler 42 and conduit 48.

It will be understood that when either of

valves

43 or 143 are intermediate the positions shown in Figures 9 and 9a, no flow of oil will occur. In the case of the wheel drive, the wheels will be locked and in the case of the scoop, it, also, will be locked in the position it happens to be when valve 143 is moved to such intermediate position. It is apparent, therefore, that the control valves and motors provide braking means for the movement of the machine or the movement of the scoop.

The valves just described are disposed in a convenient location in the operators compartment 53, as shown in Figures 2 and 3, this compartment being provided with a seat 54 and a steering device 55 for guiding the machine. The steering device includes a reduction gear box 56 at its lower end which may be operatively linked to the steering wheels for controlling same. Since steering pitman arms, drag links, tie rods and other linkage employed for this purpose are well known in the art of steering of vehicles, the details have been omitted to simplify the disclosure.

The pump 40 may be provided with any suitable type of bypass valve 60 and bypass conduit 61 for permitting circulation between its inlet and discharge, as is well understood in the art.

When the machine is employed in a well-ventilated atmosphere, such as above the surface of the ground, any type of prime mover may be used, including a gasoline engine. When used in a mine, however, either a diesel engine or an electric motor is preferred. Electric motors, of course, produce no fumes, and it is now possible to condition the exhaust gas from diesel engines so that the mine atmosphere is not contaminated with'objectionable gases. When an electric motor is employed,

- it may be connected to a trolley source of power, or by retractible cable reels with wires extending between the unloading station and the loading station, reels of this type being well known.

While the

motors

35 and 33 are disclosed as directly connected to the differential pinions, it will be understood that suitable gearing, or other power transmission means. may be interposed between the motors and pinions so employed to furnish a desired speed of the machine.

While I have referred to the differential as containing a ring gear and pinion, it will be apparent that 5 Where higher reduction ratios are desired, the ring gear may be in the form of a worm wheel and the pinion in the form of a Worm. The language ring gear and pinion, as subsequently employed in the claims, is, therefore, intended to be generic to either type of gearing, just referred to.

While I have described one manner of effecting speed control by cutting one of the motors out of the circuit, allowing the other motor a greater volume of liquid, it will be apparent that the speed of the machine, either one or both motors driving same, be varied by varying the pump pressure, and/or varying the pump speed by varying the speed of its prime mover.

Many modifications Within the purview of the invention will become apparent to those skilled in the and, hence, the specific disclosure is to be regarded as exemplary only, and the invention not limited thereto except as required by the state of the prior art and the scope of the appended claims.

Having described the invention, what is claimed new is: V

1. A material handling device having a scoop-end, comprising; a bin having an inclined portion projecting over the scoop-end of the device, scoop means pivotally carried by and on a fixed axis adjacent the scoop end of the device for movement between a lowered position wherein it may load material and a raised position gravitationally directly over the lowered position wherein it may unload the material into the bin, two pairs of wheels supporting the bin, each pair of Wheels including differential gearing means for driving same, and one pair of wheels being steerable, first rotatable reversible hydraulic motor means operatively connected to the differential gearing for one pair of Wheels, second rotatable reversible hydraulic motor means operatively con nected to the difrerential gearing for the other pair of Wheels, a liquid pump carried by the device for circulating liquid under pressure through the first and sec ond motor means and back to the pump, means carried by the device for operating the pump, and control means carried by the device for supplying the first and second motor means with liquid for flow therethrough in either of opposite directions, whereby the first and second motor means may be reversed and the Wheels rotated in either of opposite directions of rotation.

2. A device in accordance with claim 1 including control means for discontinuing circulation of fluid from the pump through the motor means for one pair of wheels, and for establishing a liquid by-pass circuit to permit same to idly rotate from power received from the pair of wheels same is operatively connected to, the discontinued circulation being supplied to the motor means for the other pair of Wheels, whereby the latter receives a greater quantity of liquid and rotates at a higher speed.

3. A material handling device in accordance With claim 1 including hydraulic actuator means operated by said pump for raising the scoop to the raised position.

4. A material handling device in accordance with claim 3 wherein the scoop means includes spaced memhers mounting same for rotation about a substantially horizontal axis fixed near their upper ends and with respect to the bin, at least one of said members having curved means for receiving a flexible member thereabout, one end of said flexible member being aflixed to the upper of the curved means and the other end aflixed relative to the bin, a rotatable member moveable relative to the bin by the actuator means, said flexible member being trained about said rotatable member in a manner such that an increment of bodily movement or the rotatable member effects a multiplication of said movement to the first-named end of the flexible member.

5. A device in accordance with claim 4 wherein said curved means is constructed and arranged to accelerate the angular movement of the scoop as it moves during the last portion of its movement from the lower {to the upper position while said rotatable member bodily moves at substantially constant velocity.

6. A device in accordance with claim 4 wherein said curved means comprises a portion circular and concentrio with said axis and another portion non-concentric with said axis.

References (Iited in the file of this patent UNITED STATES PATENTS