Search Images Maps Play YouTube News Gmail Drive More »
Sign in
Screen reader users: click this link for accessible mode. Accessible mode has the same essential features but works better with your reader.

Patents

  1. Advanced Patent Search
Publication numberUS3338441 A
Publication typeGrant
Publication dateAug 29, 1967
Filing dateSep 22, 1965
Priority dateSep 26, 1964
Publication numberUS 3338441 A, US 3338441A, US-A-3338441, US3338441 A, US3338441A
InventorsFlint John C E
Original AssigneeDowty Technical Dev Ltd
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydraulic apparatus
US 3338441 A
Images(2)
Previous page
Next page
Description  (OCR text may contain errors)

29, 1967 J. c. E.- FLINT 3,338,414?

HYDRAULIC APPARATUS Filed Sept. 22, 1965 2 Sheets-Sheet 1 FEG.|

INVENTOR JOHN C. E. FLINT Aug. 29, 1967 Filed Sept. 22, 1965 J. c. E., FLINT 3,338,441

HYDRAUL-IC- APPARATUS '2 Sheets-Sheet FI G.2

Iuvamoe United States Patent 3,338,441 HYDRAULIC APPARATUS John C. E. Flint, Chalford, England, assignor to Dowty Technical Developments Limited, Cheltenham, England, a British company Filed Sept. 22, 1965, Ser. No. 489,195 Claims priority, application Great Britain, Sept. 26, 1964, 39,319/64 6 Claims. (Cl. 214-674) This invention relates to hydraulic apparatus suitable for raising and lowering the load-carrying forks of a forklift device.

According to this invention, 'an hydraulic apparatus suitable for raising and lowering the forks of such a device includes a variable-delivery hydraulic pump arranged to be driven from a power source, and a liquidpressure operable servomotor, the output member of which is mechanically connected to load-carrying forks, the motor being so hydraulically connected to the variable-delivery hydraulic pump as to be operable thereby, at least for raising of the forks, at a rate which is dependent upon the pump delivery condition selected. The forks are substantially vertically guided on a tiltable support and the apparatus further includes a fixeddelivery hydraulic pump, arranged to be driven from the same power source as the variable delivery hydraulic pump, which fixed-delivery pump supplies liquid under pressure for the operation of a further servomotor or servomotors which control the attitude of the support, thereby to change the tilt and/ or the reach of the forks, suitable control valves being rovided for control of these further servomotors. Suitable relief valves may also be provided in the hydraulic circuits associated with the fixed-delivery pump and with the variable-delivery pump.

Both the variable-delivery pump and the fixed-delivery pump may draw their liquid from a common reservoir.

The servomotor associated with the variable-delivery pump is of single-acting telescopic type, the pump charging the cylinder thereof for raising of the forks, but being effectively caused to operate under reverse flow for contraction of the motor and lowering of the forks. Accordingly, the variable-delivery pump may have a deliveryvarying mechanism of such nature that, by a suitable operators control, it can be moved from a zero delivery position, in which the servomotor is substantially held in the position it has attained, progressively to a maximum delivery position in which the servomotor is extended in the forks-raising direction at a maximum rate. Conversely, the

delivery-varying mechanism may also be moved from the zero delivery position progressively to the maximum reverse flow condition in which the servomotor is contracted in the forks-lowering direction at a maximum rate.

In cases where leakage through the variable-delivery pump is such as to prevent the required loads from being held satisfactorily when the delivery-varying mechanism is in its neutral condition, a lock valve is provided on the outlet side of the pump, this being released automatically when the delivery-varying mechanism is moved into the reverse flow condition.

The variable-delivery and fixed-delivery pumps are driven together through the same shaft by an electric motor, itself powered by batteries carried upon the forklift device. Alternatively, the two pumps may be driven by an internal combustion engine.

One embodiment of the invention-will now be particularly described by way of example with reference to the accompanying diagrammatic drawings wherein:

FIGURE 1 is a diagrammatic illustration of a forklift truck having the inventive hydraulic apparatus embodied therein; and

FIGURE 2 is a diagrammatic illustration of the hydraulic apparatus. l

Referring to the drawings, an hydraulic apparatus forming part of a forklift truck 8 and intended for the raising, lowering and tilt control of the forks or load-carryingmember 11 of the truck, includes a variable-delivery pump 12 and a fixed-delivery pump 13, both arranged to be driven by a common electric motor 14 itself powered bybatteries (not shown) carried upon the vehicle 8. Both pumps 12 and 13 are driven by the same shaft 14a and draw their hydraulic liquid for operation from a common reservoir 15.

The variable-delivery pump 12 is constructed in accordance with that described in the specification of copending United States patent application Ser. No. 429,409. The input member 16 of the delivery-varying mechanism of this pump is operated by a manual control lever 17 and connecting rod 18. The lever 17 is movable from the zero flow position shown to the right in FIGURE 2 for progressive increase in the pump delivery flow and to the left for progressive increase in reverse flow.

The variable-delivery pump 12 is connected to deliver liquid under pressure through a pipe 19 to one side of a servomotor for raising the load-carrying member 11. This motor is in the form of a lift jack 20 of single-acting tele-' scopic type. The output member or piston rod 21 of this lift jack is connected by a chain mechanism 22 of conventional form to the load-carrying member 11 of the forklift truck. A relief valve 23 is provided in the pipe 19 at a position adjacent the cylinder of the jack 20, this relief valve spilling to tank 15.

The fixed-delivery pump 13 delivers through a pipe 24 to a tilt control valve 25 of open-centre spool type. This valve is provided with a manual control lever 26 and as well as having a pipe connection 27 back to the reservoir 15, it also has pipes 28 and 29 respectively connecting with either side of a tilt control servomotor in the form of a telescopic jack 30. The cylinder 31 of the jack 30 is pivotally connected at 32 to the body of the forklift truck while the output member or piston rod 33 is pivotally connected to the cylinder of the lift jack 20. This cylinder is pivotally mounted on the body of the truck at 9 so that, as well as affording raising. and lowering control of the load-carrying member, it is capable of imparting to the member the tilt controlling adjustment afforded by the tilt control jack 30. l

The pipe 24 is provided with a relief valve '34, which like the relief valve 23 also spills to the reservoir 15.

The tilt control valve 25 is of such construction that when it is in the neutral position its spool is in the position diagrammatically shown in FIGURE 2 with the diagrammatic centre portion 36 placing a branch pipe39 from the pipe 24 in communication with a pipe 40 which connects with the pipe 27 and thus with reservoir 15. A one-way check valve 38 is ineffective in the circuit when the spool is in the equilibrium position, but the section 36 provides open-centre characteristics for the valve when in this equilibrium position. 7

When the manual control lever is moved to the right in FIGURE 2 the section of the spool shown diagrammatically at 35 is also moved to the right so that the pipes 27 and 28 are placed in communication as also are the pipes 29 and 24. This results in movement to the left of the piston rod 33 of the jack 30, the liquid passing into the jack cylinder doing so through the check valve 38.

When the manual control lever 26 is moved to the left in FIGURE 2 on the other side of the equilibrium position, the section of the spool shown diagrammatically at 37 is brought into effect so that the pipe 29 is broughtinto communication with the pipe 27 and thus with drain, and the pipe 24 is brought into communication with the pipe 28. In consequence, pressure liquid is able to pass through the pipe 28 to the left-hand side of the piston of the jack 30 so that the jack moves to the right in FIG- 3 URE 2, liquid exhausting from the other side of the jack passing through the pipes 29 and 27 to drain. During such operation the check valve 38 is operative again in the supply line to the jack.

In operation of the hydraulic circuits associated with the'load-carrying member 11, when the control lever 17 is moved to the right from its neutral position, the variable-delivery pump 12 commences to deliver liquid under pressure through the pipe 19, the amount of flow being dependent on the extent of movement of the lever to the right. This results in an upward movement in the drawing of the piston and piston rod 21 of the lift jack 20. When the lift jack reaches its upper limit of travel, if the lever 17 is still held in a positive delivery position, pressure in the pipe 19 is relieved to reservoir through the relief valve 23. Otherwise, when the load-carrying member 11 has reached its desired height, the lever 17 is moved back to the neutral position, there being substantially no inherent leakage within the variable-delivery pump 12 so that the load-carrying member 11 and the load it carries are held in the raised position by the column of oil extending between the pump 12 and the jack 20 with the relief valve 23 maintained closed.

When it is desired to lower the load-carrying member 11, the lever 17 is moved from its neutral position to the left in FIGURE 2, whereupon the operation of the variable-delivery pump 12 is reversed, thereby affording reverse flow through the pump. Hence, the jack 20 contracts at a rate dependent upon the extent to which the lever is moved to the left, contraction of course being assisted by the effective weight of the member 11.

Since the variable-delivery pump 12 and the fixeddelivery pump 13 are driven by the same electric motor 14, then during lift operation of the member 11, the fixed delivery pump 13 is also being driven, but the tilt control valve 25 associated therewith is in the neutral position so that the delivery of the pump 13 is allowed to flow through the unloading passage formed by the pipe 39, section 36 of the spool and pipe back to the reservoir 15.

However, when the manual control lever 26 of the tilt control valve 25 is moved either to the left or to the right, liquid under pressure in the pipe 24 is caused to pass either through the pipe 28 or the pipe 29, as explained above, to the left or right-hand sides of the jack 30 so that the jack is either contracted or extended, as the case may be. Tilt is thus imparted to the member 11 by way of the jack 20.

The variable-delivery pump 12 is of somewhat larger capacity than the fixed-displacement pump. When the delivery-varying mechanism of the variable-delivery pump is in a partial flow condition, the power wasted corresponds only to the leakage in the pump in operation, whereas in the case of a fixed-delivery pump, partial flow can only be achieved by discharging the balance of the pump flow to reservoir at high pressure, which wastes a corresponding fraction of pump power. However, the fixed-delivery pump 13 is of such smaller capacity than the variable-delivery pump 12 that heat generated when its output is throttled by the unloading passages in the valve structure under restrictive flow conditions, is tolerable.

Since in the system above-described the lifting and tilting circuits are separate, operation at different pressure levels cannot cause power wastage.

The above system is so arranged that there is no interaction between lift and tilt circuits so that these can easily be operated simultaneously.

The control of the variable-delivery pump is such that there is very little dead travel on the pump stroke control, and it would also be possible to reduce the dead travel on the lever 26 of the tilt control valve 25 by suitably incorporating a cam on the operating spindle thereof.

Further, with the variable-delivery pump, the problem of inching, otherwise evident in spool valves associated with fixed-delivery pumps and there overcome by the introduction of inching slots which can be designed for one pressure only, does not arise because inching with the variable-delivery pump is hardly dependent upon pressure.

In another embodiment of the invention the apparatus includes a further spool valve for the direction of fluid derived from the fixed-delivery pump to a further servomotor in the form of a telescopic jack. This jack is so geometrically arranged in relation to the tilt control jack and the lifting jack as to afford reach control for the load-carrying member 11.

In other embodiments, further circuits are powered by the fixed-delivery pump, or jointly by additional fixeddelivery pumps driven from either the same power source or a separate power source.

In another embodiment of the invention, where the construction of the variable-delivery pump is such that when the delivery-varying mechanism is in the neutral position a small amount of leakage back through the pump might occur to prevent a load from being satisfactorily held, a lock valve shown in dotted detail at 41 is provided in the line 19 upon the outlet side of the variable-delivery pump 12, automatic release linkage 42, also shown in dotted detail, being provided and operable when the lever 17 of the delivery-varying mechanism is moved to the left in FIGURE 2 for the reverse flow condition.

Thus, by the invention, difiiculty of manipulation of at least two services at the same time and in which pump flow must be shared, is avoided, as is a system of preferences which of necessity would have otherwise been built in to ensure that the important services are not starved of operating liquid. Further, there is no interaction between the separate lift and tilt circuits and there is no effect by the tilt circuit upon the more important lift circuit. However, as in the above embodiment where a reach circuit is combined with a tilt circuit it is still unlikely that more than one would be used simultaneously with lift.

The invention is in no way limited to driving of the pumps by an electric motor, as in other embodiments, they are driven by internal combustion engines.

I claim as my invention:

-1. In a forklift device having a vehicular body, a tiltable support thereon, and load-carrying forks substantially vertically guided on the support, hydraulic control apparatus comprising a power source, fixed and variable delivery hydraulic pumps driven by the power source, and a pair of liquid-pressure-operated servomotors, one of which is carried on the tiltable support and operatively interconnected with the forks to raise and lower the forks in use, the one servomotor being of the single acting type and there being a hydraulic interconnection between the one servomotor and the variable delivery pump whereby the variable delivery pump operates the one servomotor at a rate determined by the delivery selected therefor, and the other of which servomotors is carried on the body of the device and operatively interconnected with the tiltable support to vary the attitude of the support in use, there being a hydraulic interconnection between the aforesaid other 'servomotor and the fixed delivery pump, and valve means in the latter hydraulic interconnection, whereby the fixed delivery pump operates the aforesaid other servomotor at times determined by operation of the valve means.

2. A forklift device according to claim 1, wherein relief valves are provided in the hydraulic circuits associated with the fixed-delivery pump and with the variabledelivery pump. 1

3. A forklift device according to claim 1, wherein the variable-delivery pump and the fixed-delivery pump are so connected as to draw their liquid from a common reservoir.

which is movable from a zero delivery position wherein the aforesaid one 'servomotor is substantially held in the position it has attained, progressively to a maximum delivery position wherein the one servomotor is extended in the forks-raising direction at a maximum rate.

5. A forklift device according to claim 4, wherein the delivery-varying mechanism is also movable from the zero delivery position progressively to a maximum reverse flow condition in which the one servomotor is contracted in the forks-lowering direction at a maximum rate.

6. A forklift device according to claim 1, wherein leakage through the variable-delivery pump is such as to prevent the required load from being held in position when the delivery-varying mechanism is in its neutral condition, and a lock valve is provided on the outlet side 15 of the variable-delivery pump, which lock valve is so constructed as to be releasable automatically when the delivery-varying mechanism is moved into the reverse flow condition.

References Cited UNITED STATES PATENTS 2,008,687 7/ 1935 Dean.

2,389,164 11/1945 Payne 6052 2,914,922 11/ 1959 Gibson 6052 3,146,593 9/1964 Stacey 6052 3,163,008 12/ 1964 Hansen 6052 X 3,219,259 11/ 1965 Horton 6052 X EDGAR W. GEOGHEGAN, Primary Examiner.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US2008687 *Mar 8, 1934Jul 23, 1935Walter C DeanAutomatic tension winch
US2389164 *Sep 11, 1944Nov 20, 1945Harvey Payne WilliamMechanism for supporting and automatically adjusting arc furnace electrodes
US2914922 *Apr 6, 1956Dec 1, 1959Unitron CorpHydraulic system for extending and retracting an antenna mast or the like
US3146593 *Apr 18, 1960Sep 1, 1964Parker Hannifin CorpDual pump system and control valve assembly therefor
US3163008 *Apr 9, 1963Dec 29, 1964Elmer K HansenHydraulic drive system
US3219259 *Oct 21, 1963Nov 23, 1965Yale & Towne IncVacuum supply system for industrial truck
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3754394 *Dec 2, 1971Aug 28, 1973Hyster CoHydraulic control system for electric lift truck
US8001751 *Sep 14, 2007Aug 23, 2011Cnh America LlcMethod for gradually relieving pressure in a hydraulic system utilizing reverse fluid flow through a pump of the system
EP0306988A2 *Sep 9, 1988Mar 15, 1989DEERE & COMPANYHydraulic brake system for a utility vehicle
Classifications
U.S. Classification414/635, 60/426
International ClassificationB66F9/22, B66F9/20, F15B11/00, F15B11/17
Cooperative ClassificationF15B2211/7107, B66F9/20, F15B11/17, F15B2211/27, F15B2211/3116, F15B2211/20546, F15B2211/20576, B66F9/22
European ClassificationB66F9/22, F15B11/17, B66F9/20