U.S. patent number 3,908,515 [Application Number 05/395,647] was granted by the patent office on 1975-09-30 for hydraulic circuit with selectively actuatable float control.
This patent grant is currently assigned to Caterpillar Tractor Company. Invention is credited to Howard L. Johnson.
United States Patent |
3,908,515 |
Johnson |
September 30, 1975 |
Hydraulic circuit with selectively actuatable float control
Abstract
A hydraulic system having the combination of a source of
pressurized fluid, a linear hydraulic motor, a main control valve
to selectively direct hydraulic fluid to the motor, and a lock
valve disposed between the control valve and motor is provided with
an auxiliary valve to by-pass the main control valve to disable the
lock valve to provide a float condition for the motor.
Inventors: |
Johnson; Howard L. (Joliet,
IL) |
Assignee: |
Caterpillar Tractor Company
(Peoria, IL)
|
Family
ID: |
23563901 |
Appl.
No.: |
05/395,647 |
Filed: |
September 10, 1973 |
Current U.S.
Class: |
91/420; 91/437;
91/447; 91/464; 91/445; 91/453 |
Current CPC
Class: |
F15B
13/01 (20130101) |
Current International
Class: |
F15B
13/00 (20060101); F15B 13/01 (20060101); F15B
011/08 (); F15B 013/042 (); F15B 013/043 () |
Field of
Search: |
;91/420,445,437,447,453,464 ;137/596.12,596.13 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Cohen; Irwin C.
Attorney, Agent or Firm: Phillips, Moore, Weissenberger
Lempio & Strabala
Claims
What is claimed is:
1. In a hydraulic system for selectively positioning a work member
in selected fixed positions the combination comprising:
a linear double-acting hydraulic motor connected to a work member,
a source of fluid pressure including a sump and a pump for
supplying fluid for operating said motor, a three position
directional control valve in a valve housing and having a neutral
position, and raise and lower positions for selectively directing
fluid from said source to either end of said motor for operation of
said motor for positioning said work member, a single control lever
for operating said control valve, lock valve means including first
and second passage means communicating said fluid respectively with
alternate ends of said motor, check valve means disposed in each
said passage means to normally block flow of said fluid from said
motor and including pressure-responsive piston and plunger means in
each said passage means for unseating said check valve means to
provide communication between both ends of said motor and sump by
way of said directional control valve, said check valve means
disposed between said control valve means and said hydraulic motor
for normally locking said motor in a selected position;
solenoid operated auxiliary valve means separate spaced from and
independent of said directional control valve and valve housing
disposed between said source of fluid pressure and said lock valve
means for bypassing said directional control valve for directing
fluid solely to each said piston and plunger means solely for
unseating each said check valve means for communicating both ends
of said motor with said sump by way of said directional control
valve for enabling free floating movement of said hydraulic motor
when said main control valve is in a neutral position between said
raise and said lower positions.
2. The hydraulic system of claim 1 wherein said solenoid operated
auxiliary valve means comprises a pair of solenoid operated
two-position valves.
3. The hydraulic system of claim 2 including control means for said
solenoid operated auxiliary valve means comprising a source of
electrical power and switch means for selectively activating said
solenoids.
Description
BACKGROUND OF THE INVENTION
The present invention relates to hydraulic circuits and pertains
particularly to a circuit having a lock valve selectively
actuatable to provide a floating condition for a hydraulic
jack.
It is common practice to utilize an earthmoving vehicle for
ancillary operations by attaching an auxiliary implement thereto.
For example, motor graders are frequently employed for snow removal
by attaching a snow plow to the forward end thereof. In many cases,
the auxiliary implement, such as the snow plow, operates more
efficiently if it is free to ride or float on the surface so it can
follow the surface contour. However, many of the hydraulic control
systems of such vehicles employ a lock valve which would prevent
free floating of the blade. Thus, one of the difficulties
encountered in using a vehicle for ancillary operations is that of
providing an attachment type control circuit which provides a float
position without employing a sophisticated and expensive control
valve, and which is compatible with the basic hydraulic circuit of
the vehicle.
SUMMARY OF THE INVENTION
It is the primary object of the present invention to provide a
control system that overcomes the above problems of the prior
art.
In accordance with the present invention a hydraulic control system
for controlling hydraulic jacks for positioning an implement or the
like and including a lock valve for maintaining the implement in a
fixed position is provided with an auxiliary valve to by-pass the
main control valve to disable the lock valve to provide a float
condition for the implement.
BRIEF DESCRIPTION OF THE DRAWINGS
Other objects and advantages of the present invention will become
apparent from the following description when read in conjunction
with the accompanying drawings wherein:
FIG. 1 is a schematic layout of a circuit in accordance with the
present invention; and
FIG. 2 is a schematic of a modification of an auxiliary valve for
the circuit of FIG. 1.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
Referring more particularly to FIG. 1 of the drawing, a hydraulic
circuit in accordance with the present invention generally
comprises a source of pressurized fluid including a pump 11 which
draws fluid from a sump or reservoir 12. The pump supplies
pressurized fluid by way of a supply conduit 13 to a main control
valve 14 with fluid exhausted from the control valve being returned
to the reservoir through a return line or conduit 15. A relief
valve 16 interconnects the supply conduit 13 and the return conduit
15 to relieve excessive pressure in the hydraulic circuit.
The control valve 14 is of the type that has three positions
attainable by actuation of a control lever 17 to one of the three
positions indicated by the letters R, N, and L. The control valve
is operative in selecting one of the R or L positions to direct
fluid via supply lines 21 and 22 to either the head or rod end of a
double acting hydraulic motor or jack 23. When the control valve is
in the neutral position, both of a pair of control conduits 18 and
19 are in communication with the return conduit 15 to reservoir 12.
The conduits 18 and 19 communicate fluid from the control valve 14
to a pilot operable lock valve 20, where the fluid is communicated
by way of motor supply lines 21 and 22 to jack 23. The hydraulic
jack 23 is controlled by the lock valve through conduits 21 and
22.
The lock valve 20 includes a valve body 24 having a bore 25
extending longitudinally therethrough. A first pair of axially
spaced radial ports 26 and 27 are formed in the body and
communicate the conduits 18 and 19, respectively, with the bore 25.
A second pair of axially spaced radial ports 28 and 29 are formed
in the body and communicate the conduits 21 and 22, respectively,
with the bore. The valve body has a third radial port 30 formed
therein intermediate the ports 26 and 27.
A pair of identical check valve assemblies 31 and 32 are
individually disposed in opposite ends of the bore and secured in
place by a respective one of a pair of plugs 33 and 34 individually
threadably secured in the open end of the bore. Check valve
assembly 31 normally blocks port 28 from port 26 while check valve
assembly 32 normally blocks port 29 from port 27. Each check valve
assembly includes a ball 35 and 36 resiliently urged against a seat
37 and 38 by a compression spring 39 and 40.
A pair of opposed axially aligned actuator pistons 41 and 42 are
reciprocally mounted in the bore 25 of the valve body 24 between
the check valve assemblies 31 and 32. Suitable spacing means such
as protuberances 43 and 44 are adapted for abutting engagement with
each other and form a chamber 45 between the pistons. Each piston
includes a plunger 46 and 47 which extends outwardly from the outer
end of each piston for engagement with the balls 35 and 36 of the
respective check valve assembly.
A pair of solenoid control valves 48 and 49 are in communication
with the port 30 and chamber 45 of the valve body through a conduit
50. The valve 48 is normally open and in communication with
reservoir 12 through a return conduit 51. The solenoid valve 49 is
normally closed and communicates with the fluid supply conduit 13
through a branch or by-pass conduit 52. A suitable conductor 53
electically connects the solenoid valves to a normally open toggle
switch 54 which is connected to a suitable electrical source such
as a battery 55.
In an alternate embodiment as shown in FIG. 2, the solenoid
operated valves 48 and 49 of FIG. 1 may be replaced with a single
2-position, 3-way solenoid control valve 56 which normally
communicates the conduit 50 with the return conduit 51. Closing the
toggle switch 54 energizes the solenoid control valve causing it to
shift to a position to communicate the branch conduit 52 with the
conduit 50. This communicates pressurized fluid to chamber 45 which
forces pistons 41 and 42 to unseat ball check valves 35 and 36 to
thereby disable the lock valve 20.
OPERATION
During normal vehicular operation, the toggle switch 54 is open so
that the chamber 45 is vented to the reservoir 12 through the
conduit 50, the normally open solenoid valve 48, and the return
conduit 51. With chamber 45 vented, the lock valve 20 functions as
a conventional lock valve whereby fluid from both ends of the
hydrostatic jack 23 is blocked by the respective check valve
assemblies 31 and 32 of the lock valve. When the control valve 14
is shifted to direct pressurized fluid through conduit 18 to the
lock valve, the ball 35 of the check valve assembly 31 is unseated
by the pressurized fluid which is then transmitted to the hydraulic
jack through conduit 21. Simultaneously, the pressurized fluid
entering the lock valve through the conduit 18 acts upon the
actuator piston 41 shifting it and the actuator piston 42 to the
right. The plunger 47 of the piston 42 engages and unseats the ball
36 of the check valve assembly 32 permitting fluid exhausted from
the hydraulic jack through the conduit 22 to be exhausted through
conduit 19, the control valve 14 and the return conduit 15 to the
reservoir 12. Conversely, pressurized fluid directed through
conduit 19 passes through the lock valve in a similar manner and to
the head end of the hydraulic jack through conduit 22. The fluid
exhausted through conduit 21 passes through the lock valve 20,
conduit 18, control valve 14, and return conduit 15 to the
reservoir.
To obtain a float position of the hydraulic jack 23, the toggle
switch 54 is closed to direct electrical energy to the solenoid
control valves 48 and 49. Simultaneously, the valve 48 is shifted
to a closed position blocking communication therethrough while
valve 49 is shifted to an open position to direct pressurized fluid
from the pump 11 through conduits 13, 52 and 50 into the chamber 45
of the lock valve 20. The pressurized fluid in chamber 45 urges the
actuator pistons 41 and 42 in opposite directions to unseat the
balls 35 and 36 of both check valve assemblies 31 and 32. This
communicates both the head end and the rod end of the hydraulic
jack 23 with the reservoir 12 through the various conduits and
provides the float condition.
* * * * *