Note: Descriptions are shown in the official language in which they were submitted.
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This application is a divisional of copending Canadian
application Serial No. 354,772, filed June 25, 1980~ in the name of
TRI~ Inc.
This invention relates to a flùid controller which in-
cludes a metering section and a control valve section, and which
responds to rotation of an input shaft to meter fluid flow from a
source to a motor such as the steering motor of a vehicle. It
relates particularly to a controller in which the valve section is -
formed by a stacked assembly of plate valves which control fluid
flow and which, along with the metering section, also form the outer
periphery of the controller, and minimize the need for complex,
heavy cast housing parts. Further, it relates to a controller which
is compact, and which meters needed flow to a primary steering
motor, and directs excess flow to an auxiliary motor. Additionally,
it relates to a controller characteri~ed by unique structure
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for providing a spring centering force for biasing the
~` controller to a neutral condition, for forming pressure
dams to m;nimize leakage of metered fluid, and for sealing
the input shaft against leakage of fluid.
Background of the Invention
Steering controllers are well known for controlling
fluid flow to operate the power steering systems of off
the road vehicles such as trucks, farm tractors, farm
combines, and end loaders, etc. Such controllers are
typically designed to meter flow from a source re.g., the
power steering pump) and direct the metered flow to power
the vehicle steering motor.
In steering controllers known as integral controllers
a control valve section and a metering section are
disposed within a housing which is usually formed by one
or more cast iron housing members. In the absence of
steering effort, the control valve section is in a neutral
condition in which no flow is directed to the steering
motor. In response to operation of an input shaft
connected with the vehicle steering wheel, the control
valve section is moved away from the neutral condition
into an operating condition in which the valve section
directs flow from the source to the metering section, and
directs metered flow from the metering section to the
steering motor. When operation of the steering wheel
.3 ~ ~
ceases, the control va]ve section is returned to ~he
neutral condition.
U.S. Patent 3,895,888 discloses one such controller.
The controller includes a metering mechanism formed by the
intermeshing teeth of a pair of gerotor gear members
having relative orbital and rotational movement. An input
shaft is fixedly coupled with one gerotor gear member to
rotate one of the gerotor gear members therewith. The
other gerotor gear member is coupled wit'n a rotatable
control valve element and, in response to rotation of the
one gerotor gear member, effects rotation of the control
valve element by a limited extent from a neutral condition
to place the controller in an operating condition. At
~igures 14-16 the patent discloses a controller in which
the control valve includes a rotatable plate valve and
provides a very compact structure.
Some steering controllers have also been designed so
as to be capable of not onl,y metering needed flow to ~he
steering motor, but also ~irecting excess flow to an
auxiliary moto~ associated with equipment such as
backhoes, li~ting devices, etcO carried by the vehicleO
U.S. Patents 3,834,278 and 4,050,474 disclose such types
of controllers. In U.S. Patent 3,834,278 an axially
movable valve element controls flow from a source in
response to rotation of an input shaf t connected with the
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vehicle steering wheel. When the controller is in a
neutral condition, all flow from -the source is
directed to the auxiliary motor. When the controller
is placed in an operating condition, needed flow to
the steering motor is metered and directed to the
steering motor, and excess f]ow is directed to the
auxiliary motor. ~n U.S. Patent 4,050,474 a control
valve comprises a pair or rotatable valve ~lembers
coupled together by a lost motion connection. One
valve element is fixed with the input shaft and the
other valve element is connected with one of a palr of
gerotor gear elements forming the metering section.
The controller of each of the foregoing patents
includes a fairly large, complex cast ho~sing member.
In the controllers of U.S. Patents 3,83~,278 and
4,050,474 the cast housing members enclose the valve
section and also include parts of the flow control
passages. In U.S. Patent 3,895,888, a cast housing
member encloses the metering section and the rotatable
plate valve member, and also forms an opening shaped
to receive the bearings and seals which support and
seal the input shaft. To form such cast housing
members properly usually requires a nu~ber of precise
machining steps. Also, the cast members are usually
bulky, and, being cast of iron, constitute a
significant portion of the overall weight of the
controller.
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The controller disclosed in each of the ~oregoing
patents also includes a spring centering mechanism which
biases the control valve toward a neutral condition.
Rotation of the input shaft actuates the valve element
against the bias of the spring centering mechanism. In
U.S. Patent 3,895,888 (~igs. 14-16) the spring centering
mechanism includes a spherically shaped detent which is
spring biased in a radial direction into a V-shaped groove
in the rotatable plate valve member. In U.S. Patent
3,834,278 the spring centering mechanism comprise-s a
torsion rod disposed on a bore wlthin the axially movable
valve member. The torsion rod is twisted or wound by
movement of the valve member away from neutral, and
unwinds to urge the valve member to the neutral condition
when steering effort ceases. In U.S. Patent 4,050,474 the
spring centering mechanism comprises a series of leaf
springs compressed against the housing and against ~he
relatively rotatable valve members.
The controller of U.S. Patent 3,834,278 also has
pressure dams for blocking leakage of metered fluid to a
low pressure return port when the controller is in an
operating condition. Pressure dam grooves are disposed
between grooves at metered ~luid pressure and at return
pressure. In neutral, inlet ~luid pressure, which is
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close to metered fluid pressure, is communicated with the
pressure dam grooves. When the controller is in an
operating condition only one pressure dam groove is needed
to block leakage of metered fluid to return. The other
pressure dam groove forms part of a flow passage directing
flow from the motor to a reservoir. In such controllers a
check valve or a specially designed orifice is usually
used to minimize flow from the pump through whichever
pressure dam groove is in the latter condition.
In Canadian Patent Application Serial No. 336,108, a
controller is disclosed in which pressure dams are formed
in a different manner. Specifically, in neutral there is
communication between the pump and the reservoir through
the pressure dam grooves. Check valves are used to
minimize flow through the pressure dam grooves in this
condition. Pressure dams are created by relative movement
of a pair of valve members to an operating condition in
which they block flow through the pressure dam grooves.
The controller of U.S. Patent 3r83~,278 also shows a
typical dynamic seal arrangement for minimizing leakage of
high pressure fluiA about the input shaft. A specially
formed bore in the housing encircles the input shaft, and
an arrangement of elements forming a dynamic seal are
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disposed between the bore in the housing and the rotatable
input shaft.
Summary of the Invention
The present invention provides a eompact integral
steering controller having a metering section, and a valve
section which is formed by a stacked assembly of plate
- valves, in accordance with the broad concept of TJ.S.
Patent 3,895,888, and which also improves upon the
eontroller disclosed therein in several important aspects.
One improvement is that the construction of the
eontroller of the invent;on minimizes the use of complex
east housing parts, which add considerably to the weight
of a controller and which often require a number of
precise macnining steps to manufacture. The controller
includes a metering section and a control valve section
disposed between a pair of end platesO An input shaft
extends through one o~ the end plates to provide an input
signal for operating the controller. In the control valve
section a unique stacked assembly of plate valves not only
eontrols flow but also defines a part of the outer
periphery of the controller, thereby eliminating cast
housing parts in the valve section. The metering section
includes a gerotor type metering mechanism disposed within
a thin tubular shell which, along with the end plates,
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defines the remainder of the outer per;phery oE the
controller. The thin tubu]ar shell, which in the
preferred embodiment is the only cast housing piece in the
controller, is relativel~ simple in shape and is
relatively light in weight in comparison to cast housing
pieces which have been sugges-ted for previous controllers.
Another improvement of the controller of the present
invention is that it is very compact, and yet is designed
to both meter needed flow to the steering motor and direct
excess flow to an auxiliary motor. The stacked assembly
of plate valves forming the control valve section is
constructed such that when the control valve section is in
neutral all flow is directed to the auxiliary motor, and
communication between the source and the metering section
is blocked. In response to rotation of the steering
wheel, flow is metered and directed to the steering motor,
and flow to the auxiliary motor is gradually restricted as
a function of the extent o~ movement of the control valve
section away from its neutral condition.
A further improvement of the contro31er of the
invention is the spring centering mechanism which biases
the control valve section to a neutral condition. The
control va]ve section preferably comprises a rotatable
plate valve ~ember disposed between a pair of plate valve
members which are fixed in the controller. The rotatahlè
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plate valve mernber includes one or more arcuate slo~s each
oE which is aligned with an arcuate slot in one of the
adjacent fixed plate valve members. One or more helical
springs are each disposed partially in an arcuate slot in
the rotatable plate valve member. Each suc~ helical
spring is also disposed in, and compressed in, the aligned
arcuate slot in the one of the fixed plate valve members.
At least one such helical spring is also compressed in the
arcuate 510t in the rotatable plate valve member to exert
a centering ~orce on the rotatable plate valve member to
bias the plate valve member to the neutral condition.
Each spring is compressea further by a predetermined
amount of rotation of the rotatable plate valve member
away from the neutral condition. By varying the length of
the aligned slots the spring centering ~orce exerted at
predetermined amounts of relative rotation of the plate
valve rnembers can be precisely controlled.
Still another improvement of the controller of the
invention resides in simply formed structure which creates
a pressure dam for resis-ting leakage of metered fluid to
return when the rotatable plate valve member is moved away
from the neutral condition and to an operating condition.
The fixed and rotatable plate valve members have end
surfaces in abutting, sliding relationship with each
other. A pressure dam groove is formed in the end surface
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of one of the relatively movable plate va~ve members~
When the plate valve members are in the neutral condition
the pressure dam is communicated with a return port,
but the plate valves cooperate to block flow between the
S inlet port and the return port. In response ~o rela~ive
movement of the plate valve members to an operating
condition the pressure dam groove is disposed between a
flow path containing metered fluid and a flow pa~h
containing low pressure return fluid. The abutting end
surfaces o the relatively movable plate valve members
cooperate such that in response to movement o~ the plate
valve members to an operating condition a static body of
fluid is created in the pressure dam groove. Pressure
from the inlet port is communicated with the pressure dam
groove to bring the pressure in the pressure dam groove to
inlet pressure, which is close to the pressure of the
metered fluid. The pressure dam groove is simply formed
and without the use of a valve or an oxi~ice to block flow
therethrough, ~ecause neither in neutral nor in an
operating condition is ~he pressure port expected to
communicate with the return port through the pressure dam
~roove. ` - -
Yet ano~her feature of the present invent;on resides
in the structure or sealing the input shaft against
leakage of high pressure fluid. The inp`ut shaft extends
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-through one of -the end plates of the controller and is connected for joint
rotation with a drive plate having a radial surEace which is in facing relation
with an interior surface of the end plate. Sealing is effected by a special
arrangement of elements surrounding the input shaft and disposed between the
facing surfaces of the drive member and the interior surfaces of the end plate.
The elements include a sealing ring of resilient compressible material encirc-
ling the input shaft and being compressed between the facing surfaces of the
drive plate and the end plate, a thrust bearing circumscribing the sealing ring
for setting a minimum spacing between the facing surfaces and for taking up
axial forces, and a spacer ring between the sealing ring and the input shaft
for preventing radial extrusion of the sealing ring. This seal arrangement
may be simpler to construct than previous types of input shaft seals, because
it does not require specially formed grooves in a housing to support the sealing
elements. Yet it is believed to provide effective sealing against leakage of
fluid.
Broadly stated, the present invention provides a controller for
controlling fluid flow from a source to a primary motor and to an auxiliary
motor, said controller comprising an inlet port for connection to said source,
a return port for comlection to a reservoir, a pair of working po:rts for con-
nection to opposite sides of said primary motor, an auxiliary port for
connection to said auxiliary motor, a metering section for metering fluid flow
in response to an input signal, said metering section including a gerotor gear
set comprising a pair of relatively rotatable and orbital gear members defining
expandable and contractable fluid pockets in response to rela-tive rotational
and orbital movement thereof, commutation valve means for controlling fluid
flow between a pair of fluid chambers and said fluid pockets in timed relation
to the relative orbital and rotational movement oE said gear members, and a
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control valve section :Eor directing fluid flow to the auxil:iary motor and
for directing fluid flow to the primary mo-tor in response to said input signal,
said control valve section comprising a series of adjacent plate valve members,
said series of plate valve members being biased to a neutral condition and
being relatively movable away said neutral condition to an operating condition,
and means for effecting relative movement of said plate valve members in
response to said input signal to position said plate valve members in said
operating condition, said plate valve members including relatively movable
facing end surfaces which cooperate to direct all flow from said source to
said auxiliary motor when said plate valve members are in said neutral condi-
tion, and to restrict flow to said auxiliary mo-tor and direct flow to said
primary motor as a function of the extent of the relative movement of said
valve plate members away from said neutral condition.
The invention and that of application Serial No. 354,772 will
now be described in greater detail with reference to the accompaning draw-
ings:
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Figure 1 is a schematic representation of a fluid system
having a controller according to the invention for controlling fluid
flow to a steering motor and an auxiliary motor;
Figure 2 is a longitudinal sectional view of the controller
of Figure l;
Figures 3 and ~ are views of opposite sides of a manifold
plate valve member in the controller of Figure 2, taken respectively
along the lines 3-3 and ~-4 of Figure 2;
Figures 5 and 6 are views of opposite sides of an
isolation plate va~ve member of the controller of Figure 2, taken
respectively along the lines 5-5 and 6-6 of Figure 2;
Figure 7, on the same drawing sheet as Figures 3 to 5
is a sectional view of the isolation plate valve member of the
controller of Figure 2, taken along the line 7-7 of Figure 2;
Figure 8 is a view of one end surface of a movable plate
valve member forming part of the controller of Figure 2;
Figure 9 is an enlarged view oE an area of the plate valve
member of Figure 8;
Figure 10 is a sectional view of Figure 9, taken along
the line 10-10 of Figure 9;
Figure 11 is a view of one side of the gear set forming
part of the metering section of the controller of Figure 2, taken
along the line 11-11 of Figure 2, with certain portions omitted;
Figure 12 is a view of one side of the commutator valve
for controlling flow to and from the fluid pockets of the metering
section of the controller of Figure 2, taken along the line 12-12
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of Figure 2;
Figure 13 is an enlarged perspective view of a spring
centering mechanism embodied in the controller of Figure 2;
Figure 14, on the same drawing sheet as Figures 8 to
10, is an enlarged view of an input shaft seal embodied in the
controller of Figure 2;
Figures 15 and 16, on the same drawing sheet as Figure
6, are views of opposite sides of the movable plate valve member
of the controller of Figure 2, taken along the lines 15-15 and
16-16, respectively of Figure 2, with the fluid passages in the
face of the adjacent fixed plate val~e member superimposed
thereon;
Figures 17 and 18 are enlarged representations of
opposite sides of the movable plate valve member, with the flow
passages in the faces of the adjacent fixed plate valve members
superimposed thereon and showing the relative positions of the
plate valve members when the mova~le plate valve member has been
rotated i~n one direction to an operating condition in which the
member cuts off all flow to the auxiliary motor; and
Figure 19, on the:same drawing sheet as-Figure 17; is
an enlarged fragmentary view of a surface portion of the movable
plate valve member showing how flow
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is gradually restricted to the auxiliary motor before
reaching a position where Elow to the auxiliary motor is
cut o~f.
Detailed Description of the Preferred Embodiment
. . .
As discussed above, in addition to having a number of
improved structural features, a controller according to
the invention is also designed to meter Elow from a source
to a primary motor, such as the steering motor of a
vehicle, and to direct excess flow to an auxiliary motor
for oper`ating additional equipment carried by the
vehicle. Fig. 1 shows a controller 10 according to the
invention in a hydraulic system including a steering motor
12 and an auxiliary motor 13. The controller 10 is
operated by an input signal from a vehicle steering wheel
14, and directs flow from a pump lS to the vehicle
steering motor 12 and to the auxiliary motor 13.
As is known, the amount of flow needed for steering
may vary, depending upon factors such as the rate of
movement of steering wheel 14, the amount of turning
desired, etc. The controller 10 assures that as much of
the output of the pump 15 as is needed for steering is
metered and directed to the steer;ng motor 12. Excess
flow from the pump, i.e., flow beyond that needed for
steering, is directed to the auxiliary motor 13 (under the
further control of a manually operated valve 16). When no
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steering is taking place, the controller 10 :is in a
neutral condition in which it directs al]. of the flow from
pump 15 to the auxiliary motor 13.
Referring to Fig. 2, the controller 10 includes a
valve section 17 and a metering section 18 disposed
between a pair of end plates 19, 20. The valve section 17
includes a stacked assembly of plate valves disposed
adjacent end plate 19. The metering section 18 includes a
gerotor gear type metering mechanism disposed within a
thin cylindrical tubular shell 21. The assembly of valve
plates, and the cylindrical tubular shell 21 are clamped
between the end plates 19, 20 by means of a series of
bolts 22 which extend through the plate valves and the end
plates 19, 20 and are locked in place by respective nuts
23.
An input shaft 24 connected with the steering wheel
14 extends through the end plate 20. The input shaft 24
is coupled for joint rotation with a drive plate 25 which
is disposed within the tubular shell 21. The drive plate
25 has a cylindrical outer surface 25a which is rotatably
supported on the cylindrical inner surface 27 of the
tubular shell 21. Rotation of the input shaft 24 and the
drive plate 25 transmits the input signal from the
steering wheel 14 to operate the elements of the
controller as described more fully hereinafter.
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The end plate 19 includes an inlet port 26 connected
with the pump 15, a return port 28 connected with a
reservoir 30, a pair of cy].inder ports 32, 34 connected
with opposite chambers of the steering motor 12, and an
auxiliary port 36 connected with the auxiliary motor 13.
The valve section 17 controls flow between the
various ports and the mètering section 18. When no
steering is taking place, the valve section 17 is biased
to a neutral condition in which it directs flow from the
inlet port 26 to the auxiliary port 36 and blocks
communication of the inlet port 26 with the metering
section 18. Rotation of the steering wheel 14 moves the
valve section 17 away from the neutral condition and
places the controller in an operating condition. When the
valve section 17 is in an operating condition fluid from
the inlet port 26 is metered and directed to one of the
cylinder ports 32, 34 to pressurize the associated chamber
of the steering motor 12. Flow returning from the
contracting chamber of the steering motor is directed
through the other cylinder port to the return port 28,
which is connected with reservoir 30.
The need to direct a greater proportion of the output
of the pump to the steering TnOtOr increases with movement
of the valve section away from the neutral condit;on.
During a steering maneuver, as the steering wheel 14
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rotates the valve section 17 away from the neutral
condition to direct metered flow to one cylinder port,
flow to the auxlliary port 36 is gradually restricted as a
function of the extent oE movement of the valve section
away from the neutral condition. Only excess flow, i.e.,
beyond that needed for s~eeriny, is directed to the
auxiliary mo-tor. If the steering wheel rotates the valve
section far enough away ~rom the neutral condition, such
as during an extremely rapid steer;ng maneuver, all flow
from the pump 15 is directed to operate the steering motor
12, and flow to the auxiliary motor 13 is cut off.
Referring to Figs. 2 and 11, the metering section 18
includes a gerotor gear set having an outer gear member 4
with internal teeth and an inner gear member 46 with
external teeth. The inner gear member 46 has one less
tooth than the outer gear member 44. The outer gear
member 44 is fixed to the drive plate 25 and rotates
jointly with the drive plate 25 and the input shaft 24
about a common central axis 48. The inner gear member 46
has a central axis 50 which is eccentrically disposed with
respect to the central axis 48. With this construction,
the gear members 44, 46 are adapted for relative
rotational and orbital movement, as w;ll be readily
recognized hy those o~ ordinary skill in the art.
The intermeshing teeth of the gerotor gea~ members
44, 46 define expansible and contractable fluid pockets 52
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(Fig. 11). As the gear members rotate and orhit relative
to each other, some of the fluld pockets 52 are expanding
while other fluid pockets are contracting. A commutation
valve 54 tFig. 12), described more fully hereinafter,
controls flow to and from the expansib~e and contractable
fluid pockets 52 in timed relation to ~he movement o~ the
gerotor gear members.
As noted above, the control valve section 17 includes
a stacked assembly of plate valve member.s fixed adjacen~
the end plate 19. The fixed plate valve members incluc3e a
valve ring 55 sandwiched between a manifold plate valve 58
and an isolation plate valve 70~ A pair of static seals
57 prevent fluid leakage between the valve ring 55, the
manifold pla~e vaive j~ anci Irie lsola~lon pia~e va lve 7~.
The valve ring 55 includes a central opening 59 defining
part of a chamber therein, and a rotatable pla~e valve
member 56 is supported in that chamber for rotation about
the central axis 48.
The manifold plate valve member 5~ comprises three
plates 60, 62 and 64 bonded together by copper ~razilly,
and includes an end surface 66 abutting, and in relatively
sliding engagement with, one end surface 68 of rotatable
plate valve member 56. The isolation pla,e valve member
70 comprises four plates 72, 74, 76 and 78 bonded together
by copper brazing and includes an encl surface 80 abuttin~,
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and .in relatively sliding engagement with, the other end
surface 82 of the rotatable plate valve member 56.
A wobble shaft 84 having a central axis 86 disposed
at an angle to the central axis 48 is adapted to rotate
the plate valve member 56 ~ointly with the inner gerotor
gear member 46. The wobble shaft 84 is also supported in
such a manner that it can pivot relative to the gear
member 46 and the plate valve member 56 to allow the inner
gerotor gear member 46 to orbit with respect to the outer
gerotor gear member 44.
The plate valve member 56 is spring biased to a
neutral condition relative to fixed plate valve members 58
and 70, as described more fully hereinafter. In a neutral
. condition the plate valve members direct Elow from the
inlet port 26 to the auxiliary port 36. The plate valve
members also isolate the inlet port 26 from the metering
section 18 so that no flow is directed from the pump to
the metering section 18. As the steering wheel 14 rotates
the input shaft 24, torque is transmitted through the
gerotor gear members 44, 46 to rotate the plate valve
member 56 relative to the fixed plate valve members 58, 70
in order to move the plate valve member 56 away ~rom the
neutral condition and to place the valve section 17 in an
operating condition.
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A pair oE chambers 88, 90 (separated by a sealing
member 9].) are disposed adjacent the metering section 18.
When the valve section 17 is placed in an operating
condition, the plate valve members 56, 58 and 70 estab].ish
fluid communication be~ween the inlet port 26 and one of
the chambers 88, 90. The plate valve members also
establish fluid communica~ion between the other of
chambers 88, 90 and one of the cylinder ports. The
commutation valve 54 communicates the chambers S8, 90 with
the fluid pockets formed by the gerotor gear members 44,
46 such that flow from the chamber 88 or 90 which is
connected to inlet port 26 is directed to the fluid
pockets which are expanding and flow from the fluid
pockets which are contracting is directed to the other of
chambers 88, 90 and thereby to the cylinder port which is
being pressuriæed.
Flow is gradually restricted to the auxiliary port 36
as a function of the degree of movement of the plate valve
member 56 away from the neutral condition. If the plate
valve member 56 is moved far enough away from neutral ~as
during an extremely rapid steering maneuver) flow to the
auxiliary port 36 is shut off, and all flow is metered and
directed to the steering motor through one of the cylinder
por-ts 32, 34.
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The various ports are formed similarly to auxiliary
port 36 which is shown in section in Fig. 2. The port 36
includes a tubular element 92 extending through an opening
in the end plate 19. The tubular element 92 includes a
central opening 96 defining a fluid passage which
communicates with one side of the manifold plate valve
member 58. A static sealing ring 98 surrounds the fluid
passage 96. Similarly, each other port also comprises a
tubular element extending through end plate 19 and
defining a fluid passage surrounded by a static sealing
ring.
As discussed above, the manifold plate valve member
58 includes three plates 60, 62, 64 which are bonded
together by copper brazing. As seen in Fig. 2, the
15 manifold plate valve member 58 includes end surface 100
which is adjacent the end plate 19, and end surface 66
which is adjacent the end surface 68 of the rotatable
plate valve member 56. A static sealing ring 99 is
disposed between end plate 19 and the manifold plate 58.
Figs. 3 and 4 show the opposite sides of the manifold
plate valve member 58. Formed in the end surface 100 is
an inlet passage 102, an auxiliary passage 10~, a return
passage 106, and a pair of cylinder passages 108, 110, all
of which communicate with their respective ports. The
25 inlet passage 102 and auxilary passage 104 are each
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circular and extend axially through the plates 60, 6Z,
64. Each of the cylinder passages 108, 110 comprises a
circu].ar passage which extends through the plates 60, 62
and communicates with a respective flat sided passage 114,
112 extending through plate 64 and foeming a window in the
end face 66. Further, a pair of passages llfi, 118
extending through plate 64 form metering windows in the
end surface 66 of the plate valve member 58. ~dditionally,
another pair oE passages 120, 122 extending through plate
64 form windows on opposite sides of the aux;liary passage
104.
A passage 124 extending through plate 64 forms a
return window in the end face 66. The return window 124
communicates with the return passage 106 in plate 60 by
means of a passage 126 Eormed in the intermediate plate
62. A tear drop-shaped passage 128 formed in the
intermediate plate 62 communicates the inlet passage 102
with another passage 130 in the plate 60. This latter
passage communicates inlet pressure with a recessed cavity
. 20 131 (Fig. 2) formed in the surface of end plate 19
adjacent the manifold plate valve member 58 in order to
pressure balance the stacked assembly of plate valves
forming the valve section 17.
As seen in Fig. 4 the plate 64 includes three
circumferentially spaced arcuate slots 132 having radial
3 1 (~
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end walls 132a . These slots are in the end surface 66 of
the manifold plate valve member 58 which is adjacent the
rotatable plate valve member 56. The arcuate slots 132
form part of the spring centering mechanism described
hereinafter.
Referring to Figs. 2, 5, 6 and 7 the isolation plate
valve member 70 includes a series of four plates 72, 74,
76, 78 bonded together, also b~ copper brazing
techniques. Plate 72 includes an end face 80 adjacent the
rotatable plate valve member 56. Formed in end face 80
are auxiliary window 134, a pair of windows 136, 138 on
opposite sides of auxiliary window 134, a return window
143, a pair of inlet windows 140, 142, and a pair of
cylinder windows 144 r 146. A passage l48 extending
through plate 72 forms a metering window in end surface
80. A series of holes in plate 74, 76 and 80 form a
passage 150 which extends through the plate valve member
to its backside (see Fiq. 6) and which communicates the
metering window 148 with chamber 90. Another passage 154
in plate 72 forms a metering window in end surface 80.
The metering window 154 includes a central openinq in
plate 72, which communicates the metering window 154 with
a series of central openings in the plates 74, 76, 78 (one
is shown at ]56 in Fig. 6, and another at 205 in Fig. 7).
These control openinqs communicate meterinq window 154
with chamber 8$.
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The plate 72 also includes three circumferentially
spaced arcuate slots 158 having radial end wa]ls 158a.
The slots 158 are in the end surface 80 of the lsolation
plate valve member which is adjacent the rotatable plate
valve member 56. The slots 158 form part of the spring
centering mechanism described more fully hereinaEter.
As seen in Figs. S and 7 the inlet windows 140, 142
in the isolation plate valve member 70 extend through
plates 72, 74 and communicate with a slot 160 in the
intermediate plate 76. This communicates the inlet
windows 140, 142 with each other.
The commutation valve 54 shown in Figs. 2 and 12
includes plate valve structure including a pair of p7ates
162, 164 bonded together by copper brazing and disposed
15 within a valve ring 165. The plates 162, 164 are coupled
to the inner gerotor gear member 46 for movement therewith
by means of a series of pins 166 disposed in respective
slots 163, 167 in the commutation valve and the inner gear
member.
The drive plate 25 which is ~ixed to the input shaft
24, is disposed adjacent one side of the pockets formed by
the gerotor gearset to seal the pockets against leakage
therefrom. One end surface 177 of the commutat;on plate
valve structure is disposed adjacent the other side of the
gearset and communicates fluid to and from the pockets
I lB~31(~
-2S-
from that side. A pressu~e plate 178 adjacent the other
end surface 179 of the co~utation valve structure is
clamped to the outer gerotor gear member 44 and the drive
plate 25 by a series of bolts 180. This construction
maintains a uniform and relatively small clearance between
drive plate 25 and the commutation plate valve structure
regardless of pressures in the fluid pockets.
The commutation valve 54 includes pairs of fluid
openings 168, 170 (Fig. 12) which are adjacent the fluid
pockets formed by the gearset. Fluid passages 172 connect
the fluid openings 168 with a central opening Eorming part
of the chamber 88. The openings 170 communicate directly
with the outer periphery of the commutation valve wnich
defines part of the chamber 90.
During a steering maneuver, rotation of the steering
wheel 14 rotates the drive plate 25 and the outer gerotor
gear 44. Torque transmitted between the teeth oE the
gerotor gear members causes the inner gerotor gear member 46
to rotate slightl~ to rotate the
valve member 56 away from the neutral condition and to an
operating condition. When the valve member 56 is in an
operating condition, one of the chambers 88, 90 is
commun;cated with the inlet port 26 and the other chamber
is communicated with one oE the cylinder ports. The
relative orbital and rotational movement of the ~ear
7 ~3 ~(~
-26-
members ~4, 46 valves the openings 168, 170 in the
commutation valve such that whichever of chambers 88, 90
is connected with the inlet port 26 communicates inlet
fluid with the expanding pockets of the metering
mechanism, and the other chamber, which is connected with
the cylinder port, receives metered fluid from the
contracting pockets. Such co~utation is in accordance
with the principles disclosed in U.S. Patent 3,598,509.
The rotatable plate valve member 56 includes a series
of arcuate openings extending axially therethrough and
forming windows in both end surfaces 68, 82 of the plate
valve member. As seen in Fig~ 8 the arcuate openings
include an auxiliary opening 182, and a pair of inlet
openings 184, 185 on each side thereof. The arcuate
openings further include a return opening 186, a pair of
cylinder openings 188, 789, and a pair of metering
openings 190, 191.
The plate valve member 56 also includes a hexagonal
shaped central opening 192. A hexaqonal block 194 is
shaped to fit snugly in the hexagonal opening 192 (Figs.
2, 15, 16) so that the plate valve member 56 rotates
therewith. A pin 196 is rotatably journaled in the
hexagonal block 194 and also in the fixed manifold plate
valve member 58.
3 1 6~3 1 (~
-27-
-
The hexagonal block 194 includes a slot 198 of
generally rectangular cross section (Fig. 7). The wobble
shaft 84 has an end portion 199 wh;ch extends into the
slot 198 and couples the block 194 with the inner gerotor
gear 46 for joint rotation while allowing the wobble shaft
to rock and to slide in the slot 198 in order to follow
the orbiting movement of the inner gerotor gear. The end
portion 199 of the wobble shaft includes side surfaces 201
(F;g. 7~ which are segments of a spherical generated
profile, and upper and lower segments each of which
comprises a pair of converging flat surfaces 203 joined by
a slightly curved surface 203a (Fig. 2~. With this
configuration, the end portion 199 can rock and slide
axially in the slot 198 to allow the wobble shaft to
follow the orbiting movement of the inner gerotor gear
member 46. The end portion 199 will, however, act upon
upper and lower surfaces 198a, 198b of the the slot 198 to
rotate the hexagonal block 194 and thereby the plate valve
member 56 jointly with the wobble shaft 84 (see Fig. 7).
The inner gear member 46 also includes a slot 200.
An end portion 204 at the other end of the wobble shaft 84
is shaped similarly to the end portion 199, and extends
into the slot 200. The engagement of end portion 204 with
the slot 200 al]ows the wobble shaft to rock and slide
25 axially in the slot 200 as the inner gear member 46
3.~. n
-2~-
-
orbits, but co~ples the wobble shaft with the gear member
46 for joint rotation. Thus, the enga~ement of the end
portions 199, 204 of the wobble shaEt 84 with the slots
198, 200 couples the inner gear member 46 and the
hexagonal block 194 for joint rotation, and allows the
wobble shaft 84 to pivot relative to the hexagonal block
194 and the inner gear member 46 ~s the inner gear member
rotates and orbits.
The range of rotation of the inner gear member 46 and
the plate valve member 56 is limited. As seen in Fig. 7
the central opening 205 in the isolation plate valve
member 70 forms a series of stops 205a The stops 205a
cooperate with the corners 206 of the hexagonal block 194
to limit the range of rotation of the hexagonal block and
the plate valve member 56. Thus, they limit the range of
rotation of the inner gerotor gear member 46.
When the input shaft 24 is rotated to effect a
steering maneuver~ it rotates the outer gerotor gear
memher 44. Rotation of the outer gerotor gear member 44
causes the inner gear member 46 to initially rotate.
The plate valve member 56 rotates with the gerotor
gear member 46 to place the plate valve member 56 in an
operating condition. If the gerotor gear member ~6 and
the plate va~ve member 56 are rotated to their extrerne
3 1 ~
-29-
position, continued rotat;on of the outer gerotor gear
member ~ with the input shaft thereafter results in only
orbiting movement of the inner gerotor gear member 46.
The broad principles and advantages oE a controller in
which torque is transmitted through a gerotor gearset to a
valve member whose range of rotation from neutral is
limited is disclosed in U.S. Patent 3,895,888.
The spring centering mechanism exerts a centering
force on plate valve member 56 to bias the plate valve
member 56 to the neutral condition. During a steering
maneuver the centering force must be overcome in order to
rotate the plate valve member 56 away from the neutral
condition and to an operating condition. The spring
centering mechanism returns the plate valve member 56 to
the neutral condition when the steering effort ceases.
The plate valve member 56 includes three arcuate
slots 208 which are aligned with the arcuate slots 132,
158 in the manifold and isolation plate valve members when
the plate valve members are in neutral. Each of the
arcaate slots 208 includes radial end walls 208a. As set
forth above, each of the arcuate slots 132, 158 in the
fixed plate valve members have respective end wa]ls 132a,
and 158a.
A pair of helical springs 207, 209 are disposed
partially in each slot 208 in the rotatable plate valve
member 56 (Fig. 13). The helical spring 207 is also
3 ;~ ~
-30-
-
d.isposed in the slot 132 in the man;fold plate valve
member 58. The helica]. spring 209 is also disposed in the
aligned slot 158 in the f;xed isolat.ion pl.ate valve member
70. Both helica] springs 207~ 209 are compressed against
the respectlve radial end wal~s 132a, 158a of the slots
132, 158 in the fixed plate valve members. Springs 207,
20g have oppositely directed helices which maintains the
springs in abutting relation and prevents their coils from
interfering with each other.
The spring 20~ is compressed between the radial end
walls 208a of the plate valve member 56 and the end walls
1.58a of the plate valve member 70. The arcuate slot 208
in plate valve member 56 and the arcuate slot 158 in the
iso]ation plate valve member 70 are equal in length. The
radial end walls 158a, 208a of the slots are also aligned
with each other so that the spring 209 is also compressed
between radial walls 208a of slot 208 of p]ate valve
member 56 as well as between radial walls 158a of slot ].58
in isolation plate member 70. The spring 209 thus exerts
a centering force on the plate valve member 56 biasing the
plate valve member 56 to the neutral cond;tion. The
centering force must be overcome to move the plate valve
member 56 away from neutral. The centering spring force
preloads the plate va].ve memher in neutral and also
provides the steering wheel operator with a "Eeel" of the
~6~3~
~31-
neutral valve pos;tion s;nce the preload force must be
overcome prior to initiating valve movement or a steering
maneuver.
The arcuate slot 132 in manifold plate va].ve member
58 is shorter than the slots 158, 208. Its radial end
walls 132a are equidistantly spaced from the end walls
158a, 208a of the slots 158, 208. Spring 207, which is
compressed against the end walls 132a of slot 132, does
not exert a centering force on plate valve member 56 when
plate valve member 56 is in the neutral condition.
When plate valve member 56 is rotated a~Yay from the
neutral condition the spring 209 is further compressed
between one of the end walls 208a in plate valve member 56
and the opposite end wall 158a in the fixed isolation
plate valve member 70. This increases the force in spring
209 urging the plate va].ve member 56 back to its centered
position. When the plate valve member 56 rotates away
from neutral by a predetermined amount it also compresses
the spring 207 between t~e radial end wall 208a and the
opposite end wall 132a in the slot 132 in the fixed
manifold plate valve member 58. This substantially
increases the force urging the plate valve member 56 back
to îts neutral condition.
In the preferred embodiment it has been found
desirable that the spring centering force provide lighter
3 ~ n
-32-
res;stance to movement of the plate valve member 56 away
from neutral over approximately half its potent;al path of
travel away from neutralr and that the spring centering
force increase significantly at about half the path of
travel of the p].ate valve member 56 away from neutral.
This is accomplished by designing the size of slots 132,
158 and 208 such that the spring 207 .is not compressed
until the plate valve member 56 rotates away from neutral
by approximately half its potential length of travel.
This provides a qood correlation between the steering
effort required to rotate the plate valve member 56 and
the fluid pressure re~uired at the steering motor.
As sho~ld be clear from the foregoing, each spring
207, 209 acts individually to resist rotation of the plate
valve member 56 away from neutral. The point at which
spring 207 is cGmpressed further by rotation of plate
valve member 56 away from neutral, and the force w;.th -
which it acts~ depends primarily upon the respective
lengths of the aligned slots 132, 158, 208, and also the
load ~ersus deflection rate of the springs 207, 209. By
varying the size of the slots, or the spr;ng coefficients
of springs 207, 209, the point at which spring 207 acts,
and the force with which it acts can be varied.
In addition, the foregoing principles can be used to
apply add;tional amounts of spr;.ng force at d;screte
-33-
increments o~ movement of the p]ate valve metnber 56 away
from neutral. E'or example r in the disclosed ernbodiment
three sets of aligned slots 132, 158, 208 and cooperating
springs 207, 209 are shown. Only one set need have the
construction oE slots 158~ 208 and spring 209 to provide
the spring centering force on the plate valve member 56 in
the neutral conditlon. The remaining five springs and
their respective slots can be similar to the spring 207
and the slots 132, 208 in that the sprin~s begin to act
only at a predetermined amount of rotation of the plate
valve member 56 away from the neutral condition.
Turning now to the actual flow of fluid in the
controller, in neutral all flow is directed to the
auxlliary port 36, and flow is isolated from the metering
section 18. In neutralr -inlet Eluid communicates with the
arcuate slots 184~ 185 (see Figs. 15, 16) in the movable
plate valve member 56. The arcuate slots 18~, 185 are-
overlapped by windows l36, 138 in the isoJation plate
valve member 70 and windows 120, 122 in the manifold plate
valve member 58. The windows 120, 122, l36 and 138 also
overlap auxiliary slot 182 in the movable plate valve
member 56. Slot ]82 communicates with the auxiliary
passage 104 in the manifold plate valve member. Thus, a
flow of ~luid is directed to the auxiliary passage 104.
This flow is directed to the auxiliary port 36. The plate
~ ~431(3
-3~-
-
valve members block the metering windows 1~8, 154 in the
isolation plate valve member from communicating with the
chambers 88, 90. Thus, in neutral all flow ~rom the inlet
port is directed to the au~iliary port, and ~luid is
S isolated from the metering section 180
Upon a predetermined amount o~ movement of the plate
valve member 56 in one direction away from neutral, flow
across slots 184, 185 to the auxiliary window 182 is
blocked (Figs. 17r 18). Inlet fluid is communicated
across slot 185 to one metering window 148 in the
isolation plate valve member 70. The inlet fluid is
thereby directed to the chamber 90. The commutatio~ valve
54 directs ~luid from chamber 90 to the expanding pockets
of the metering mechanism, and fluid from the contracting
pockets of the metering mechanism is directed to the other
chamber 88. The chamber 88 communicates with the metering
window 154 in the isolation plate through the central~
openings (e~g., 156, 205) in the isolation plate valve
mem~er 70O
The metered fl~id communicated with the metering
window 154 is directed across slot 18~ in plate valve
member 56 to the cylinder window 144 in the maniEold plate
valve member 58. From the cy~inder window 144 it is
communicated with one of the cylinder ports. Flow
returning from the other cylinder port communicates across
1 ~ 6~3 1 ~J
~35-
windows 1~6, 143 in the maniEold pl.ate valve mem~er 70 and
slots ].86, 189 in the movable plate valve member 56. Such
flow .is a]so communicated with return window 124 in the
manifold plate va].ve member 5B and to the return port.
As the plate valve member 56 moves away from the
neutral condition, but before reaching the position of
Figs. 17, 18, there is a gradually increasing restriction
of flow from the inlet to the auxiliary port. This occurs
because of U-shaped grooves 210 in slots 18~, 185 of the
movabl.e plate valve member 56, and cooperating oppositely
directed U-shaped grooves 212 in the windows 120, 122 and
136, 138 of the fixed plate valve members (see Figs.
17-19). Certain of those U-shaped grooves move toward
each other as the plate valve member 56 moves initially
away from neutral (Fig. 19) and are u.ltimately over].apped
to increase restriction of flow from the inlet port to the
auxiliary port with increasing movement of the plate valve
members away from neutral. Rotation of the plate valve
members to an extreme position (Figs. 17, 18) moves those
~-shaped grooves past the overlapped relation, thereby
cutting off all flow from the inlet port to the auxiliary
port.
Rotation of the plate valve member 56 in the opposite
direction from that shown in Figs. 16 and 17 results in a
flow pattern with simi].ar characteristics but different
3 1 n
-36-
directions. That i.s, flow is across the metering window
154 in the isolation plate to chamber 88, and metered flow
is directed through chamber gO across the metering windo~
148 in the isolation plate valve member 70, and through
S window 146 in the manifold plate valve member 58 to the
other cylinder port. Return flow is directed from the
opposite cylinder port to the return window ].2~ in the
manifold p]ate valve member 58 and thereby to the return
port.
As noted abover a particular characteristic of the
controller of the invention resides in the manner in which
pressure dams are formed to block leakage of metered fluid
to return when the controller is in an operating
condition.
In the present .inventlon, the movable plate valve
member 56 is constructed such that when the controller is
placed in an operating condition, a pressure dam is
created to block leakage of metered fluid flow to return~
The pressure dam is created in one of a pair of pressure
-20 dam grooves 216, 218 formed in each end surface 68, 82 of
the plate valve member 56, and on opposite sides of the
return window 186. In neutral, the pressure dam grooves
216, 218 are at return pressure because they face the
return windows 12~ 3 in the manifold and isol.ation
plate valve members 58, 70, respectively. ~Towever, the
7~ it~
-37
-
plate valve members block flow from the inlet port to the
return por~, so there is no flow from the inlet port
through the pressure dam grooves when the plate valves are
in neutral.
Each surface of the plate valve member 56 includes a
pair of inner and outer arcuate pressure balance grooves
220, 222 respectively. These pressure balance grooves are
in continuous communication with the inlet windows 184,
185 in the plate valve member 56. Thus, they are
continuously at inlet pressure.
When the plate valve member 56 rotates to an
operating position, the pressure dam yrooves 2l6 or 218 in
both end faces oE the plate valve member 56 are disposed
between slots 188 and 18~ in the plate vatve member 56
which are, respectively, at metering pressure and at
return pressure. In the posltion shown in Figs. 17 and 18
pressure dam grooves 218 are in that position. Initially,
as the plate valve member 56 moves to an operating
condition those pressure dam grooves 218 each move into
facing relation with the adjacent end faces oE the
manifold and isolation plate valves to form a static
pocket of fluid. A groove 221 in the adjacent end surface
of each of the manifold plate valve 58 and the isolation
- plate valve communicates high pressure fluid
from the inner pressure balance groove 220 to each oE the
3 i n
-38-
pressure dam grooves 2l8. This brings the Eluid pressure
in the pressure dam grooves 21~ essentially to inlet
pressure. Therefore, there is very little pressure
differential between those pressure dam grooves and the
metered fluid pressure in the adjacent metering slot 188,
and this blocks leakage of Eluid from the metering slot
188 and to the return slot 186.
Upon rotation of the valve member 56 in an opposite
direction away from neutral, pressure dams are created in
the other pressure dam grooves 216 in each end face of the
plate valve member 56 to block leakage of metered fluid to
return. Inlet pressure in the outer pressure balance
grooves 222 is communicated to -the pressure dam grooves
216 by means of grooves 223 in the adjacent end surfaces
of the mani~old plate valve 58 and the isolation plate
valve 70.
The pressure dam grooves 216, 218, the arcuate
pressure balance grooves 220, 222 form part oE a series of
grooves which also pressure balance the opposite end faces
68, 82 of rotatable plate valve member 56. A series of
long radial pressure balance grooves 224 and short radial
pressure balance grooves 226 minimize unbalance pressures
from occurring on the plate valve member 56.
A further feature of the invention resides in the
arrangement which seals the input shaft 24 against
3..~ n
-39-
leakage. As shown in Figs. 2 and 14 a surface 229 on
drive plate 25 is in facing relation with an interior wall
230 of the end plate 20 which surrounds the input shaft
24. A needle bearing 234 spaces the surface 229 from the
interior wall 230 by a predetermined minimum amount ~
(Fig. 14). The needle bearing 234 al.so takes up axial
orces between the facing surfaces.
A sealing ring 232 of resilient compressible material
surrounds the input shaft 24 inwardly of the needle
bearing 234. The sealing ring 232 has an uncompressed
thickness greater than the minimum distance D set by the
needle bearing 234 and is compressed between the surface
229 and the interior wall 230 of end plate 20. A metal
spacer ring 228 between sealing ring 232 and the input
shaft 24 is dimensioned so that its axial end faces 240,
242 are closely spaced from the Eacing surEaces 229 J 230
in order to prevent radial extrusion of the sealing ring
232 due to fluid pressure. High pressure fluid (either
metered or inlet) communicating with the chamber 90 which
surrounds the commutator valve 54 is thus seal.ed against
leakage around the input shaft. The seal arrangement is
simple to construct and assemble, and yet ls effective to
seal the controller against leakage about the input shaft.
As seen in Fig. 2, the end plates 19, 20, the outer
periphery of the plate valves 55, 58 and 70 and the
3 ~ f)
--~o--
tubular shell 21 Eorm the outer periphery oE the
controller. The unique seal arrangement described above
seals the input shaft 24 against leakage of hi~h pressure
fluid. The controller is also sealed against leakage by
means of static seals 57 between ring 55 and the adjacent
fixed plate valves 58, 70, and static seal 99 between
manifold plate valve ~8 and the end plate 19. ~s seen in
Fig. 2, additional sealing is provided by static seals 244
at the ends of t'ne tubular shell 21 adjacent the isolation
plate 70 and end plate 20.
The fact that the valve section 17 and the tubular
shell are bolted between the end plates 19, 20 further
helps to minimize the likelihood of leakage because those
elements are forced tightly against each other. The high
pressure fluid directed to chamber 131 minimizes internal
leakage because it provides an equal area on either side
of the manifold plate exposed to high pressure and the
manifold plate valve therefore remains flat.
In the construction of the various elements of the
controller, the gear members 44, ~ are preferably formed
by known powder metal techniques. The vario~s plate
members which are used to form the controller are all
preferably stamped out of shee-t stee~ stock. The tubular
shell 21 is the only housing element which is preferably
cast of iron. However, as clearly seen from Fig. 2, this
1 ~43 1r)
~41~
element is fairly thin, and is relatively simplc in shape
in comparison to the bulkier, heavier and more complicated
types of housing elements which are usually used in
forming fluid controllers. Moreover, it is contemplated
that even this element may be made of powdered metal.
Thus, according to the foregoing description, the
applicant has provided what is believed to be a compact,
simply made, and yet efficient controller for controlling
f~ow from a source.
` ,
.
