IE20040688U1 - A fluid control valve - Google Patents
A fluid control valveInfo
- Publication number
- IE20040688U1 IE20040688U1 IE2004/0688A IE20040688A IE20040688U1 IE 20040688 U1 IE20040688 U1 IE 20040688U1 IE 2004/0688 A IE2004/0688 A IE 2004/0688A IE 20040688 A IE20040688 A IE 20040688A IE 20040688 U1 IE20040688 U1 IE 20040688U1
- Authority
- IE
- Ireland
- Prior art keywords
- flow
- spool
- fluid
- combiner
- motors
- Prior art date
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 107
- 230000001276 controlling effect Effects 0.000 claims abstract description 8
- 238000005461 lubrication Methods 0.000 claims abstract description 8
- 230000005540 biological transmission Effects 0.000 claims description 24
- 238000007906 compression Methods 0.000 claims description 13
- 230000000977 initiatory Effects 0.000 claims 1
- 230000001360 synchronised Effects 0.000 abstract 1
- 238000009987 spinning Methods 0.000 description 4
- 230000000903 blocking Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000006011 modification reaction Methods 0.000 description 2
- 230000001105 regulatory Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000001010 compromised Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Abstract
ABSTRACT The invention provides a fluid control valve for controlling the flow of hydraulic fluid from a hydraulic pump to and from a plurality of hydraulic motors. The valve conveniently includes selector valve for selectively energizing a flow divider/combiner spool that controls the flow of hydraulic fluid to and from the motors. The flow divider/combiner spool has on its periphery lubrication grooves which also act as metering grooves. An advantage of the fluid control valve of the invention is that it regulates and equalises the flow and pressure of the hydraulic fluid delivered between a hydraulic pump and a plurality of hydraulic motors, thereby enabling each hydraulic motor to rotate in a synchronized fashion when traction control is required and without the operator having to deactivate the valve, the valve will disengage once traction to all wheels has been regained.
Description
A FLUID CONTROL VALVE
The present invention relates to a fluid control valve for controlling the flow of hydraulic
fluid from a hydraulic pump to and from a plurality of hydraulic motors. More
particularly, the invention relates to a hydraulic fluid control valve for dividing, regulating
and equalizing the flow and pressure of the hydraulic fluid delivered to and from two or
more hydraulic motors when configured as a parallel drive circuit.
Fluid control valves are well known in the art and have found application in both fuel
control systems and compression release engine brakes of vehicles. In particular, such
valves are commonly used to control the flow of hydraulic fluid in the hydraulic drive
systems of vehicles. Taking as an example, a hydraulic parallel drive system for a vehicle
such as a three—wheel drive forklift, an inherent feature of this type of drive system is an
open differential whereby an unregulated but balanced amount of hydraulic fluid is
delivered to each wheel of the Vehicle. This arises because hydraulic fluid such as oil will
always flow through the path of least resistance. Having an open differential is an
advantage when a vehicle is travelling on feasible ground such as a paved surface. In such
conditions, the open differential allows driving around bends and turning when the tyres
are in Contact with the feasible driving surface. However, this advantage is lost when the
vehicle encounters terrain where traction is compromised.
With an open differential, if a wheel looses traction, all drive power is delivered to that
wheel resulting in the wheel spinning without gripping the surface to enable it to move the
vehicle in the direction of travel. In such conditions, full flow of hydraulic fluid is
supplied to the wheel that is spinning, resulting in a drop in system pressure. With no
remaining flow available for the other drive wheels that do have traction, the vehicle
eannot continue its motion in a forward or reverse direction. In order to regain vehicle
motion, power must be taken from the wheel that is spinning out and redistributed to the
wheels that are not. In hydraulic parallel drive systems this is achieved by regulating or
metering the fluid flow to the wheel that is spinning out while also maintaining sufficient
system flow and pressure to drive the remaining wheels that do have traction.
United States Patent Specification No. US 5,647,211 discloses a valve for controlling the
flow of hydraulic fluid from a hydraulic pump to and back from a pair of hydraulic motors.
The valve disclosed in US 5,647,211 is a complex flow divider which comprises two flow
dividers, namely one flow divider for each wheel motor. Also several spools and a
plurality of pressure selector valvesl solenoid control valves are used. The valve as
disclosed in US 5,647,211 also does not readily or easily lend itself to driving a three
wheeled vehicle having three wheel motors.
It is therefore an object of the present invention to provide an improved fluid control valve
for use in hydraulic parallel drive systems to divide, regulate and equalize the flow and
pressure of the hydraulic fluid to and from a plurality of hydraulic motors.
Thus, the present invention seeks to alleviate the disadvantages of known fluid control
valves by providing an improved control valve, with a simple and robust design, and
having less components than existing valves known in the art.
Accordingly, the present invention provides a fluid control valve for use in controlling the
flow of hydraulic fluid from a hydraulic transmission pump to and from a plurality of
hydraulic motors, the valve comprising a plurality of fluid lines for providing fluid to the
respective hydraulic motors, a spool chamber and a flow divider/combiner spool which is
longitudinally slideably moveable within the spool chamber between a first position and a
second position; wherein in the first position, the flow divider/combiner spool provides
unrestricted flow from the transmission pump to and from the plurality of motors, and in
the second position the flow divider/combiner spool provides metered flow from the
transmission pump to and from the plurality of motors.
Conveniently, the fluid control valve includes a single spool chamber and a single flow
divider/combiner spool.
Thus, the fluid control valve of the invention has the significant advantage that it allows for
a single flow divider/combiner spool which is capable of controlling the flow of hydraulic
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fluid from the pump to and from a plurality of wheel motors. This represents a significant
advance over the prior art.
Conveniently, the flow divider/combiner spool is held in the first position by a
compression spring.
The fluid control valve also includes operator—controllable selector means for controlling
the position of the spool in the spool chamber. Conveniently, this operator-controllable
selector means comprises a solenoid operated, 3-way selector valve, which when energized
causes the flow divider/combiner spool to move within the spool chamber under pressure
from an external charge pump to the second position in which the spring is compressed.
Alternatively, the operator—controllable selector means may be a switch operable by
pneumatic, mechanical, electrical or manual means.
Ideally, metered flow is provided by means of a plurality of fluid metering means located
in a non—continuous manner along the length of the flow divider/combiner spool.
Ideally, the plurality of fluid metering means comprise a series of grooves formed on the
outer surface of the flow divider/combiner spool.
Preferably, when the flow divider/combiner spool is in the second position the fluid
metering grooves are in fluid communication with the fluid lines connecting the
transmission pump and the plurality of motors, thereby allowing metered flow from the
transmission pump to and from the plurality of motors.
Advantageously, the grooves on the outer surface of the flow divider/combiner spool act as
lubrication grooves to aid movement of the spool to and from the first and the second
position within the spool chamber.
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Conveniently, the lubrication grooves on the outer surface of the spool also function as a
metering flow path when the spool is in the second position.
Preferably, the flow divider/combiner spool also includes a plurality of full-flow means
provided along the length of the spool. The full—flow means/ full—flow sections are ideally
provided in an arrangement with a full—flow section adjacent the metering means (metering
grooves). Thus, full-flow sections and metered flow grooves are provided in an alternate
arrangement along the length of the spool.
Conveniently, when the spool is in the first position, the full—flow sections are in fluid
communication with the fluid lines connecting the transmission pump and the plurality of
motors, thereby allowing full flow from the transmission pump to and from the plurality of
I1’l0tOI'S .
The invention will hereinafter be described more particularly with reference to the
accompanying drawings in which are shown, one example of a fluid control valve in
accordance with the present invention.
In the drawings:
Figure 1 is a schematic diagram of a parallel circuit hydraulic drive system for a three-
wheel drive vehicle which includes the fluid control valve of the present invention;
Figure 2 is a front sectioned View of the fluid control valve when the selector valve is de-
energized, showing the flow divider/combiner spool in a first position permitting full
unrestricted flow to and from a plurality of motors and a transmission pump;
Figure 3 is a front sectioned view of the fluid control valve when the selector valve is
energized, showing the flow divider/combiner spool in a second position, thereby allowing
metered flow to and from a plurality of motors and a transmission pump;
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Figure 4 is an exploded view showing the components of the fluid control valve of the
present invention including a detailed side view of one of the grooved segments provided
on the flow divider/combiner spool;
Figure 5 is a top section view of the manifold block of the fluid control valve along the
lines A—A of Figure 2;
Figure 6 is a side section view of the manifold block of the fluid control valve along the
lines B—B of Figure 2;
Figure 7 is a top section view of the manifold block of the fluid control valve along the
lines C-C of Figure 3; and
Figure 8 is a side section view of the manifold block of the fluid control valve along the
lines D—D of Figure 3.
Referring to the drawings and initially to Figure 1, there is shown and indicated generally
by reference letter A, a parallel circuit hydraulic drive system for a vehicle such as a three
wheel drive forklift which incorporates the fluid control valve of the present invention.
The hydraulic drive system A includes a prime mover 6, and a high-pressure transmission
pump 5 coupled to the prime mover 6 to provide the hydraulic drive for the hydraulic drive
system A. Also included in the hydraulic drive system A are a charge pump 4, fluid supply
and return lines 8 and 9, motors 7, a source of fluid 19 and a reservoir (or sump) 14.
The high-pressure transmission pump 5 is operable in forward or reverse bias thereby
providing high-pressure fluid supply to line 8 or 9 while the other line 9 or 8 acts as a low
pressure fluid return line.
The fluid control valve 1 comprises a manifold block la having fluid lines 8, 8a, 8b, 8c, 11,
12, 13, a spool chamber (not shown), a flow divider/combiner spool 2 and a control
compression spring 10. Additionally and conveniently, the fluid control valve comprises a
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solenoid operated, 3-way, selector valve 3. Fluid path 11 connects the flow
divider/combiner spool 2 to the reservoir 14, as well as linking selector valve 3 to the
reservoir. Fluid path 12 provides a pressure connection between the selector valve 3 and
the charge pump 4 whereas fluid path 13 connects the flow divider/combiner spool 2 to the
selector valve 3.
Referring now to Figures 1 and 2, the flow dividerl combiner spool 2 comprises a high
pressure shuttle type spool. The spool position in the spool chamber is determined by
whether or not the selector valve is energized. When the flow divider/combiner spool 2 is
in the first position, as shown in Figure 2, allowing unrestricted flow to and from a
transmission pump and the plurality of motors, the flow divider/combiner spool 2 is held in
the first position by the force of the compression spring 10. When it is desired to move the
flow divider/combiner spool 2 to the second position in which metered flow to and from
the motors is possible, the selector valve 3 is energized, resulting in a charge pressure from
a charge pump 4 overcoming the compression force of the spring 10 and acting to move
the spool 2 in the spool chamber 21 to a second position (as shown in Figure 3), in which
the spring 10 is shown fully compressed.
The manifold block 1a of the fluid control valve is mounted on a vehicle chassis or axle
through mounting holes 20. The flow divider/combiner spool 2 extends along the length of
the manifold block la and is capped at either end with a sealing member 17 and access
plug 16.
Fluid line 8 splits into fluid lines 8a, 8b and 8c which intersect the flow divider/combiner
spool 2. The fluid control valve 1 provides divided flow from transmission pump 5 to
motors 7 via fluid lines 8a, 8b and 8c or combined flow from motors 7 to transmission
pump 5 via fluid lines 8a, 8b or 8c.
Divided flow to the motors 7 is provided when the transmission pump 5 is operating in
forward bias and fluid line 8 is a high—pressure fluid supply line, with fluid line 9 acting as
a low—pressure fluid return line. Combined flow from the motors 7 is provided when the
transmission pump 5 is operating in reverse bias and fluid line 8 is a low—pressure fluid
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return line, with fluid line 9 acting as a high-pressure fluid supply line. Fluid line 9 splits
into fluid lines 921, 9b and 9c which feed the motors 7. Fluid flow through the flow
divider/combiner spool to or from the motors can either be unrestricted or metered
depending on whether or not the selector valve 3 is energized.
As shown in Figure 2, when the selector valve 3 is de—energized, a connection between
fluid path 11 and fluid path 13 is made while blocking the connection to fluid path 12.
This enables the compression spring 10 to control the position of the high—pressure flow
divider/combiner spool 2 since fluid path 13 has a direct connection to the reservoir 14. In
this mode, full unrestricted flow to or from the motors 7 is permitted.
Referring now to Figures 1 and 3, when the selector valve 3 is energized, a connection
between fluid path 12 and fluid path 13 is made while blocking the connection to fluid path
11. As a result, a charge pressure from the charge pump 4 overcomes the compression
spring 10 and the position of the high—pressure flow divider/combiner spool 2 shifts within
the spool chamber 21 to a second position which provides metered flow to or from the
motors 7.
Referring now to Figure 4, the high pressure flow divider/combiner spool 2 is shown in
more detail. The spool 2 includes a plurality of full flow sections 221 and a plurality of
discrete (non—continuous) metered flow sections (grooves) 2b. The full flow sections 2a
are aligned with the fluid lines 8a, 8b and 8c when the selector valve 3 is de—energized,
whereas the metered flow sections 2b are aligned with the fluid lines 8a, 8b and 8c when
the selector valve 3 is energized. The flow divider/combiner spool 2 has cylindrical
metering and lubrication grooves 15 on the outer surface of flow sections 2b which act as a
metering flow path when the selector valve 3 is energized. Construction hole plugs 18 on
the periphery of the manifold block la block access to fluid lines 11, 12 and 13.
Considering the operation of the flow divider/combiner spool 2 in more detail. Referring to
Figures 5 and 6, when the selector valve is de—energized, a fully extended compression
spring 10 holds the spool 2 in a first position such that full flow sections 2a are aligned
with fluid lines 8a, 8b and 8c permitting full unrestricted flow to or from the motors 7. In
particular, Figure 6 shows an unrestricted flow path from fluid line 8a, 8b or 8c around the
shuttle spool 2 to a motor 7.
Referring now to Figures 7 and 8, when the selector valve is energized, a charge pressure
from charge pump 4 results in shifting of the flow divider/combiner spool 2 within the
spool chamber 21, overcoming the force of the compression spring 10 such that the flow
divider combiner spool 2 assumes a second position in which metered flow sections 2b are
aligned with fluid lines 8a, 8b, and 8c. The cylindrical metering and lubrication grooves
on the outer surface of metered flow sections 2b are aligned with fluid lines 8a, 8b and
c permitting metered flow to or from the motors.
In particular, Figure 8 shows the metered flow path from fluid line 8a, 8b or 8c through the
spool chamber 21 to a motor 7 through the metering and lubrication grooves 15 on the
outer surface of flow sections 2b. A metering channel flow path 22, formed by and
between metering and lubrication grooves 15 and the spool chamber 21 provide a metered
flow path from fluid line 8a, 8b or 8c to a motor 7.
The fluid control valve 1 will now be described in use. In normal driving mode, that is, on
a good traction surface such as a paved surface, the compression spring 10 forces the high
pressure flow divider/combiner spool 2 to one side thereby enabling full free flow from the
transmission pump 5 to or from the wheel motors 7.
When driving on uneven ground, in conditions where wheel slip is likely, the selector
valve 3 is activated by the driver causing a charge pressure from the charge pump 4 to
overcome the compression spring force and move the divider/combiner spool 2 in the
opposite direction. This results in metered flow to or from the wheel motors 7. Metered
flow is only provided while the selector valve 3 is activated. By restricting the flow of
fluid to or from the wheel motors 7, the same flow and pressure is delivered to each wheel
allowing vehicle motion to be resumed.
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It will of course be understood that the invention is not limited to the specific details herein
described which are given by way of example only and that various modifications and
alternations are possible without departing from the scope of the invention.
MACLACHLAN & DONALDSON
Applicants’ Agents
Merrion Square
DUBLIN 2
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The following replacement page 9 was filed on 11/10/2005
P3559688
It will of course be understood that the invention is not limited to the specific details herein
described which are given by way of example only and that various modifications and
alternations are possible without departing from the scope of the invention as defined in the
appended claims.
Claims (5)
1. A fluid control valve for use in controlling flow of hydraulic fluid between a hydraulic transmission pump and a plurality of hydraulic motors, the valve comprising a plurality of fluid lines for providing fluid to the respective hydraulic motors, a spool chamber and a flow divider/combiner spool which is longitudinally slideably moveable within the spool chamber between a first position and a second position; wherein in the first position, the flow divider/combiner spool provides unrestricted flow between the transmission pump and the plurality of motors, and in the second position, the flow divider/combiner spool provides controlled flow between the transmission pump and the plurality of motors.
2. A fluid control Valve as claimed in Claim 1, wherein the fluid control valve includes a single spool chamber and a single flow divider/combiner spool, and further comprises operator—controllable selector means for initiating the controlling position of the flow divider/combiner spool in the spool chamber; optionally wherein the flow divider/combiner spool is held in the first position by a compression spring and wherein the operator—controllable selector means comprises a solenoid operated, 3-way selector valve; whereby the selector means need only be activated by the operator to overcome the force of the compression spring so as to move the spool from the first position to the second position.
3. A fluid control valve as claimed in Claim 1 or Claim 2, wherein a plurality of fluid flow control members located in a non-continuous manner along the length of the flow divider/combiner spool provides controlled flow; optionally wherein the plurality of fluid flow control members comprise a series of grooves formed on the outer surface of the flow divider/combiner spool, whereby with the flow divider/combiner spool in the second position, the fluid control members are in fluid communication with the fluid lines connecting the transmission pump and the plurality of IE M0688 ll motors, thereby allowing controlled flow from the transmission pump to and from the plurality of motors; optionally wherein the grooves on the outer surface of the flow divider/combiner spool act as lubrication grooves to aid movement of the spool to and from the first and the second position within the spool chamber.
4. A fluid control valve as claimed in any preceding claim, wherein the flow divider/combiner spool includes a plurality of full-flow means provided along the length of the flow divider/combiner spool; optioanlly wherein the filll-flOW means are sections provided in an arrangement with a full- flow section adjacent the flow control members; optionally wherein the full-flow sections and the flow control members are provided in an alternate arrangement along the length of the flow divider/combiner spool; and optionally wherein with the flow divider/combiner spool in the first position, the full-flow sections are in fluid communication with the fluid lines connecting the transmission pump and the plurality of motors, thereby allowing full flow from the transmission pump to and from the plurality of motors.
5. A fluid control valve, substantially in accordance with any of the embodiments herein described with reference to and/or shown in the accompanying drawings. MACLACHLAN & DONALDSON, Applicants’ Agents, 47 Merrion Square,
Publications (2)
Publication Number | Publication Date |
---|---|
IE20040688U1 true IE20040688U1 (en) | 2006-04-19 |
IES84323Y1 IES84323Y1 (en) | 2006-08-23 |
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