U.S. patent number 3,698,415 [Application Number 05/059,081] was granted by the patent office on 1972-10-17 for pressure-regulating valve.
This patent grant is currently assigned to Linde Aktiengesellschaft. Invention is credited to Franz Forster, Gunter Hantelmann, Alfred Krusche.
United States Patent |
3,698,415 |
Forster , et al. |
October 17, 1972 |
PRESSURE-REGULATING VALVE
Abstract
A pressure-regulating valve has a control member shiftable in a
cylindrical bore of the valve housing by a lever or like actuator.
The control member bears upon the valve body via a plurality of
springs, at least one of which comes into play only after the
control member has been displaced through a predetermined
extent.
Inventors: |
Forster; Franz (Haibach,
DT), Krusche; Alfred (Grossostheim, DT),
Hantelmann; Gunter (Neuenrade, DT) |
Assignee: |
Linde Aktiengesellschaft
(Wiesbaden, DT)
|
Family
ID: |
5741695 |
Appl.
No.: |
05/059,081 |
Filed: |
July 29, 1970 |
Foreign Application Priority Data
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Aug 1, 1969 [DT] |
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P 19 39 293.9 |
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Current U.S.
Class: |
137/102; 91/434;
137/529 |
Current CPC
Class: |
F15B
13/0422 (20130101); G05D 16/101 (20190101); Y10T
137/2544 (20150401); Y10T 137/7905 (20150401) |
Current International
Class: |
F15B
13/042 (20060101); F15B 13/00 (20060101); G05D
16/04 (20060101); G05D 16/10 (20060101); G05d
007/00 () |
Field of
Search: |
;137/102,529
;91/433,434 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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536,796 |
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May 1941 |
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GB |
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1,112,101 |
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May 1968 |
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GB |
|
Primary Examiner: Nelson; M. Cary
Assistant Examiner: Zobkiw; David J.
Claims
We claim:
1. A hydraulic system comprising a pump, a reservoir, and a
pressure regulator connecting said pump and said reservoir to a
load, said pressure regulator comprising:
a housing provided with a bore;
a manually controlled input member slidable in said bore and
actuatable from a starting position to control the pressure at said
load;
a valve member slidable in said bore and defining a controllable
passage therein;
means connecting said passage in a hydraulic network with said
pump, said reservoir and said load;
first spring means interposed between said members and having a
force/displacement characteristic increasing with displacement at a
rate greater for a larger displacement of said input member than
for a smaller displacement of said input member from the starting
position of the latter, said first spring means comprising at least
two parallel springs rendered successively effective between said
members upon displacement of said input member, said parallel
springs including inner and outer coaxial springs, the outer spring
being prestressed and bridging said members in all positions
thereof, the inner spring being shorter than said outer spring and
forming a lost-motion coupling with at least one of said members;
and
second spring means in said bore biasing said valve member toward
said input member, said valve member being constructed and arranged
for biasing against said first spring means by the fluid pressure
at said load, said input member including:
a spring seat slidably mounted in said bore, said outer spring
bearing upon the said seat,
a shoulder carried by said input member and axially entrained with
said seat in the direction of said valve member for engagement with
said inner spring, and
a pin connected to said spring seat and to said shoulder and
extending outwardly of said housing;
a control plate swivelably mounted on said housing and engageable
with said pin while being provided with a control lever; and
a spring received in said bore and bearing at an end upon said
housing and at the other end against said spring seat, said means
for connecting said passage in said hydraulic network including a
first fitting connecting said bore on the side of the valve member
opposite said input member with said load, said passage including a
channel in said valve member opening into said
side of said bore and a circumferential groove formed in the
periphery of said valve member and communicating with said
channel,
an inlet port communicating with said bore and formed in said
housing while being connected to said pump, and
an outlet port formed in said housing and opening into said bore
while being connected with said reservoir, said groove selectively
communicating with said ports upon axial displacement thereof.
2. The hydraulic system defined in claim 1 wherein the hydraulic
network is a vehicle transmission.
3. The hydraulic system defined in claim 1 wherein the hydraulic
network is the hydraulic circuit of a machine having hydraulic
load-operating means.
4. A hydraulic system comprising a pump, a reservoir, and a
pressure regulator connecting said pump and said reservoir to a
load, said pressure regulator comprising:
a housing provided with a bore;
a manually controlled input member slidable in said bore and
actuatable from a starting position to control the pressure at said
load;
a valve member slidable in said bore and defining a controllable
passage therein;
means connecting said passage in a hydraulic network with said
pump, said reservoir and said load;
first spring means interposed between said members and having a
force/displacement characteristic increasing with displacement at a
rate greater for a larger displacement of said input member than
for a smaller displacement of said input member from the starting
position of the latter,
second spring means in said bore biasing said valve member toward
said input member, said valve member being constructed and arranged
for biasing against said first spring means by the fluid pressure
at said load, said means for connecting said passage in said
hydraulic network includes a first fitting connecting said bore on
the side of the valve member opposite said input member with a
hydraulic load, said passage including a channel in said valve
member and opening into said side of said bore and a
circumferential groove formed in the periphery of said valve member
and communicating with said channel, an inlet port communicating
with said bore and formed in said housing while being connected to
a source of hydraulic pressure, and an outlet port formed in said
housing and opening into said bore while being connected with a
fluid reservoir, said groove selectively communicating with said
ports upon axial displacement thereof.
Description
FIELD OF THE INVENTION
Our present invention relates to a pressure-regulating valve and,
more particularly, to a pressure regulator for a hydraulic or other
fluid-responsive network.
BACKGROUND OF THE INVENTION
Pressure-regulating valves have been proposed heretofore for the
manual or automatic regulation of the pressure in a line of
hydraulic or other fluid-responsive network, the valve comprising
essentially a valve member which is displaceable against the force
of a restoring spring, the effect of which is regulated by a
control member which is effective to establish the prestress of the
spring. Pressure control valves of this type have generally
provided springs with a linear characteristic, i.e. the
relationship between the force applied by the spring to the valve
member and the displacement of the valve member was generally
linear. As a result, the control pressure increases linearly with
the degree of displacement of the control member. When the control
pressure is effective upon a piston, the degree of displacement of
the piston is linearly proportional to the degree to which the
control member has been displaced. This linear relationship between
the input or control signal and the output pressure is desirable in
many cases.
However, when the control device is to be employed to operate a
stepless transmission, i.e. to displace the movable member of a
stepless hydrostatic transmission, the aforedescribed linearity of
the relationship between the control input and the result of this
input, is often undesirable. In these cases, it is preferred that,
in the region of small displacements from the null or neutral
(idler) position of the control member, the transmission provide
highly sensitive or fine control whereas displacements which
deviate greatly from the idling condition respond with reduced
sensitivity. For example, when the transmission is that of an
automotive vehicle, it is desirable that control of the
transmission be most sensitive with low vehicle speeds while the
sensitivity is decreased for high vehicle speeds. With hydraulic
controls for other purposes, a similar relationship is often
desirable.
OBJECTS OF THE INVENTION
It is therefore the principal object of the present invention to
provide a manual or automatic pressure control for a
fluid-responsive system especially a hydraulic system, which
affords greater control or sensitivity at selective areas in the
response characteristic than at other regions.
Another object of our invention is to provide a control valve
arrangement or a hydrostatic transmission or like hydraulic control
system which provides greater sensitivity in the operational modes
of the system at which increased sensitivity is desired, and is
consequently more efficient, accurate and sensitive than earlier
systems.
It is yet another object of our invention to provide a highly
versatile control valve for hydraulic systems of various types.
It is also an object of the invention to provide a control valve
whose rate of response is more sensitive at small deviations from a
null or normal position, but which increases as the deviation from
this null or normal position increases.
SUMMARY OF THE INVENTION
These objects and others which will become apparent hereinafter,
are attained, in accordance with the present invention, in a valve
system having a control or input member which, in the terms used in
servomechanism practice, represents the input signal and is
displaceable in a cylinder bore provided with a valve constituting
the output member, the displacement of the valve representing an
output signal which is controlled by the input signal.
In accordance with the principles of the present invention, a
spring means is provided between the control or input member, and
the valve body or output member, the spring means having at least
one spring element which fails to act in force-transmitting
relationship until one of the members has been displaced
sufficiently toward the other member to bring that spring into
play. It will be immediately apparent, therefore, that the system
is more highly sensitive to displacements of the control member (or
the valve member) within small deviations from a normal position,
but that, as the deviation increases and the other spring is
brought into play, the sensitivity is somewhat decreased.
For a predetermined degree of displacement of the input or control
member in the region of the starting position, therefore, the
sensitivity or control effect is greater than for the same degree
of displacement of the control member at a greater deviation from
the normal or starting position. With small displacements of the
control member, once a small deviation from the starting position
is established, therefore, a highly sensitive control of the
pressure is obtainable, indeed the sensitivity may far exceed that
which is available with greater offset from the starting
position.
The principles of the present invention are achieved by providing a
spring means between the input member and the valve body whose
force/displacement characteristic increases at a faster rate, i.e.
with greater slope, than the linear characteristic of a simple
spring. The restoring force of the spring means according to the
present invention thus rises more rapidly with compression than the
restoring force of a linear spring. Hence, the characteristic of
the spring means of the present invention can be described as
progressive or as approximating the exponential.
It has been found, according to the invention that a substantially
discontinuous increase in the restoring force should be provided,
according to the present invention, with displacement of the input
member and, to this end, we subdivide the spring means into at
least two spring elements, one of which couples the input member to
the valve body over the entire stroke of the input member, while
the second spring element forms a lost-motion connection with the
input member and is brought into play only after a predetermined
degree of displacement of this member. For small displacements of
the input member, therefore, only the first spring element is
effective to couple the valve body with the input member whereas
larger displacements of the input member bring into action the
second spring element. With the second spring element in effect,
the force supplied to the valve body increases more sharply than
with the first spring element so that the force/displacement
characteristic breaks sharply upward and the overall characteristic
has an exponential appearance.
The spring means, therefore, in its most general sense, may
comprise a plurality of springs effective in series and with
different stiffnesses. In this system, the softest spring will be
compressed predominantly prior to the development of sufficient
force to compress the stiffer springs, thereby producing the
increasing characteristic without a sharp demarcation between two
distinct slopes. More generally, however, the springs will be
provided in parallel, i.e. each spring will couple the input member
with the valve body independently of the other spring. These
springs may, therefore, have different lengths, corresponding to
the displacement threshold of the particular characteristic and any
spring without lost-motion relationship with the input member may
be prestressed to the desired stiffness level. The short springs,
therefore, need not be prestressed and only need be brought into
play after an initial displacement of the input member.
DESCRIPTION OF THE DRAWING
The above and other objects, features and advantages of the present
invention will become more readily apparent from the following
description, reference being made to the accompanying drawing in
which:
FIG. 1 is an axial cross-sectional view of a valve system embodying
the present invention;
FIG. 1a is a section along the line IA--IA of FIG. 1;
FIG. 2 is a fragmentary cross section of a portion of this
valve;
FIGS. 3 and 3A are diagrammatic illustrations of other spring
arrangements in accordance with the invention; and
FIG. 4 is a graph illustrating the spring relationships of the
present invention.
SPECIFIC DESCRIPTION
In FIGS. 1 and 2, we show a valve arrangement according to the
present invention which comprises a housing 1 in the form of a
cylinder mounted upon a panel or control board 1a and provided with
an axially extending bore 2 in which an input member 3 is axially
shiftable.
The upper end of the bore 2 is closed by a guide bushing 5 whose
O-rings 5a sealingly engage the wall of bore 2 and which is held in
place by a backing sleeve 5b. A lip type gland or seal 5c is
received in a groove 5d of bushing 5 to hug a pin 4 whose lower end
4a bears upon the input member 3. The upper end 4b of the pin 4
projects beyond the bushing 5 and abuts, via a ball bearing 4c, a
control plate 31 to which a handle 28 is affixed. The surface 31a
of control plate 31, against which the pin 4 bears, extends
transversely to the axis of the cylinder housing 1 and parallel to
the pivot axis 27a defined by a swivel joint generally represented
at 27. The swivel joint comprises a generally spheroidal shoe 27b
which surrounds a ball 27c, the latter being attached to member 1a
via a pedestal 27d. The socket 27b is, in turn, attached to the
plate 31 by a connecting bar 27e.
As is described in greater detail hereinafter, therefore, the plate
31 is pivotable about the axis 27a to actuate pin 4b and about the
axis 27f perpendicular to the plane of the pin 4b and the pivot
axis 27a which enables the valve to operate a pair of further pins
represented at 29 in FIGS. 1 and IA.
The member 3 comprises a spring seat or plate 3a defining a
shoulder against which abuts an outer helical compression spring 14
which may be held under prestress and serves to restore members 3
and 4 to the rest position illustrated in FIG. 1. The spring 14,
therefore, acting to swing the handle or lever 28 about the pivot
axis 27a in the clockwise sense. At its lower end, the spring 14
bears against a shoulder 17 formed in the housing 1 and fixed with
respect to the latter.
The spring seat 3 is provided with a boss 6 which is coaxial
therewith and serves as a centering member for the springs 14 and
15, the latter being coaxially received within spring 14 and
bearing axially upon the shoulder 3a. At its lower end, the spring
15 is seated against a shoulder 18 formed on a valve body 9 which
is axially shiftable within the bore 2. The spring 15,
consequently, is continuously in contact with both the input member
3 and the valve body 9 so that it serves as a continuously
effective force-transmitting and coupling member. In FIG. 4, the
characteristic of the spring 15 is represented at K.sub.1 and has a
slope which is relatively shallow.
From the boss 6 a stud 8 projects axially downwardly and defines an
angular shoulder 7 with this boss. The shoulder 7, moreover,
defines a spring seat for a coil spring 16, coaxially surrounded by
the spring 15 and guided on the stud 8 and a similar stud 20 formed
on the boss 19 of valve member 9. The boss 19 defines the
aforementioned shoulder 18 with the valve member 9 and, moreover,
has a shoulder 20a at the base of the stud 20 against which the
spring 16 may be compressed.
With the input member 3 in its illustrated position, the shoulder 7
is spaced from the upper end of the spring 16 upon a lost-motion
play .DELTA.x, corresponding to the stroke of the input member 3
prior to its engagement with the spring 16. The spring 16 lies in
parallel with spring 15 as a coupling between the input member and
the valve body 9, the collective characteristic of the two parallel
springs being represented at K.sub.2 in FIG. 4. It will be
appreciated that the force/displacement characteristic as seen at
the springs, increases sharply at the point .DELTA.x corresponding
to engagement of the input member 3 with spring 16.
The bore 2 is provided at its lower end with an axially extending
spool valve bore 10 closed at its bottom end by a fitting 21. The
latter is formed with a prismatic head 21a enabling a washer 21b to
be clamped against the lower wall 21c of the housing 1 while
threaded socket 10a at the lower end of bore 10. The fitting 21 is
connected to a fluid network, a pump 30a is connected to the
reservoir 30b and is provided with an accumulator 30c to maintain
constant pressure and reduce surges. The hydraulic system 30a and
30c is connected to the inlet fitting 23 by the usual passage and
has been illustrated and described only in the most diagrammatic
sense.
Between the fitting 21 and the valve body 9, we provide a spring 22
which serves to restore the original position of the valve member 9
against displacement by the control member 3. The spring 22 is
seated within a cylindrical recess 13 of the body 9, this recess
opening downwardly and having a passage 13a communicating with a
transverse bore 11 of the valve member. The bore 11 opens, into an
annular groove 12 along the periphery of the valve body 9 which
selectively connects with radial port 25 or with radial port 24.
The radial port 24 communicates in turn with a port 23 extending
perpendicular to the plane of the paper and connected to the
hydraulic pump 30a as represented diagrammatically in FIG. 1. The
connection 26 forms a hydraulic return path including bore 25 to
the reservoir 30b. The fitting 21 is, in turn, connected with the
load 30d, i.e. a hydraulic vehicle transmission.
The housing 1 can be provided with two or more control valves whose
pins are represented diagrammatically at 29 and one of which is
illustrated on the right-hand side of FIG. 1. These systems include
valve members 29a connected by single springs 29b with the input
element 29c. These control valves are used for the regulation of
equipment or the like which does not necessitate fine control as
noted earlier. As shown in FIG. 1a, displacement of the lever 28
about the axis 27f will actuate the lower valve whereas
displacement with the lever 28 in the opposite direction will
actuate the upper valve. A counterclockwise displacement of lever
28 actuates pin 4 while the clockwise displacement of the lever
actuates both of the pins 29. It has already been noted that the
valve system of the invention is preferably employed for hydraulic
transmissions in which a swash plate or tiltable control head of a
hydrostatic axial-piston pump is hydraulically displaced. The
springs 29b, of course, may have linear characteristics. The valve
may also be used in the hydraulic controls of a forklift truck,
front-end loader, excavator or like vehicle wherein the hydraulic
system operates arms, lifters or other loads.
Below, we have described the operation of the valve on the
left-hand side of FIG. 1, i.e. the valve structure in accordance
with the present invention having a nonlinear operating
characteristic. It will be apparent that the conventional valves in
the right-hand side of the housing operate in accordance with
conventional principles which need no elucidation.
Upon a counterclockwise displacement of the lever 28 about the axis
27a and the plate 31 rigid with this lever, the pin 4 and the
spring seat 3a are shifted downardly (FIG. 1) see FIG. 2. Spring 15
is thereby compressed to increase the downward or resisting force
applied to the valve body 9. The latter is thereby shifted
downwardly against the force of spring 22 to connect the annular
groove 12 with bore 24 and the pressure inlet 23, whereupon
hydraulic fluid flows under pressure through the port 23, the bore
24, the annular groove 12, the radial port 11, the axial passage
13a, the interior chamber 13 of valve member 9 and the fitting 21
to the load 30d. A pressure is built up in the hydraulic network
represented by load 30d and is effective to displace the valve body
9 upwardly against the force of spring 15 until this pressure, when
taken over the effective cross section of the valve body 9, in
conjunction with spring 22, suffices to balance and then exceed the
spring force 15. The valve body 9 thus reaches equilibrium. When
the lever 28 is then shifted to the left (counterclockwise) a
limited degree further, the spring seat 3 is shifted downwardly
again and the spring 15 is further compressed. The restoration of
the equilibrium follows as previously described.
However, in an extreme position of the lever 28 (FIG. 2) the
shoulder 7 engages the spring 16 which adds its force to that of
spring 15 and bearing upon the valve body 9. The pressure buildup
required to shift the member 9 back into its equilibrium position
thereby increases sharply in accordance with the characteristic
illustrated at K.sub.1, K.sub.2 in FIG. 4. At this threashold point
therefore, each millimeter of displacement of the lever 28 and the
pin 4 corresponds to a greater pressure increment in the hydraulic
network 30d to which the system is connected.
When the pressure in the bore 30 increases sufficiently to overcome
the force of the spring 15 or of the springs 15 and 16 together,
the valve body 9 is shifted upwardly until the bore 11 and the
annular groove 12 communicate with the bore 25 to bleed pressure
from the load to the reservoir 30b, thereby maintaining the
pressure associated with the position of lever 28. The out-flow
from the load 30d is, of course, throttled by the lever edge of the
groove 12.
In FIG. 3, we have shown a modified spring arrangement between the
input member 103 and the valve member 109. In this system, the
springs are provided, not in parallel, but in cascade; the springs
include a spring 116a of relatively low stiffness (i.e. a
relatively soft spring), a spring 116b of moderate stiffness and a
spring 116c of high stiffness. As a consequence, the entire spring
assembly will compress upon the displacement of member 103 with
force/displacement characteristic and shown at 100 in FIG. 4. It
will be evident that the system of FIG. 3 may be simply interposed
between the input member and valve member of the valve illustrated
in FIG. 1. The single spring 216 has a similar characteristic but
is of progressively varying cross section and stiffness and is
composed of synthetic resin. The spring is received between members
203 and 209 as previously described. The spring may be designed so
that a portion thereof (216a) will have its turns compress into
contacting relation prior to other portions.
* * * * *