U.S. patent number 3,620,238 [Application Number 04/888,740] was granted by the patent office on 1971-11-16 for fluid-control system comprising a viscosity compensating device.
This patent grant is currently assigned to Toyoda Koki Kabushiki Kaisha. Invention is credited to Minoru Kawabata.
United States Patent |
3,620,238 |
|
November 16, 1971 |
FLUID-CONTROL SYSTEM COMPRISING A VISCOSITY COMPENSATING DEVICE
Abstract
Fluid-control system comprising fluid-control means having a
positive viscosity-resistance characteristic the flow resistance of
which increases with an increase in viscosity, and further
comprising vortex means having a negative viscosity-resistance
characteristic the flow resistance of which increases with a
decrease in viscosity to compensate for changes in the flow
resistance of the fluid-control means due to changes in fluid
viscosity. The vortex means is provided with a circular hollow
chamber, a tangential nozzle connected to a source of
incompressible and viscous pressure fluid, and a central output
port connected to the fluid control means.
Inventors: |
Minoru Kawabata (Asahi-machi,
JP) |
Assignee: |
Toyoda Koki Kabushiki Kaisha
(Asahi-machi, Kariya-shi)
|
Family
ID: |
11632394 |
Appl.
No.: |
04/888,740 |
Filed: |
December 29, 1969 |
Foreign Application Priority Data
|
|
|
|
|
Jan 28, 1969 [JP] |
|
|
44/6219 |
|
Current U.S.
Class: |
137/810;
137/812 |
Current CPC
Class: |
F15C
1/02 (20130101); F15C 1/16 (20130101); Y10T
137/2098 (20150401); Y10T 137/2109 (20150401) |
Current International
Class: |
F15C
1/02 (20060101); F15C 1/00 (20060101); F15C
1/16 (20060101); F15c 001/16 () |
Field of
Search: |
;137/81.5 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Samuel Scott
Attorney, Agent or Firm: Holcombe, Wetherill &
Brisebois
Claims
What is claimed is:
1. A fluid-control system comprising fluid control means having a
positive viscosity-resistance characteristic, and vortex means
having a negative viscosity-resistance characteristic connected in
series, said vortex means comprising a circular chamber, a single
tangential nozzle adapted to be connected to a source of
incompressible and viscous pressure fluid and a single central
output port connected to said fluid control means, whereby any
change in the viscosity of the fluid flowing in said system which
causes a change in the flow resistance of said fluid control means
produces a compensating change in the flow resistance of said
vortex means.
2. A fluid-control system as claimed in claim 1, wherein said fluid
control means comprises at least one pure fluid control
element.
3. A fluid-control system as claimed in claim 2, wherein said pure
fluid control element is a wall-attachment element comprising a
main nozzle connected to the output port of the vortex means to
deliver a main jet, control nozzles downstream of said main nozzle
on opposite sides of said main jet for deflecting the path of said
main jet and output ports positioned to receive the deflected
jet.
4. A fluid-control system as claimed in claim 2, wherein said pure
fluid control element is a jet deflection proportional element
comprising a main nozzle connected to said output port of the
vortex means to deliver a main jet, control nozzles downstream of
said main nozzle on opposite sides of said main jet for deflecting
the path of said main jet, and output ports positioned to receive
the deflected main jet.
Description
This invention relates to a fluid-control system, comprising a
viscosity compensating device adapted to compensate for changes in
the viscosity of a viscous fluid flowing through the control
system, so that the operative characteristics of the system may be
kept constant.
Generally, since the viscosity of a viscous fluid, and in
particular of an incompressible fluid such as oil, flowing in a
fluid-control system, is affected by changes in temperature, the
flow rate in the control system, and particularly in constricted
portions of fluid passages, is affected, and therefore pressure in
the system is changed. Thus, there is danger that the control
system may not operate correctly and reliably. In particular,
fluid-control systems comprising a plurality of pure fluid control
elements are greatly influenced by changes in the viscosity of the
viscous fluids used as operative fluids. A "pure fluid control
element," as used herein, comprises a chamber enclosed by
sidewalls, and a main nozzle from which the fluid, hereinafter
referred to as a "main jet," is introduced, at high speed, into the
chamber. Output ports in the chamber receive the main jet. Control
nozzles deflect the main jet, so that the output ports are supplied
with the main jet in different proportions. Pure fluid control
elements of this kind may be classified as belonging to one or the
other of two types, depending on the conditions controlling the
deflection. One type is an element deflecting the main jet
proportionally to the input to the control nozzle, and is called a
jet deflection proportional amplifier. The other type is a
wall-attachment amplifier wherein the deflected condition is
maintained stable by the wall-attachment or Coanada effect. In both
types the jet speed and flow rate of the main jet are affected by
changes in the viscosity, if constant fluid pressure is supplied to
the main nozzle. Thus, the pressure and flow rate in the output
port are changed. Consequently, in a jet deflection proportional
amplifier, the gain is changed. As a result there is danger not
only of incorrect operation in the fluid-control system but also of
lowering the reliability of the operation. In the wall-attachment
amplifier, substantially the same characteristic change as in the
jet-deflection proportional amplifier is produced, so that the main
jet is not always deflected by the same constant control input. In
order to avoid such conditions it is desirable that the temperature
of the operative fluid be maintained constant so that the viscosity
remains unchanged. However in this case an additional thermostat is
required at the pressure fluid supply source, which results in
volume and weight increases and complication in the control system.
Particularly for vehicles, small size and light weight in the
control system are strongly required. Therefore it is difficult to
keep the temperature of the operative fluid constant. Thus, a
simple viscosity compensating device is required, which has no
undesirable effects on the operative characteristics of the control
system, even when the viscosity of the operative fluid is changed
by changes in the temperature thereof.
The primary object of this invention is to provide a fluid-control
system comprising a simple and effective viscosity compensating
device.
Another object of the invention is to provide a fluid-control
system comprising fluid control means having a positive
viscosity-resistance characteristic and vortex means having a
negative viscosity-resistance characteristic which compensates for
changes in the viscosity of the fluid in the fluid control
means.
The foregoing and other objects of the present invention will
become fully apparent from the following description of a preferred
embodiment of said invention with reference to the accompanying
drawings, in which:
FIG. 1 is a plan view of the plate 1 of a viscosity compensating
device connected to a wall-attachment element according to the
present invention as seen from the left of FIG. 2, with the plate 2
removed;
FIG. 2 is a side elevation of the device shown in FIG. 1; and
FIG. 3 is a cross-sectional view showing a vortex-type element used
to describe its theoretical operation.
DESCRIPTION OF THE INVENTION
Generally, a pure fluid control element such as a wall-attachment
element utilizing two dimensional flow is not actuated until the
Reynolds number in its main nozzle becomes larger than a specified
value.
Now the Reynolds number in substantially two dimensional flow is as
follows.
Re =2V. Ws. t/.nu.(Ws +t) (1) where
Re=Reynolds number
Ws=Width of main nozzle
t=height of main nozzle
v=average flow speed in main nozzle
.nu.=coefficient of kinetic viscosity.
As is apparent from the above equation (1), Re becomes a function
of v, that is, Re becomes larger with an increase in v, when the
main nozzle of the identical size and the identical operative fluid
are used. It is, however, uneconomical to increase Re more than
required to increase the quantity of fluid used in fluid control
system. Thus, it is desirable to set Re within a preferable range,
but as previously mentioned, the viscosity of the fluid changes
considerably with changes in temperature, and thus Re is influenced
by .nu.. Re changes with a change in .nu., even if v is constant.
Thus, in order to keep Re constant, it is preferable to change v in
direct proportion to the change in .nu..
Flow rate in two dimensional flow is as follows:
Q=Ws. t.sup.3 .DELTA.p/12..mu.. l (2) where
i Q=flow rate
Ws=width of main nozzle
t=height of main nozzle
.DELTA.p=pressure difference across the nozzle
.mu. =coefficient of viscosity
l =length of the nozzle. Thus, flow rate Q changes with a change in
pressure difference .DELTA.p. In a pure fluid control element, the
pressure downstream of the main nozzle is approximately constant,
and thus the change in flow rate Q is substantially equal to the
change in pressure upstream of the main nozzle. Therefore, in order
to keep the Reynolds number Re constant, the pressure upstream of
the main nozzle may be changed in direct proportion to the change
in viscosity.
If the fluid flow in the main nozzle is a steady flow, the flow
resistance is as follows.
R=.DELTA.p/Q where
R=flow resistance
.DELTA.p=pressure difference across the main nozzle
Q=flow rate from equation (2) Thus, the flow resistance R increases
with an increase in the coefficient of viscosity .mu., and vice
versa. This positive viscosity-resistance characteristic is
hereinafter referred to as a positive characteristic.
As shown in FIG. 3, a vortex amplifier comprises a cylindrical
vortex chamber, a tangential supply port, and a central output
port. When fluid is introduced from the supply port into the vortex
chamber, fluid issues from the output port following a vortex path
in the vortex chamber. The pressure drop in the vortex chamber is
given as a function of the radial distance from the center of the
vortex chamber.
Generally, vortex flow may be characterized by the tangential
velocity-radial distance relationship
v.phi.r.sup.n=constant= K.sub.2
or v.phi.=K.sub.2 r.sup.-.sup.n (5) where n is a parameter
determined by the viscosity of the fluid and practically
-1<n<+1 from equations (4) (5) For an incompressible fluid,
.rho. is constant and equation (6) integrates to the general form
where C.sub.1 is a constant of integration. If the pressure at r=0
is P.sub.1, C.sub.1 =P.sub.1 equation (8) gives the pressure drop
in the vortex chamber. Further
P-P.sub.1= QR (9) where
Q=flow rate in the vortex chamber
R=flow resistance in the vortex chamber. Substituting equation (8)
into equation (9) gives When n=-1, that is, viscosity is zero, flow
resistance R.sub.1 is as follows. When n=+1, that is, viscosity is
infinite, flow resistance R.sub.2 is as follows. As is apparent
from the above equations (11) (12), R.sub.1 >R.sub.2. Thus, the
flow resistance increases with a decrease in viscosity, and vice
versa.
This negative viscosity-resistance characteristic is hereinafter
referred to as a negative characteristic.
Thus, the connection of the vortex-type element to the pure fluid
control element causes the vortex element to automatically regulate
the supply pressure or flow rate to the pure fluid element to keep
the Reynolds number in the main nozzle of the pure fluid element
constant, even if the viscosity of the fluid in the pure fluid
element is changed.
Referring now to FIGS. 1 and 2, a wall-attachment element 20 is
illustrated as a representative pure fluid control element. A
vortex type element 10 is connected to the wall-attachment element
20 upstream thereof. The vortex-type element compensates for
changes in the viscosity of fluid in the wall-attachment element. A
flat plate 1 is recessed to form both the wall-attachment element
and the vortex-type element, and is tightly sealed to a flat plate
2.
The vortex type element 10 comprises a circular chamber 12, a
tangential nozzle 14 and a central output port 15. The nozzle 14 is
connected to a pressure fluid supply source (not shown) through a
supply port 11.
The wall-attachment element 20 is provided with a main nozzle 23, a
pair of control nozzles 24 and 25, a chamber 22 and a pair of ducts
28 and 29. The main nozzle 23 extends at one end into the chamber
22 and communicates at the other end with a supply port 21
connected to the output port 15 of the vortex-type element 10. The
control nozzles 24 and 25 extend from opposite sides into the
chamber 22 at substantially right angles to the main nozzle 23, and
are respectively connected to control ports 33 and 34. The chamber
22 is divided into the two ducts 28 and 29 by a divider 30. A pair
of vent passages 31 and 32 open respectively into the ducts 28 and
29 downstream of the chamber 22. The ducts 28 and 29 are
respectively connected to output ports 26 and 27.
Operative fluid having a certain viscosity, for example, an
incompressible fluid such as oil, and supplied through the supply
port 11, enters along the wall 13 into the chamber 12 through the
nozzle 14, following a vortex path. This vortex flow decreases the
pressure in the center of the chamber 12 and this pressure
decreases as the radial distance from the center decreases. The
higher the flow speed in the nozzle is, the stronger the vortex
flow becomes, and the pressure in the central output port 15
therefore becomes lower and the flow resistance in the chamber 12
is increased. When the viscosity of the fluid is decreased, the
viscous resistance of the fluid is decreased, so that the vortex
flow in the chamber 12 increases to increase the flow resistance.
Inversely, the viscous resistance of the fluid increases with an
increase in the viscosity thereof, so that the vortex flow in the
chamber is decreased to reduce the flow resistance. Thus, the
connection of a vortex-type element to a pure fluid control element
such as the wall-attachment element permits the vortex-type element
to compensate for changes in the viscosity of the fluid in the
wall-attachment element.
The fluid from the output port 15 of the vortex type element 10
issues into the chamber 22 through the supply port 21 and the main
nozzle 23. This main jet adheres to one of walls 35 and 36 in the
chamber 22. This phenomenon is called the wall-attachment effect or
Coanda effect, by which deflected condition is maintained stable.
Assuming that the main jet issues initially from the left output
port 26, if a control flow is introduced into the control nozzle
24, the main jet is deflected to the right and then adheres to the
wall 36 in the chamber 22. Thus the main jet continues to leave
from the right output port 27 until a control flow is introduced
into the control nozzle 25. Under one stable condition, the greater
part of the main jet is supplied to the next device to be operated
through the left output port 26, while under the other stable
condition, the greater part of the main jet is supplied to the next
device through the right output port 27. The next device is
operated in response to the difference in momentum between the
control flows supplied to the control nozzles 24 and 25.
Vent passages are required to maintain the deflected condition
stable even when the loads exerted on the output ports 26 and 27
are increased.
The main jet, when in a stable condition, is responsive to jet
speed in the main nozzle, the shape and size of the main nozzle,
and the viscosity of the main jet and is usually designed to that
the Reynolds number in the main nozzle is more than
4.times.10.sup.3 . The Reynolds number Re is given by equation (1)
and changes with any change in the viscous resistance in the
hydraulic circuit without compensation for such change. Thus, the
entrainment characteristic of the main jet is changed, which causes
a change in the time required for switching between deflected
conditions. Consequently, the flow rates and pressures in the
output ports 26 and 27 are changed. However, as previously
described in detail, the vortex element 10 connected to the main
nozzle 14 serves to compensate for such conditions, in response to
changes in fluid viscosity, and thus automatically regulates the
pressure and flow rate of fluid supplied to the main nozzle.
Thus the vortex element serves to maintain the Reynolds number in
the main nozzle constant. Consequently, the operative
characteristic of the hydraulic circuit is kept stable, and is
unaffected by changes in fluid viscosity, which results in
increased accuracy and reliability in the control of the hydraulic
circuit.
While the vortex element is connected to a wall-attachment element
in the above embodiment, the vortex element may be applied to a jet
deflection proportional element or like element, and almost the
same effect may be obtained. Further while the vortex element is
applied to one pure fluid control element in the above embodiment,
the vortex element may be applied to a plurality of pure fluid
control elements. In this case, the vortex chamber and tangential
nozzle of the vortex element are designed to compensate for the
viscosity changes of all the pure fluid elements.
It is desirable to provide suitable means such as an enlarged
passage portion or foraminous screen in the connecting passage
between the output port of the vortex element and the supply port
of the pure fluid element for dissipating the vortex flow in the
connecting passage.
While the invention has been described in terms of one specific
embodiment, it should be understood that the novel characteristics
of the invention may be incorporated into other structural forms
without thereby departing from the spirit and scope of the
invention, as defined in the following claims.
* * * * *