U.S. patent number 3,919,844 [Application Number 05/495,470] was granted by the patent office on 1975-11-18 for fluid couplings.
This patent grant is currently assigned to Fluidrive Engineering Company Limited. Invention is credited to John Elderton.
United States Patent |
3,919,844 |
Elderton |
November 18, 1975 |
Fluid couplings
Abstract
A scoop-trimmed fluid coupling is modified by increasing the
size of its baffle, drilling two sets of holes in the impeller wall
and altering the numbers of vanes on the impeller and the runner. A
substantially constant output torque is maintained when
accelerating a load simply by increasing the filling when the input
torque drops but otherwise holding the filling constant.
Inventors: |
Elderton; John (Hampton Hill,
EN) |
Assignee: |
Fluidrive Engineering Company
Limited (Isleworth, EN)
|
Family
ID: |
10399378 |
Appl.
No.: |
05/495,470 |
Filed: |
August 7, 1974 |
Foreign Application Priority Data
|
|
|
|
|
Aug 9, 1973 [UK] |
|
|
37840/73 |
|
Current U.S.
Class: |
60/330; 60/347;
60/351; 60/365 |
Current CPC
Class: |
F16D
33/20 (20130101); F16D 33/08 (20130101) |
Current International
Class: |
F16D
33/20 (20060101); F16D 33/00 (20060101); F16D
33/08 (20060101); F16D 033/00 () |
Field of
Search: |
;60/327,330,334,347,351,352,357,365 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Geoghegan; Edgar W.
Attorney, Agent or Firm: Woodhams, Blanchard and Flynn
Claims
I claim:
1. In a variable filling fluid coupling having vaned impeller and
runner elements together defining a toroidal working circuit for a
liquid, comprising the improvement wherein the coupling has a
baffle of diameter at least 1.25 times the inner profile diameter
of the working circuit, the runner of the coupling has between 10
and 35% more vanes than the impeller of the coupling, and the
impeller has two sets of holes through the wall thereof, the
centres of one set of holes being spaced from the coupling axis by
from 53 to 63% of the outer profile radius of the working circuit
and the centres of the second set of holes being spaced from the
coupling axis by from 65 to 75% of the outer profile radius of the
working circuit.
2. A coupling according to claim 1, wherein the spacing between the
two sets of holes is about 10%, measured in the radial direction of
the coupling, of the radius of the outer profile of the working
circuit.
3. A coupling according to claim 1 wherein the runner has between
15 and 25% more vanes than the impeller.
4. A coupling according to claim 1, wherein the two sets of holes
have pitch circle diameters respectively substantially 58% and 70%
of the outer profile diameter of the working circuit, and the
runner has approximately 20% more vanes than the impeller.
5. A coupling according to claim 1, wherein the baffle has a
diameter of substantially 1.3 times the inner profile diameter of
the working circuit.
6. A coupling according to claim 1, wherein the two sets of holes
have pitch circle diameters respectively substantially 58% and 70%
of the outer profile diameter, and the runner has between 15% and
25% more vanes than the impeller.
7. A coupling according to claim 6, wherein the baffle has a
diameter of substantially 1.3 times the inner profile diameter of
the working circuit.
8. A coupling according to claim 1, wherein the spacing between the
two sets of holes is about 10%, measured in the radial direction of
the coupling, of the radius of the outer profile of the working
circuit, and wherein the runner has between 15% and 25% more vanes
than the impeller.
9. In a variable filling fluid coupling having vaned impeller and
running elements together defining a toroidal working circuit for a
liquid, comprising the improvement wherein the coupling has a
baffle of diameter greater than the inner profile diameter of the
working circuit to minimize the maximum torque generated by the
coupling when driving a load, the runner of the coupling has
between 10 and 35% more vanes than the impeller of the coupling,
and the impeller has two sets of holes through the wall thereof,
the centres of one set of holes being spaced from the coupling axis
by from 53 to 63% of the outer profile radius of the working
circuit, and the centres of the second set of holes being spaced
from the coupling axis by from 65 to 75% of the outer profile
radius of the working circuit.
10. A coupling according to claim 9, wherein the runner has between
15% and 25% more vanes than the impeller.
11. A coupling according to claim 9, wherein the centres of said
one set of holes are spaced from the coupling axis by about 58% of
the outer profile radius of the working circuit, and wherein the
centres of said second set of holes are spaced from the coupling
axis by about 70% of the outer profile radius of the working
circuit.
12. A coupling according to claim 11, wherein the runner has about
20% more vanes than the impeller.
Description
This invention relates to fluid couplings of the kind comprising
vaned impeller and runner elements which together define a toroidal
working circuit for a liquid and in which the degree of filling of
the working circuit can be varied in use. An object of the
invention is to provide a variable-filling fluid coupling which
will transmit a substantially uniform torque whilst accelerating a
load, when under the control of a control arrangement for the
coupling such that the filling of the working circuit is increased
whenever the transmitted torque falls below a predetermined value
and the filling is held constant whenever the transmitted torque is
not below the predetermined value. One field in which such a
requirement arises is to be found in drives for long conveyor
belts. Such conveyor belts, which may be several miles in length,
are used for example for conveying minerals from a mine to a
railhead or harbour. Considerable economies can be made in the
capital cost of the conveyor belt by reducing the number of belt
plies so that the belt will for example withstand forces up to but
not greater than say 50% greater than the normal operating values.
To prevent damage to the belt, the belt drive must be prevented
from exerting forces greater than 150% of the normal full load
value. Another application where the same requirements apply would
be a large fan where the application of excessive driving torques
could cause damage to the fan. Furthermore, in the case of electric
motor drives, limitation of the maximum torque applied to the load
and thus of the maximum torque applied to the motor can prevent
undue disturbance of the electrical network and can also prevent
excessive voltage drop where the electric motor is situated in a
remote location requiring long power lines.
According to the present invention, there is provided a
variable-filling fluid coupling typically of the scoop trimming
type having a baffle of diameter at least 1.25 times the inner
profile diameter of the working circuit, the runner of the coupling
having between 10 and 35% more vanes than the impeller of the
coupling, and the impeller having two sets of holes drilled
therethrough, the centres of one set of holes being spaced from the
coupling axis by from 53 to 63% of the outer profile radius of the
working circuit and the centres of the second set of holes are
spaced from the coupling axis by from 65 to 75% of the outer
profile radius of the coupling. Preferably, the spacing between the
two sets of holes is about 10%, measured in the radial direction of
the coupling, of the radius of the outer profile of the working
circuit.
Preferably the runner has between 15 and 25% more blades than the
impeller. In one advantageous embodiment, the baffle has the
diameter of 1.3 times the inner profile diameter of the working
circuit, the two sets of holes have pitch circle diameters
respectively 58 and 70% of the outer profile diameter and the
runner has approximately 20% more blades than the impeller.
Embodiments of the invention will now be described by way of
example with reference to the accompanying drawings in which:
FIG. 1 is an axial sectional view of a scooptrimmed fluid coupling
in accordance with the invention,
FIG. 2 shows a view of the impeller as seen in the direction of the
arrows II--II in FIG. 1,
FIG. 3 is a graph showing the torque coefficient K plotted against
percentage slip as the coupling accelerates a load from rest to
operational speed, the filling of the coupling being increased
whenever the transmitted torque falls below a predetermined value
K,
FIG. 4 is a graph corresponding to FIG. 3 for a conventional
coupling, similar to that shown in FIGS. 1 and 2 but without any of
the characterising features of the invention,
FIG. 5 shows a similar graph to FIG. 4 for a coupling of
conventional construction with the exception of having an enlarged
baffle,
FIG. 6 shows a corresponding graph for a coupling having a baffle
and pattern of holes in the impeller wall in accordance with the
invention but having a substantially equal number of vanes on the
impeller and runner,
FIG. 7 shows diagrammatically an installation incorporating the
coupling and its control arrangement and
FIGS. 8 and 9 are views corresponding to FIGS. 1 and 2 of another
coupling in accordance with the invention.
The scoop-trimmed fluid coupling shown in FIGS. 1 and 2 is of
conventional construction in so far as it comprises coaxially
mounted input and output shafts 1 and 2 interconnected by a ball
bearing 3, a rotating casing 4 secured to the input shaft 1, a
vaned impeller 5 secured to the casing 4, a vaned runner 6 secured
to the output shaft 2 and defining with the impeller 5 a toroidal
working circuit W, and a trimming scoop 7 slidably mounted in a
stationary structure 8 and projecting into a scoop chamber 9
defined between the back of the impeller 5 and a scoop chamber
casing 10 secured to the outer periphery of the rotating casing 4
and to the impeller 5.
The coupling shown in FIGS. 1 and 2 departs however from
conventional practice in that its baffle 11 has a radius 1.3 times
the inner profile radius 12, as opposed to a more conventional
value of 1.1 times the inner profile radius, the impeller 5 has two
series of holes 13 and 14 drilled through it and the runner 6 has
about 20% more vanes than the impeller. In the particular coupling
shown in FIGS. 1 and 2, the working circuit W has an outer profile
radius 15 of 53/4 inches. A conventional coupling of this size
would have for example 42 vanes on the impeller and 40 vanes on the
runner. In the coupling shown in FIGS. 1 and 2, the impeller has 45
vanes but the runner has 54 vanes and may be of similar
construction to the impeller shown in FIG. 2 (the pattern in each
of the three sectors of the coupling being identical) with the
exception that the three widest pockets 21, 22, 23 formed between
the vanes are each divided into two pockets by the addition of a
vane in each of these pockets. Alternatively, the vanes in both
impeller and runner may be equi-spaced.
The two sets of holes, 13, 14 are drilled through the wall of the
impeller. The holes 13, 14 are typically 1/4 inch in diameter. With
the exception of one pocket, alternate pockets each have one hole,
either 13 or 14. The centres of the holes 13 lie on a circle
centred on the coupling axis and of diameter 65/8 inches. The
centres of the holes 14 also lie on a circle centred on the
coupling axis of diameter 81/8 inches. Thus, the holes 13 lie on a
circle whose radius is about 58% of the outer profile radius 15
while the holes 14 lie on a circle whose radius is about 70% of the
outer profile radius 15.
FIG. 3 shows the "K" value (proportional to the transmitted torque
for a constant motor speed) plotted against the percentage slip for
a variety of different loads when accelerating a load from rest
(100% slip) to full speed. The graphs were obtained with a control
system (similar to that shown in FIG. 7) which served merely to
move the scoop tube in the direction to increase the working
circuit filling in response to a reduction in the transmitted
torque as measured for example by measuring the current taken by a
squirrel-cage electric motor driving the coupling. Such a control
system has no provision for reducing the torque transmitted by the
coupling in the event that the transmitted torque exceeds the
predetermined value. Despite this, it will be noticed that the
transmitted torque does not rise more than about 10% above the
predetermined value. Furthermore, between the lines 31 and 32 the
transmitted torque is particularly constant. The portions of graphs
to the right of the line 31 correspond to the fixed initial
position of the scoop which is reached by the scoop on starting up
of the system, this position corresponding to the degree of filling
of the working circuit required to transmit the predetermined
torque at 100% slip.
In contrast, FIG. 4 shows the corresponding curves obtained with an
unmodified coupling. In the region to the right of the line 41, the
transmitted torque rises to a maximum about 50% greater than the
predetermined value. While this may not be detrimental for some
purposes, there are some applications such as the driving of long
conveyor belts having a minimum number of belt plies where the
increase in torque during acceleration could cause damage.
Even in the range between the lines 41 and 42, there are
appreciable variations in the transmitted torque, in some cases
amounting to more than 10% of the predetermined value.
The curves in FIG. 5 show the effect of increasing the diameter of
the baffle in an otherwise conventional coupling. While the
magnitude of the maximum transmitted torque is somewhat reduced, it
still represents a value some 30% above the predetermined value.
Furthermore, although the torque between the lines 51 and 52 is in
general more constant, it will be seen that there are a number of
disturbances such as are shown at 53, 54 and 55 which may be
unacceptable for some purposes.
FIG. 6 shows the effect of the combination of the larger baffle and
the two sets of holes in the impeller wall in an otherwise standard
coupling in which the impeller has 42 vanes and the runner has 40
vanes. By comparison with FIG. 5, it will be seen that the two sets
of holes render the transmitted torque much more uniform over
virtually the whole slip range up to the operating value but there
are still a number of irregularities as shown at 63, 64 and 65.
Nevertheless, it will be seen that the pattern of holes avoids any
significant increase in the torque in the high slip range to the
right of the line 61.
Comparison of FIG. 6 with FIG. 3 shows that the increase in the
number of vanes in the runner eliminates the irregularities such as
those shown at 63, 64 and 65.
FIG. 7 shows diagrammatically an application of the coupling shown
in FIGS. 1 and 2, the coupling being indicated at 103.
In the arrangement shown in FIG. 7, a three phase high voltage high
power squirrel cage motor 101 has its output shaft 102 connected to
the input of the scoop-trimmed fluid coupling 103, such as that
shown in FIGS. 1 and 2, the output of which is connected to the
load 104 to be driven. In general, the load 104, for example a long
conveyor belt, may be represented by a flywheel 105 representing
the inertia of the load and a friction brake 106 representing the
power dissipated by the load as the result of friction, air
resistance and like losses.
In known manner, the position of the scoop tube 7 determines the
degree of filling of the working circuit W of the coupling 103. The
scoop 7 is movable over its whole range of positions by a small
reversible motor 111 driving through a reduction gearbox 112.
The torque in the shaft 102 of the motor 101 is approximately
proportional to the current drawn by the motor 101. This current is
measured by a pickup coil 113 surrounding one of the leads of the
three-phase electrical supply 114 to the motor 101 and forming with
this lead a transformer. The ends of the coil 113 which thus forms
the secondary winding of this transformer, are connected to a
current sensing unit 115 which, when the current in the leads
exceeds a predetermined value energizes a relay 116 which in turn
de-energizes a motor controller 117 for the motor 111. The current
sensing unit 115 is arranged to de-energize the relay 116 when the
current in the leads 114 falls below tthe predetermined value,
thereby re-energizing the controller 117 to start up the motor 111
again.
In operation, with the system at rest, the scoop tube 7 of the
coupling 103 is in its "circuit empty" position. The motor 101 is
switched on and runs rapidly up to its normal speed since the
working circuit W of the coupling 103 is empty. The relatively low
voltage supply 121 for the motor 111 is then switched on and the
motor 111 is energized by the motor controller 117 to begin to draw
the scoop tube 7 out in the direction of the "circuit full"
position.
As a result, the working circuit W begins to fill and the torque
load imposed on the motor 101 rises. Correspondingly, the current
drawn from the high voltage supply through the leads 114 rises
until its value, as sensed by the coil 113 and the current sensing
unit 115 reaches a predetermined value, for example 140% or 150% of
the normal operational full speed loan value, whereupon the current
sensing unit 115 actuates the relay 116 to cause the motor
controller 117 to stop the motor 111. This in turn stops the scoop
tube 7.
The motor 101 then continues to drive the load 104 through the
partially filled working circuit W. The torque transmitted by the
working circuit W is sufficient to overcome the frictional forces
represented by the brake 106 and to continue to accelerate the load
104 against its inertia (represented by the flywheel 105).
If the characteristics of the coupling 103 are such that as the
speed rises, the torque transmitted by the coupling with this
particular degree of filling also rises, then the motor 111 will
remain de-energized and although the torque exerted by the motor
will increase somewhat, the filling of the working circuit W will
remain constant. When, as a result of increasing speed, the
characteristics of the coupling cause the transmitted torque to
fall below the predetermined value, the fall in the current in the
leads 114 will be sensed by the current sensing unit which will
cause the relay 116 to operate the motor control 117 to drive the
scoop tube 7 further towards the "circuit full" position until the
predetermined torque value is re-established. This "on-off
switching" of the motor 111 continues until the scoop tube 7
reaches its "circuit full" or normal operating position.
The motor 101 then continues to drive the load at normal speed.
When the motor 101 is switched off to close down the system, a
reversing switch (not shown) for the motor 111 causes the motor 111
to drive the scoop tube 7 into its "circuit empty" position ready
for the next time the motor 101 is started up.
The fluid coupling shown in FIGS. 8 and 9 differs from that shown
in FIGS. 1 and 2 principally in that it is designed to transmit
higher power at higher speeds than that shown in FIGS. 1 and 2. In
this embodiment, the outer profile radius 212 is 83/4 inches. The
axial width of the working circuit W is slightly greater than its
maximum radial dimension.
As in the case of the couplings shown in FIGS. 1 and 2, the
couplings shown in FIGS. 8 and 9 is modified from conventional
practice in a number of respects. Thus, the external diameter of
the baffle 211 is increased from its normal value of 1.1 times the
inner profile diameter of the working circuit to 1.25 or 1.3 times
the inner profile diameter. For some applications, the value of
1.25 is preferable as it gives a slightly higher maximum starting
torque.
Furthermore, the impeller 205 has 45 vanes instead of the
conventional 51 vanes and the runner 206 has 54 vanes instead of
the conventional 48 vanes. Two sets of holes 213 and 214 are
drilled in the impeller 205 with their centres respectively at
radial distances of 58% and 70% of the outer profile radius 212
from the axis of the coupling.
In addition, the impeller hub has inlet ports 220 which are
inclined at 45.degree. to the coupling axis instead of the more
usual radial disposition. Under some conditions, the inclined
disposition of the inlet ports is found to cause less delay in
establishing a stable vortex within the working circuit when
starting.
Care should be taken that there is no excessive loss of working
liquid through the bearing 203 interconnecting the inlet shaft 201
and the outlet shaft 202 under the varying operating conditions to
be encountered by the coupling. With this in mind, in the
arrangement shown in FIG. 8, a single inclined vent passage 221
permits some circulation of liquid through the bearing 203 but has
its inner end 222 positioned radially inwards of the balls of the
bearing 203. Further, the running clearance X between the hub of
the casing 204 and the shaft 202 is relatively small, being in this
case about 0.0025 inch.
The impeller has twenty-two holes 213 and twenty-three holes 214,
both sets of holes being 3/8 inch in diameter.
* * * * *