U.S. patent number 3,658,452 [Application Number 05/024,215] was granted by the patent office on 1972-04-25 for gear pump or motor.
This patent grant is currently assigned to Shimadzu Seisakusho, Ltd.. Invention is credited to Yasuo Kita.
United States Patent |
3,658,452 |
Kita |
April 25, 1972 |
GEAR PUMP OR MOTOR
Abstract
In the gear pump or motor including a pair of intermeshing
single-helical pump gears, the thrust acting on the intermeshing
gears is balanced with liquid pressure from the higher pressure
side of the pump or motor which is applied to one end of the
respective gear shafts.
Inventors: |
Kita; Yasuo (Kyoto,
JA) |
Assignee: |
Shimadzu Seisakusho, Ltd.
(Kyoto, JA)
|
Family
ID: |
14052856 |
Appl.
No.: |
05/024,215 |
Filed: |
March 31, 1970 |
Foreign Application Priority Data
|
|
|
|
|
Nov 18, 1969 [JA] |
|
|
44/92382 |
|
Current U.S.
Class: |
418/203;
415/104 |
Current CPC
Class: |
F04C
15/0042 (20130101) |
Current International
Class: |
F04C
15/00 (20060101); F01c 001/16 (); F03c 003/00 ();
F04c 001/10 () |
Field of
Search: |
;418/203
;415/96,107,105 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Croyle; Carlton R.
Assistant Examiner: Vrablik; John J.
Claims
What is claimed is:
1. In a gear pump or motor including a drive shaft, a driven shaft,
a pair of intermeshing drive and driven helical gears fixedly
mounted on the drive and driven shaft respectively, which drive and
driven gears react an axial force on the drive and driven shaft, a
casing housing the gears, the improvement comprising pressure
chambers formed in said casing in alignment with and spaced from
the end of each of the gear shafts toward which the axial force is
directed, means outside the casing for providing communication
between each pressure chamber and the higher pressure side of the
pump or motor so as to have a liquid pressure supplied from the
higher pressure side of the pump or motor to each pressure chamber,
axially movable means located in each pressure chamber for engaging
the end of the gear shaft adjacent the pressure chamber and sealing
the pressure chamber, whereby the thrust from the end of the gear
shaft and the liquid pressure in the pressure chamber bear against
the opposite ends of the axially movable means to balance the
thrust on the ends of the drive and driven shafts.
2. A gear pump or motor as in claim 1 wherein the axial movable
means located in each chamber is a piston and an annular O-ring on
the outer surface of the piston.
3. A gear pump or motor according to claim 2 further comprising a
pressure-receiving plate interposed between each shaft end and each
piston.
4. A gear pump or motor according to claim 3 further comprising a
central cavity formed in the front end surface of each piston
engaging a pressure-receiving plate, and a central port formed in
each piston to provide communication between the central cavity and
the pressure chamber.
5. A gear pump or motor according to claim 4 wherein the liquid
pressure receiving area of the piston engaging with the drive gear
shaft is approximately three times the liquid pressure receiving
area of the piston engaging with the driven gear shaft.
Description
BACKGROUND OF THE INVENTION
This invention relates to hydraulic gear pumps or motors, and more
particularly to an improved means for balancing the thrusts acting
on the intermeshing gears of gear pumps or motors using a pair of
intermeshing single-helical gears.
As for the tooth form of the intermeshing gears for gear pumps or
motors, continuous curves such as arc and sine curve have become
widely used since they are effective to preclude the so-called
"confinement" phenomenon. Even in the case of using such continuous
curve toothform, if straight tooth or spur gears are used
continuous meshing cannot be assured. It is, therefore, required to
use helical gears having a phase shift, i.e. lead, of at least
one-half pitches by the tooth width. Preferably, the lead should be
just one pitch.
With high pressure gear pumps, however, the high bearing loads make
it impossible to increase the tooth width, resulting in an increase
in the helical angle. Such an increase in the helical angle in turn
results in increasing the axial component of the meshing force and
also increasing the axial unbalanced force exerted due to the
inclination of the tooth grooves. Since these unbalanced forces act
as a high thrust load, it has been impossible heretofore to
increase the pump pressure.
In order to solve these problems, an attempt has been made to use
double-helical gears so that said axial unbalanced thrusts can be
counteracted. The gear pumps or motors with the double-helical
gears are, however, disadvantageous in that a higher meshing
accuracy which results in an increase in cost is required. In
addition, the double helical gears are not utilizable for higher
pressure pumps because they suffer from higher bearing loads due to
an increase in the tooth width.
The primary object of the invention is to provide new and improved
gear pumps or motors including a pair of intermeshing
single-helical pump gears in which the above mentioned
disadvantages with known gear pumps or motors can be avoided.
Another object of the invention is to provide new and improved gear
pumps or motors including a pair of single helical pump gears in
which the thrusts acting on the intermeshing helical gears due to
various factors are all conveniently balanced though the
utilization of the liquid pressure of the higher pressure side of
the pumps or motors.
A further object of the invention is to provide improved means for
applying liquid pressure from the higher pressure side of gear
pumps or motors to the one end of the gear shafts thereof in such a
manner that different total pressures are applied to the one end of
the gear shafts according to the different total thrusts acting on
those gear shafts.
SUMMARY OF THE INVENTION
In the gear pump or motor according to the invention, the thrusts
acting on the intermeshing helical gears are balanced with a liquid
pressure. The source for such liquid pressure for balancing the
thrusts acting on the gears may be the higher pressure side of the
gear pump or motor. The liquid pressure is applied to the one end
of each of the gear shafts. In a preferred embodiment of the
invention, the one end of each of the gear shafts is engaged with a
piston axially slidable in a cylinder which is formed in the
casing. Each of the cylinder is communicated with the higher
pressure side of the pump or motor so as to apply the liquid
pressure to the pistons in the respective cylinders. The liquid
pressure receiving areas at the one ends of the gear shafts are so
dimensioned as to balance the respective thrusts of different
magnitudes.
In a gear pump, the liquid pressure receiving area at the one end
of the drive gear shaft is approximately three times the liquid
pressure receiving area at the one end of the driven gear
shaft.
Other features of the invention will be described herein after in
conjunction with the drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a central vertical longitudinal sectional view of a
typical form of the gear pump embodying the present invention;
and
FIG. 2 is an enlarged view of the portion indicated by the lines of
2--2 of FIG. 1.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawings, first particularly to FIG. 1, the
present invention is illustrated in connection with a gear pump,
but it should be understood that the invention may be utilized in
connection with a gear motor.
The pump includes a pair of intermeshing helical gears 11 and 12
mounted within a cylindrical casing 13. The casing 13 comprises a
cylindrical side wall body 14 and end closures 15, 16 at opposite
ends of the body 14. Hereinafter one end closure 15 is referred to
as the front head while the other end closure 16 is referred to as
the end cover plate. The cylindrical body 14 is clamped between the
front head 15 and the end cover plate 16 by four bolts (not shown)
which extends through the inside of the cylindrical body 14 from
the cover plate 16 to the front head 15. Though not shown in the
drawings, the ends of bolts may terminate at the front head 15 and
be screw-secured thereto.
The front head 15 is recessed to contain a roller-bearing 19 and a
suitable oil-seal assembly 20. A drive shaft 21 extends through the
oil-seal assembly 20 and the roller-bearing 19 and into the inside
chamber of the casing 13 to engage and drive the drive gear 11. The
gear 11 is keyed in a conventional manner to the shaft 21. The
drive shaft 21 is supported on the opposite sides of the gear 11 by
a pair of needle bearings 26 and 27 which are in turn received
within bores 28 and 29 recessed in the front head 15 and the end
cover plate 16, respectively. A driven shaft 25 is supported on the
opposite sides of the driven gear 12 by a pair of needle bearings
30 and 31 which are in turn received within bores 32 and 33
recessed in the front head 15 and the end cover plate 16,
respectively.
The intermeshed helical gears 11 and 12 are supported between a
pair of side sealing plates 34 and 35. The side sealing plates 34
and 35 are at their inner ends in sliding contact and in sealing
relationship with the end faces of the intermeshing gears 11 and 12
and abut at their outer ends the end wall 36 of the front head 15
and the end wall 37 of the end cover plate 16 via seat plates 38
and 39. The seat plates 38 and 39 are always in contact with the
end wall 36 of the front head 15 and the end wall 37 of the end
cover plate 16, respectively. The reference numerals 40 and 41
indicates sealing means which are inserted between the side sealing
plate 34 and the seat plate 38, and, between the side sealing plate
35 and the seat plate 39, respectively.
The contact pressure for securing the sealing engagement between
each of the side sealing plates 34, 35 and the intermeshing gears
11, 12 is given by liquid pressure applied to the outer end of each
of the side sealing plates 34, 35. In other words, liquid pressure
from the higher pressure side of the pump is introduced to the
gaps, which may exist between the side sealing plates 34, 35 and
their respective facing seat plates 38, 39, from their peripheries.
Sealing means 40 and 41 define the liquid pressure receiving areas
of the side sealing plates 34 and 35, respectively. In the
embodiment of the invention illustrated in FIG. 1, the liquid
pressure receiving area at the outer end of the side sealing plate
34 is larger than that at the outer end of the side sealing plate
35 since the thrust force of the liquid introduced between the
intermeshing gear teeth is larger at the side of the plate 34 than
at the side of the plate 35. This system for urging the side
sealing plates to the intermeshing gears through the utilization of
the liquid pressure of the higher pressure side of the pump is
known as "Balanced Pressure Loading." No further explanation would
therefore be necessary.
Now I consider the thrusts which act on the intermeshing helical
gears 11 and 12. In FIG. 1, the arrows A and B denote the thrusts
which act on the helical gear 11 and 12, respectively. The thrust A
which act on the drive gear 11 is represented by the sum of a
thrust Fa due to the intermeshing torque T and a thrust Fp exerted
by the liquid on the side sealing plates 34 and 35.
The discharge volume D of the pump per revolution is expressed by
the following formula:
D = 2 .pi. rhb
wherein r is the pitch radius of each of the gears 11, 12, h is the
tooth height of the gears 11, 12 and b is the tooth width of the
gears 11, 12. The transmission torque T of the gears 11, 12 is
given by the following formulas:
2 .pi. T = Dp.apprxeq. 2 .pi. rbhp, accordingly,
T .apprxeq. rbhp
wherein p is the liquid pressure.
The tangential intermeshing force Ft of the gears 11 and 12 is then
expressed as follows:
Ft = T/2r .apprxeq. 1/2 bhp
Accordingly, the thrust Fa due to the intermeshing torque is given
as follows:
Fa = Ft.sup.. tan.theta. .apprxeq. 1/2 bhp tan .theta.
wherein .theta. is the helical angle of the gears 11 and 12.
On the other hand,
Fp = btan .theta..sup.. hp = 2Fa
Accordingly,
A = Fa + Fp = 3Fa .apprxeq. 1/2 bhp tan .theta. (1)
Since the direction of the thrust due to the intermeshing torque T
of the gear 12 is opposite to that of the gear 11, the thrust B
which acts on the gear 12 is expressed by the following
formula:
B = -Fa + Fp = Fa = 1/2 bhptan .theta. (2)
It will be seen from the above that the ratio of A to B is
approximately 3:1.
According to the invention, the above mentioned thrusts A and B
acting on the gears 11 and 12 are balanced with the liquid pressure
from the higher pressure side of the pump which is applied to the
one end of the respective gear shafts 21 and 25. The gear shafts 21
and 25 are engaged at their respective one ends with pistons 51, 52
via pressure receiving plate 53, 54. The pistons 51 and 52 are
slidable in axial directions within the respective cylinders 55, 56
recessed in the end cover plate 16. The cylinders 55 and 56 are
communicated with pressure chambers 57, 58 which are in turn
communicated with the higher pressure side of the pump through
passages 59, 60 and common port 61. This construction is more
clearly illustrated in FIG. 2.
Referring to FIG. 2, the drive shaft 21 with the drive gear 11 is
formed at its end face 62 with a shallow recess 63 at which the
pressure receiving plate 53 is attached and carried. The pressure
receiving plate 53 is in turn in contact with the piston 51 which
is slidably carried in a cylinder 55 which is recessed in the end
cover plate 16. The reference numeral 64 indicates an O-ring
attached to the piston 51. The cylinder 55 is opened to a pressure
chamber 57 to which a liquid pressure is supplied through the
passage 59 and the port 61 from the higher pressure side (not
shown) of the pump. The piston 51 has a central small opening 65
which communicates the cavity formed between the surface of the
pressure receiving plate 53 and the piston 51 with the pressure
chamber 57. The piston 51, the cylinder 55 and the pressure chamber
57 are all elongated in the direction of an extension of the
central axis of the shaft 21. The pressure receiving plate 54, the
piston 52, the cylinder 56 and the pressure chamber 58 are arranged
with respect to the driven shaft 25 is in the same manner as those
for the drive shaft 21.
The same liquid pressure is applied to the pressure chambers 57 and
58. However, since the ratio of the pressure receiving area of the
piston 51 to that of the piston 52 is approximately 3:1, the drive
and driven shafts 21 and 25 receive different total liquid
pressures which can effectively and substantially exactly balance
with the different thrusts A and B acting on the shafts,
respectively.
Thus, according to the invention, it has become possible to obtain
a perfect and reliable balance between the thrust acting on each of
the intermeshing helical gears and the counteracting liquid
pressure. The utilization of piston means separated from the gear
shafts is advantageous in that there is no need of carrying out an
exact alignment of each of the gear shafts with the cylinder to
which pressure liquid is supplied and dispersed with the provision
of an extremely fine sealing means for preventing pressurized
liquid from leaking along the gear shafts.
It should, however, be noted that since the gist of the invention
resides in directly or indirectly constituting the end of the gear
shaft as a pressure receiving surface, the presence of a balancing
piston and pressure receiving surface is not absolutely necessary.
It is also possible to directly admit pressurized liquid to the
gear shaft end surface by providing a seal mechanism of superior
performance in the bearing part. In this case, the gear shaft end
surface itself constitutes a pressure receiving surface. Concerning
all modified embodiments constituting other pressure surfaces
including these modified forms, the invention will comprehend
them.
It should also be noted that the arrangement is not necessarily
limited to the one shown in the drawing. As for the piston area
ratio, for example, it is not absolutely necessary to make it 3:1
and such area may be formed depending upon the unbalanced force
acting on the corresponding shaft. Further, although the static
pressure bearing mechanism has been constructed with pressure
receiving plates interposed, such pressure receiving plates are not
absolutely necessary and the balancing pistons may be disposed
directly opposed to the shaft ends and it is possible to effect
simpler engagement in lieu of the static pressure receiving
mechanism.
Further, in the present invention, the arrangement of the side
seating plates of the bearing mechanism for the gear shafts, etc.
is not limited to the one shown in the drawing. The liquid handled
by the gear mechanism for feeding of liquid will not be limited to
oil.
Further, as for the toothform of the gears of the gear pump
embodying the present invention, the case described above is one in
which a continuous curve toothform is used, but the invention can
also be embodied in a gear pump using an involute toothform or the
like which is in wide use, and the technical scope of the invention
is in no sense limited with regard to these toothforms.
It will be a matter of course that the present invention comprised
of the arrangement described so far can be used not only as a gear
pump but also as a gear motor.
* * * * *