Note: Descriptions are shown in the official language in which they were submitted.
~ 6~ 5
L I N EAR F LU I D MOTOR
Field of the Invention: Th1s invent~on rel~tes to a linear fluid motor
cornprlsin~ a piston mounted on a rod and arranged ~or the pis~on to reclp-
rocate ln an outer cylinder member, and more specifically to such a motor
which is hydraulically operated.
Description of the Prior Art: Linear hydraulic motors are utilized in a
variety of applications in machines and vehicles to accomplish power operation
and/or remote control of parts and components, the operation or remote control
being accomplished by an operator controlling the supply of pressurized hydrau-
lic fluid to the motor from a valve at an operator's station.
~arious constructions have been utilized for securing the piston to the rod
end in such motors and one of these is a threaded or screw type connection. Oneform of screw type connection comprises internal threads in an opening through
the center of the piston and mating external threads on the rod which extends
through the piston. Another known form of screw type connection uses a threadedengagement between external threads on the rod and internal threads on a lock
nut which is disposed adjacent to the p~ston and bears against it, holding it inthe des-ired position on the rod.
Such motors may be subiect to fre~uent operation and may operate at pres-
sures of 2500 pounds per square inch or more. In such motors manufactured
heretofore with normal tolerances and clearances there have been various prob-
lems and among the most serious are the problems caused by abnormal distributionoP lateral forces resulting ~rom m~sali~nment between the piston and cylinder
during some conditions of operation. Such misalignment increases the friction,
may cause noise, may allow dirt to be trapped, and cause undue wear of the
piston anci/or cylinder, and leaking.
Numerous constructions have been utilized heretofore in an attempt to
provide a suitable connection between the piston and rod of a linear hydraulic
motor and in many of such constructions it has been attempted to secure and holdthe piston and rod rigidly together so that they act as an integral reciprocal
member, even though such a rigid connection serves to perpetuate any initial
t~
,, , " . 'I :
: ' ' ' ' " " `: . ,' .,, ,,, -, . ' ,, , ' : ,, ,, ' . . ' ' '
misalignment. With normal or even extraordinary manufacturing tolerances the
alignment of the piston on the rod and the piston with the cylinder ~s not
perfect, when the piston and rod are rigidly connected together, and the
result is abnormal distrlbution of lateral forces between the piston and
cylinder under some circumstances with the resulting deleterious conse-
quences.
In carrying out this invention in a preferred form I provide a linear
fluid mctor of the piston and cylinder type in which the piston is secured
to the rod by a screw connection comprising internal threads on the piston
and the mating external threads on the piston rod. The two sets of threads
are proportioned and dimensloned so that pivotal movement of the piston rod
relative to the piston is allowed which is sufficient to prevent or reduce
abnormal distribution of lateral forces by the piston on the cylinder
during normal reciprocal operat~on of the motor.
FIGURE 1 of the drawing is a plan view of a linear fluid motor according
to the present invention in its fully retracted position,
FIGURE 2 is a view similar to FIG. 1 except with the motor in the
fully extended position,
FIGURE 3 is a fragmentary sectional view showing the portion indicated
by the numeral 3 on FIG. 27
FIGURE 4 is a view along the line 4-~ of FIG. 3,
FIGURE 5 ~s a schematic view illustrat~ng a prior art motor,
FIGURE 6 ls a fragmentary view in section of the portion of FIG. 5 in-
dicated at 6,
FIGURE 7 is a schematic v~ew of the present invention,
FIGURE 8 is a diagram which is illustrative of the present invention,
FIGURE 9 is a diagram which is illustrative of the prior art, and
FIGURE 10 is a diagram which is illustrative of the present invention.
Referring to the drawing, the numeral 10 ln FIG. 1 and other figures
indicates generally a linear fluid motor in accordance with this invention.
The motnr lQ includes an outer cylinder member 12, a piston 14 (see FIG. 3)
-2-
iL~8~;gL8 S
of circular cross section which reciprocates in the cylinder, the piston 14
being mounted on a rod 16. As shown, the motor 10 has a bifurcated portion
18 on rod 16 for connecting the motor to one portion of the devlce or
component which is to be operated by the motor while another bifurcated
portion 20 is rigidly secured as by welding to cylinder 12, the portion 20
having provision for connecting the motor to the other portion of the
device or component which is to be operated by the motor 10.
There are provisions for attaching a hydraulic conduit 22 for admitting
hydraulic fluid to and discharging it from the base structure 21 at the
head end of the motor 10, the head end bein~ the left end in FIG. 1, op-
posite the rod end. At the rod end of the motor provision is made for
attaching a conduit 24 to admit hydraulic fluid to and discharge it from
the rod end of the motor. It will be understood by those skilled in the
art that the motor 10 illustrated is a double acting device in which the
admission of pressurized hydraulic fluid at the rod end through conduit 24
and simultaneously discharging fluid from the head end through conduit 22
moves the motor toward its retracted condition illustrated in FIG. 1. The
admission of pressurized hydraulic fluid to the head end through conduit 22
and the consequent disch~rge of hydraulic fluid from the rod end through ~:
conduit 24 moves the motor from its retracted condition of FIG. 1 to or
toward its fully extended condition of FIG. 2.
FIG. 3 of the drawing is a fragmentary view partially in section
showing a portion of the cylinder 12, a portion of the rod 16 and the
piston 1~, all in the fully extended condltion of FIG. 2. This position of
the motor is also referred to as the minimum retainment position because in ~ .
this position the minimum amount of the rod 16 is retained in the cylinder
12. It ~s in this minimum retainment position that axially d~rected or
other forces actlng on the motor have the most serious effect internally on
the piston and cylinder and this is explained in greater detail hereafter.
As shown in FIG. 3, the motor 10 includes piston 14 which is mounted
on rod 10 by means of a screw connection at 28. The connection 28 comprises
, . . ~ . .
~L~36~L~5
internal threads 30 in the piston 14 and mating external threads 32 on the
rod 16. Around the outer periphery of the piston 26 is a pair of wear
rings 34 and 36 located in grooves 35 and 37 respectively, with a circular
seal 38 and preloading back up ring 39 located between the wear rings.
The piston 26 is not screwed tightly on the rod as in some prior art
constructions nor is it held by means of a lock nut which is screwed
tightly on the rod as in other prior art constructions, one of which is
depicted in FIG. 5. In FIG. 5 a piston indicated at 14a is clamped between
a nut 74 and a shoulder portion 75 on the shaft and thus the piston is
rigidly mounted on the sha~t. In the structure of FIG. 5 the nut 74 ;s
torqued so that the axial force produced on the piston at least equals and
preferably exceeds the force produced on the left end surface of the piston
14a by the hydraulic pressure in the motor during operation. Such torquing
of the lock nut or its removal requires tools which may not be readily
ava71able, particularly if repalrs are required in the field.
In the present invention the piskon is assembled on the rod without
the need for such torquing, in a manner whlch is explalned in detall
hereafter, and is held in that posit~on so that it cannot come off or
undergo any unscrewing action at all, by means of a retaining pin 40 which
is positioned in mating grooves, one in the piston 14 and the other in rod
16. See FIG. 3. The retainer 40 in turn is held by a keeper member 4~
which is held by a machine screw 44 which is threaded into an opening in
plston 14 and torqued suF~iclently to hold it ~n position. FIG. 4 is a
fragmentary view along the lines 4-4 of FIG. 3 show~ng an end view o~ the
parts comprising the arrangement For reta~nlng the piston on the rod.
A suitable seal, such as "0" ring 48 located in lnternal groove 50 in
the piston and bearing against the outer surface of rod 16, is utilized to
prevent leakage between the variable volume flu1d chambers at the opposite
ends of the piston through the screw connection 28.
At the rod end of the motor a gland assembly, indicated generally at
52, is provided for retaining the rod in alignment as it reciprocates back
--4--
- -- , . . , :
.. , .
~L~8~;~L~
and ~orth during operation. Included in the gland assembly 52 is a bearing
member 5~ which ~s secured to cylinder 12 by means of a screw connection at
56. Connectlon 56 util~zes buttress type threads which prevents the gland
member 54 from unscrewing out of the cylinder 12 even under extreme condi-
tions of operation. A seal 58 is provided to prevent leakage of hydraulic
flu;d out through the screw connection 56. An "0" ring 59 is provided at
the outer en~ of the threads 56 to prevent contam;nants from entering the
gland assembly.
The gland assembly 52 illustrated also includes a plate 60 which is
connected to gland member 54 by means of machine screws 62 through a member
64. The rod 16 extends through the opening in the gland bearing member 54
with a clearance which is discussed in greater detail hereafter~ it being
understood that gland bearing member 54 provides lateral suppor~ for rod
16. A seal 66 and an anti-extrusion back up member 68 may be located
inwardly of plate 60 and a wiper member 70 externally of plate 60 as shown
in FIG. 3.
A ring 72 on rod 16 is provided as shown in FIG. 3 between gland
member 54 and piston 26 to limit the movement of the piston toward the rod
end to the position ~llustrated in FIG. 3, and permit free passage for
fluid to and from conduit 24 as well as provide an adequate minimum retain-
ment.
In prior constructions in which it has been attetnpted to secure the
piston rigldly on the rod, to make it in effect integral with the rod,
there is almost always a crookedness angle between the piston and rod
assembly and the cylinder because of the manufacturing tolerances and
eccentricities which are always present except possibly in a very rare case
when they might cancel each other out. This crookedness angle is illus-
trated by the angle E in FIG. 5 oF the draw~ng which shows diagrammatically
in exaggerated form a prior construction in which the piston is secured
rigidly on the rod by means oF a nut 74 as explained previously. Those
parts in FIG. 5 which correspond to l;ke or similar parts in the earlier
. . . ~ -
1~6~85
figures bear the same identifying numbers with an "a" added.
The crookedness angle E ~n FIG. S is ind~cated between the centerline 76 of
the cylinder and the centerline 77,78 of the rod a~d piston. Such angle ;s at
the maximum at the minimum retainment position which is illustrated in FIG. 5
and tends to produce abnormal d~stribution of lateral forces by the piston
and/or the ~ear rings on the inner surface or barrel 13 of the cylinder at
the locations indicated at 8~ and 82 in FIG. 5. As explained later, the
numeral 77 indicates the centerline Gf the rod and 7~ the centerline of the
piston, but in FI6. 5 these two centerlines are shown as coinciding.
FIG. 6 shows in an enlarged and exaggerated view the ultimate result
of such abnormal d;stribution of forces, at location 82, na~ely, the ab-
normal wearing of the wear strip 34a and the retaining lip of the piston
indicated at 33.
FIG. 7 shows a diagrammatic view of the present invention in which the
piston rod has the same crookedness angle as in FIG. 5 but the centerline
78 of the piston remalns parallel with the centerline of the cyl~nder so
that there is no abnormal dlstribution of side forces between the piston
and the surroundlng cylinder, thus eliminating wear of the type illustrated
in FIG. 6. In FIG, 7 centerlines 76 and 78 for the cylinder and the p;ston
respectively are shown as coincident, because of the small scale, but they
actually are parallel as illustrated in FIG. 10.
The manner in which this abnormal distribution of side forces is
eliminated is expla-~ned by the following illustration havlng reference to
F~G. 8 wh~ch shows a d~agram of the key parts of a linear fluid motor in
accordance with the present invent~on having a nominal barrel or inside
diameter of the cylinder of 4 inches and a nominal outside diameter of the
plston rod of 2 inches. Other dimensions for this particular motor are
shown ~n inches in FIG. 8. The following shows how the crookedness angle is
calculated in this typical case and how the thread connection between the
piston and rod is dimensioned and proportioned to overcome the effect of
such crookedness angle, and reference should be had to FIGS. 9 and 10.
-6-
.
" ,
.. . .
6~35
These calculations show how the maximum crookedness angle is determined
for this typical fluid motor utilizing dimensions and tolerances which are
normal and attainab1e in the circumstances. All of the dimensions shown
are ln lnches. In the followlng it will be understood that the double
dimensions in each case indicate the range or tolerance for each which is
acceptable in typical manufacturing procedures. For example, the outside
diameter of the grooves in the piston for the wear r;ngs can vary from
3.768 inches to 3.766 inches and be acceptable. "O.D." means outside diam-
eter and "I.D." means inside d;ameter.
In order to calculate the maximum crookedness angle which could occur
it is necessary to determine two maximum drop or raise dimensions and the
maximum total eccentricity. Reference should be had to FIG. 9 which is a
diagram illustrating in a greatly exaggerated manner the prior art con-
struction of FIG. S. In FIG. 9 as in FIG. 5 the centerline 77 of the rod
and centerline 78 of the piston are shown as coincident and the piston is
shown at 14d in FIG. 9 in dashed lines to illustrate this; that is, the
piston is illustrated as cocked at the maximum crookedness angle. It will
be appreciated that actually the maximum crookedness angle is not percep-
tible.
The maximum center drop M, indicated in FIG. 9 at the left end of
piston 14, is determined as follows:
Piston Groove O.D. =3.768 - 3.766
2 x wear ring thickness = .250 - .2~4
Piston O.D. 4.018 - 4.010
Barrel I.D. =4.025 - 4.021
Piston O.D.(from above cal-
culation) =4.010 - 4.018 -
Max. Clearance = .015 - .003
Max. Center Drop-(1/2
Clearance) = .0075- .0015 = ~
The maxinlum center raise, indicated at N in FIG. 9 at the right end of
gland member 54, is determined in accordance with the following calculation:
Gland Bore =2.004 - 2.002
Rod O.D. =1.998 - 2.000 -
Max. Clearance = .006 - .002-
Max. Center Raise (1/2
Clearance) = .003 - .001 = N
,~ :
~6~L~5
The other dimension needed in calculating ~he maximum crookedness angle,
reflecting eccentricity, is determined in accordance with the following:
Each of the following T.I.R.'s (total indicated readings of
eccentrlcitles) = .003
1. Piston wear ring groove to threaded bore of piston.
2. Rod thread to rod O.D.
3. Gland thread to yland bore.
4. Barrel thread to cylinder bore.
4 x .003 = .012 T.I.R. maximum
or .006 off center = K
The "K" calculated above is illustrated graphically in FIG. 9 as being
additive with "M", and also additive with "N" inasmuch as "N" is above
the centerline of the cylinder, but on the opposite side of the crossover
point 81 of the centerlines, whereas the other two amounts are below.
The foregoing amounts are utillzed in determining the maximum crookedness
angle in accordance with the following formula:
Tangent E max. = M+N+K = 0075 -~ 0~3 ~ .006 = .00367
Maximum crookedness angle = .21
In the above formula P equals the distance between the extremeties of
the bearing surfaces in the minimum retainment position of the motor.
That is, the distance between 14b and 54b as shown in FIGS. 5, 8 and 9.
It is assumed for this purpose that the extreme portion of the piston as
indicated by the retaining lip at 33 in FIG. 6 is in contact with the
barrel 13 of the cylinder.
It will be appreciated that ordinarily the crookedness angle will be
less than the maximum. The maximum will occur only rarely when all of the
variances and eccentricities are cumulative and are maximum at the same
time. This maximum crookedness angle is the max~mum angle which a conven-
tional piston and rod assembly might have with respect to the cylinder in
the minimum retainment position, it be~ng understood that this applies when
it is attempted to secure the piston rigidly on the rod so they act as an
integral member whereby the centerline of the piston always coincides with
the centerline of the rod.
In the present invention the rod is permitted to pivot relatively to
the piston through a pivot angle wh~ch is always more than a predetermined
crookedness angle, so that the centerl1ne of the plston ;s allowed always
to remain parallel to the center llne of the cylinder even though the
centerline of the rod moves.
In the fluid motor disclosed herein sufficient pivotal movement is
provided between the rod and piston to compensate for the maximum crookedness
angle, that is, a pivot angle greater than the maximum crookedness angle is
provided. Such pivot angle is indicated at "F" in the diagram of FIG. 10.
In the present fluid motor the following standard threads, which
appear in the 15th Edition of the Machinery Handbook by Erik Oberg and F.
D. Jones published by the Industrial Press, New York, New York, were initially
considered for use as the internal threads 30 in the piston and the mating
external threads 32 on the rod respectively.
Piston Internal Thread 1.75-8UN-2B
MaJor Di~ension Pitch DiameterMinor Dlmension ?
1.750 1.6786-1.6688 1.6297~1.614i
Piston Rod External Thread 1.75-8UN-2A
Major Dlmension Pitch DiameterMinor Dimension
~.7477-1.7327 1.6665-1.6590 1.5943
Clearances, if the above specified standard threads were used would be as
follows:
Maior Dimension Pitch Diameter Minor Dimension
.0023-.0173 .0023-.0196 .0204-.0354
The foregoing threads might be sufficient in some clrcumstances but
they would not allow for sufficient pivoting action between the piston and
rod to exceed and thereby completely compensate for the maximum crookedness
angle. Accordingly, changes were made in the threads 32 on the
rod.
For an understanding of the manner in which the proper thread dimensions
and proportions are selected refer to FIG. lO of the drawing. It is assumed
in the present case that the effective pivot center between the rod and
~ piston is midway between the two end surfaces of the piston as indicated at
.,~ .. ~, ' ,''
,
_ g
8~
79 in FIG. 10. If the angle "F" indicated in FIG. 10 is greater than the
maximum crookedness angle "E" the movement of centerline 78 with respect to
centerline 77 when the motor is ln the minlmum retainment position, as
indicated at "G" in FIG. 10, is sufficient to exceed what would otherwise
be the max;mum crookedness angle and therefore more than compensate for it.
This construction permits the centerline 78 of the piston to remain parallel
to centerline 76 of the cylinder at all times and thereby prevent the
abnormal distribution of lateral forces by the piston on the cylinder which
results from a rigid connection o~ the piston to the rod.
The threads tentatively seleeted for this motor would provide for a
minimum movement of .0023 as indicated by the above clearance. However, `
since the pivot point is assumed to be m1dway between the ends of the
piston movement "G" o~ the ends of the piston would be determined as follows:
2 G = .0023 and
G = .00115
In the present construction in order to fully compensate for the
maximum crookedness angle it is necessary to provlde movement greater than
,~ ~ .00367 at each end of the piston, tha~ is, G ~00367.
Such minimum movement is determined by multiply~ng the distance between
pivot center 79 and the end of the piston, which is 1 ~ , by the tangent
of angle E, thus
1 x .00367 = .00367 inches
The desired minimum plvokal movement of the rod relative to the piston
can be accomplished by rolling the external piston rod thread .00367 -
.00115 = .00252 or, nominally, .003 deeper. The rod thread O.D. also is
reduced by .006. This changes the piston thread d;mensions and clearances
to the following:
Maior Dimension Pitch DiameterMinor Dimension
l.7417-1.7267 1.6605-1.6530 1.5883
New Clearances:
.0083-.0233 .0083-.0256 .0264-.0414
thus providing that "G" is a minimum of .0083 divided by 2 or .00415. Th;s
exceeds the amount of .00367 which is necessary to more than compensate for
-10-
1~61~S
1 the maximum possible crookedness angle.
In this inst~nce, rolling the threads on the piston roa only
.003 deeper enables sufficient clearance between the mating threads
to compensate for the maximum possible crookedn~ss angle as defined
hereinbefore when all variances and eccentricities ar~ assumed
to be cumulative and at their maximum values.
It will ~e appreciated that it is not necessary in utilizing
the present invention always to compensate for the maximum possible
crookedness angle, especially since the maximum occurs only rarely.
10 In the interest of reducing costs, in recognition of the fact that
some linear motors are subjected to less severe duty than others,
and other factors, it will be appreciatea that the mating threads ?
can be dimensioned and proportioned to compensate for a prede-
termined crookedness angle less than the maximum.
It will be appreciated also that it is necessary in the con-
struction described and illustrated herein to provide sufficient
clearances for the locking pin 40, the grooves in which it is
located, and other associated parts to make certain that there is
no interference by this portion of the structure with the pivotal
20 movement of the rod relative to the piston through the pivot
angle. The pivot angle is maximum at one extreme position of
the motor, which is also the minimum retainment position o
FIG. 3, while the pivot angle is minimum at the other extreme
position of the motor illustrated in FIG. 1~
~n the structure disclosed herein the rod i9 enabled to
pivot with respect to the piston, with such pivoting occurring ~'
in the thxeaded connection 30,32, through a pivot angle sufficient
ko more than overcome the maximum or a predetermined crookedness
angle, even at the point of minimum retainment. This prevents
30 or reduces abnormal distribution of lateral forces by the piston ~`
on the cylinder member during normal reciprocal operation of the
.. .. ~ . . . .. . . .
i~618S
1 motor and thereby minimizes wear and other deleterious effects
of such abnormal d.istribution and prolongs the li~e of the motor.
AS indicated in FIG . 7 the portions of piston 14 on elther side
of seal 48 have .sufficient clearance relative to rod 16 to
permit the pivoting movement of rod 16 with respect to piston 14.
It will be understood khat the present invention is not limited
to the particular linear motor structure disclosed but is
applicable to other equivalent structures. For example, it is
possible to omit wear rings 34 and 36 and their corresponding
grooves 35 and 37 in the piston 14, and utilize instead wear
surfaces which comprise or are integral with the outer cylindrical
surface of the piston. In such a case, the calculation of the
maximum crookedness angle and the desired predetermined pivot
angle of the shaft is changed accordingly.
Another way in which the structure can be modified while
still utiIizing the present invention is to provide a di~erent
structure for connecting the bearing member 54 to the cylinder
12, and adjustinc3 the formula for calculating the crookedness
angle accordingly by omitting or changing the portions relating
to the threaded connection 56~
It will be understood that the crookedness angle referred
to herein can occur in any plane and is not limited to the
single plane shown in the drawing for purposes of illustration.
The pivot connection provided by the threaded connection 28
adapts to a crookedne~s angl~ in any plane. I~ the e~ectlve
pivot point is not centered as indicated at 79 in FIG. 10 then
an appropriate adjustment should be made in determining the
pivot angle.
While I have described and illustrated herein the best
mode contemplated for carrying out my invention it will be appre-
ciated that modifications may be made. Accordingly, it should be .:
understood that I intend to cover by the appended claims all such
modifications falling within the true spirit and scope of myinvention.
`` ! - 12 ~
