U.S. patent number 3,805,672 [Application Number 05/302,233] was granted by the patent office on 1974-04-23 for double acting fluid pressure operable cylinder device.
This patent grant is currently assigned to Westinghouse Bremsen-und Apparatebau GmbH. Invention is credited to Ewald Pekrul.
United States Patent |
3,805,672 |
Pekrul |
April 23, 1974 |
DOUBLE ACTING FLUID PRESSURE OPERABLE CYLINDER DEVICE
Abstract
A double-acting fluid pressure operable cylinder device
including both resilient and needle valve means for cushioning the
end of the piston stroke against damaging impact thereof with the
cylinder head. The resilient member and needle valve are arranged
relative to each other so that the resilient member is engaged
somewhat in advance of the end of the piston stroke to commence the
cushioning effect but not so to prevent free-flow exhaust of fluid
pressure from the cylinder chamber until just before the end of the
piston stroke when the resilient member is effective for sealing
off the unrestricted exhaust path and limiting final exhaust at a
restricted rate via an adjustable needle valve.
Inventors: |
Pekrul; Ewald (Nienstedt,
DT) |
Assignee: |
Westinghouse Bremsen-und
Apparatebau GmbH (Hannover, DT)
|
Family
ID: |
5829366 |
Appl.
No.: |
05/302,233 |
Filed: |
October 30, 1972 |
Foreign Application Priority Data
|
|
|
|
|
Dec 27, 1971 [DT] |
|
|
2164832 |
|
Current U.S.
Class: |
91/396; 91/26;
92/85B; 92/85R |
Current CPC
Class: |
F15B
15/223 (20130101) |
Current International
Class: |
F15B
15/00 (20060101); F15B 15/22 (20060101); F15b
015/22 () |
Field of
Search: |
;92/85
;91/396,395,394,25,26 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Geoghegan; Edgar W.
Assistant Examiner: Hershkovitz; Abraham
Attorney, Agent or Firm: McIntire, Jr.; R. W.
Claims
Having now described the invention, what I claim as new and desire
to secure by Letters Patent, is:
1. In a cylinder device having at least one cylinder head in which
is formed a combined fluid pressure supply and exhaust cylindrical
recess for reciprocably accommodating therein, with radial
clearance, an end portion of the piston rod of a piston and rod
assembly and a diametrally enlarged portion of the piston rod
formed in juxtaposition to the adjacent one side of the piston, in
combination:
a. an annular groove formed in said cylinder head coaxially with
and adjacent to the opening of said recess, said annular groove
being defined by two oppositely facing and spaced apart end walls
radially disposed relative to the wall of said recess and joined by
a cylindrical surface forming the side wall of said groove;
b. a resilient annular sealing member disposed in said groove for
axial movement therein relative to said recess between the limits
defined by said spaced apart end walls, said annular sealing
member, when in a relaxed state, having an inner diameter larger
than said end portion and smaller than said enlarged portion of the
piston rod and an outer diameter less than that of said side wall
of said annular groove to provide an expansion clearance
therebetween;
c. unrestricted passage means comprising said radial clearance
between said piston rod and said cylindrical recess and the radial
clearance between said inner diameter of said annular sealing
member and said end portion of the piston rod for providing
unrestricted flow of fluid under pressure to and from a cylinder
chamber formed adjacent said one side of the piston during axial
movement of said end portion of the piston rod through said
unrestricted passage means coinciding with movement of the piston
in one direction toward the cylinder head or in the opposite
direction away therefrom; and
d. restricted passage means disposed in said cylinder head in
parallel relation to said unrestricted passage means with one end
opening to said annular groove and the other end opening to said
cylindrical recess, said enlarged portion of the piston rod being
effective, when moving axially through said sealing member, for
cutting off said unrestricted passage means and limiting flow of
fluid pressure between said cylinder chamber and said cylindrical
recess to a restricted rate through said restricted passage means
only,
e. said sealing member having communicating passage means formed
therein for communicating said cylinder chamber with said
restricted passage means during such time that said unrestricted
passage means is cut off and having an annular frontal portion
projecting axially out of said groove into said cylinder chamber,
said frontal portion being abuttingly engaged by the piston during
final movement thereof for providing final cushioning effect on the
piston and consequent distortion of the sealing member in said
groove against said one end of said restricted passage means for
cutting off said communicating passage means from said restricted
passage means and, therefore, said restricted flow through the
restricted passage means during said final movement of the piston
in said one direction.
2. A cylinder device, as set forth in claim 1, wherein the axial
dimension of that portion of the sealing member confined within
said annular groove is less than the axial distance between said
end walls of the groove.
3. A cylinder device, as set forth in claim 1, wherein said frontal
portion of said sealing member comprises an annular toroidal
surface formed adjacent the inner diameter of the sealing member
and in facing relation to the cylinder chamber, said toroidal
surface joining at its inner periphery with a tapered concentric
opening expanding diametrically toward the cylindrical recess and
at its outer periphery with a beveled surface sloping away from the
toroidal surface toward said cylindrical recess, the end wall of
said annular groove adjacent the cylinder chamber being
complementarily beveled and uniformly axially spaced from the
beveled surface of the sealing member.
4. A cylinder device, as set forth in claim 1, wherein said
communicating passage means in said sealing member comprises a
plurality of angularly spaced passageways extending axially
therethrough for communicating said cylinder chamber with said
restricted passage means for effecting said restricted flow to and
from said cylinder chamber during said axial movement of said
enlarged portion through said sealing member.
5. A cylinder device, as set forth in claim 4, wherein a
communication between said angularly spaced passageways and said
one end of said restricted passage means is provided via a common
annular channel formed on the side of said sealing member opposite
said frontal portion and to which said spaced passageways open,
said channel also registering with said one end of said restricted
passage means opening to said annular groove.
6. A cylinder device, as set forth in claim 5, wherein distortion
of the sealing member resulting from engagement thereof by said
piston moving in said one direction causes said annular channel to
be compressed against the respective adjacent end wall of said
annular groove and cooperating therewith for sealing off said
communication between said angularly spaced passageways and said
one end of the restricted passage means.
Description
BACKGROUND OF THE INVENTION
Other known double-acting cylinder devices are provided with
sealing members and adjustable needle valve devices at each end of
the cylinder, as above noted, each of said sealing members being
intended, just before the end of the piston stroke, to interrupt
free or direct exhaust of fluid pressure from the pressure chamber
almost simultaneously by sealing on both the piston rod projection
sliding therethrough and the groove in which the sealing element is
disposed, thereby limiting exhaust through a restricted opening of
a needle valve for cushioning the piston impact. Since the
transitional stage or change-over from direct exhaust flow to
restricted flow is simultaneous in nature, adjustment of the needle
valve to provide faster rate of exhaust for accelerating retraction
of the piston can result in severe piston impact and resulting
damage. Moreover, such damaging results may also occur if the
sealing member, due to wear resulting from constant frictional
sliding contact with the piston rod projection, loses its sealing
effect, whereby effective cushioning, which would be limited to the
effects of the needle valve only, is lost.
SUMMARY OF THE INVENTION
The object of the present invention is to provide a double-acting
cylinder device characterized by cushioning means providing
positive protection against damages resulting from piston impact at
the end of the stroke, said cushioning means being adjustable,
without risking loss of maximum cushioning effect, to compensate
for misadjustments and wear of the cylinder components.
The invention comprises a double-acting fluid pressure operable
cylinder device having pressure chambers on opposite sides of the
piston adjacent respective cylinder heads at opposite ends of the
cylinder, each of said chambers being subjectable to fluid pressure
and relief thereof alternately and in reverse order relative to
each other, depending on direction of stroke movement of the
piston. Each of the cylinder heads is provided with a coaxial
tapered recess for accommodating, at the end of the piston stroke
in one direction or the other, respective coaxial cylindrical
portions carried by the piston rod adjacent to and on opposite
sides of the piston. A resilient annular sealing member of
particular cross-sectional area is disposed, with both axial and
radial spacing, in respective particularly cross-sectionally shaped
annular grooves surrounding the openings of each of the tapered
recesses, said sealing member being engageable by the adjacent
cylindrical portion, during final movement of the piston stroke, in
advance of the end of said stroke for initiating cushioning effect
of the piston. Upon engagement of the sealing member by and sliding
movement therethrough of the cylindrical portion, said sealing
member is expandingly deformed so as to make sealing contact with
the bottom of the groove just prior to the end of the stroke,
thereby cutting off free-flow exhaustion of fluid pressure from the
pressure chamber and diverting such exhaustion at a restricted rate
through an adjustable needle valve, with which the degree of
cushioning of the piston can be regulated.
The sealing member has a beveled annular portion part of which
projects axially out of the annular groove and into the pressure
chamber beyond the inner axial limit of the cylinder head, thus
permitting the cylindrical portion of the piston to engage said
sealing member and provide cushioning effect ahead of its valve
action (seating on the bottom of the groove) before the piston
reaches the cylinder head.
The single FIGURE drawing is an axial view, in section, of a
double-acting cylinder device embodying the invention.
DESCRIPTION AND OPERATION
In the drawing, a double-acting cylinder device designated 1
comprises a cylinder casing 2 and a pair of cylinder heads 3 and 4
secured at opposite ends of the cylinder casing, respectively. A
piston 5 and a piston rod 6 are operably disposed in the cylinder
casing 2, said rod slidably extending exteriorly of the cylinder
device through a guide bushing 7 coaxially secured in cylinder head
3 and in sealingly sliding relation with a sealing ring 8 coaxially
disposed in said cylinder head adjacent the inner end of said guide
bushing. A scraper or cleaning ring 9, disposed coaxially in
cylinder head 3 adjacent the outer end of guide bushing 7, provides
cleaning action for the piston rod 6 as said rod moves reciprocably
therethrough in contacting relation therewith.
The items described below with which both cylinder heads 3 and 4
are similarly provided are assigned similar reference numerals and
primarily described in connection with cylinder head 3 only, it
being understood that the description thereof is applicable equally
to cylinder head 4 also.
An adjustable needle valve 10 is mounted in cylinder head 3,
forming a variable throttle opening 11 between a radial passageway
12 and axial passageway 13 in cylinder head 3. The piston rod 6 has
a pair of enlarged cylindrical portions 14 formed coaxially thereon
in juxtaposition to the opposite sides of piston 5, respectively.
Coaxial recesses 15 are formed in cylinder heads 3 and for
accommodating the cylindrical portions 14, respectively, at the end
of the piston strokes. Each of the recesses 15, by being connected
to a combined inlet-outlet port 16, provides passage means via
which fluid pressure may be admitted to or exhausted from the
cylinder device. The radial passageway 12 belonging to needle valve
10 also opens radially into recess 15 between the two ends of the
recess, said recess tapering from the open end adjacent piston 5
toward its base adjacent sealing ring 8. Recess 15 is
concentrically surrounded at the larger open end thereof facing
piston 5 with an annular groove 18. Groove 18 is defined by a
cylindrical side wall of greater diameter than the opening of
recess 15, an internally beveled annular flange 19 extending
radially from the end of said cylindrical side wall adjacent piston
5 and having an inside diameter smaller than said cylindrical side
wall but greater than said opening, and an annular flat bottom
surface 20 radially disposed between the other end of said
cylindrical side wall and the periphery of said opening
perpendicularly to the axis thereof. The axial boring 13 belonging
to the needle valve 10 also emerges into groove 18 at the bottom
surface 20.
It should be mentioned that the cylindrical portions 14 can be
independent sleeves or bushings, as shown in the drawing, or formed
integrally with the piston rod 6 or the piston 5.
An elastic annular sealing member 21 is normally loosely disposed
in groove 18 with a small axial clearance, as indicated at C.
Sealing member 21 is characterized by a flat sealing surface 22
complementarily adapted for sealingly engaging bottom surface 20
and cooperating therewith as a valve. Sealing member 21 is also
provided with a beveled front surface 23 facing the piston 5 and
complementary to the internally beveled flange 19. The beveled
front surface 23 joins with a toroidal surface comprising the
adjacent internal portion 24 of the sealing member 21 which
diminishes diametrally toward the juncture with said toroidal
surface, said juncture comprising a smallest diameter 26
substantially smaller than the outer diameter of the cylindrical
portion 14 which is provided with a beveled leading end 27. A
larger diameter 28 of the conical surface 25 adjacent the bottom 20
of groove 18 is essentially the same or somewhat smaller than the
outer diameter of the cylindrical portion 14.
Sealing member 21 is further provided with a plurality of angularly
spaced and axially disposed through-passageways 29 connecting a
cylinder chamber 30 to the axial passageway 13, associated with
needle valve 10, via a common annular V-shaped channel 31 formed in
the sealing surface 22 of sealing member 21 and intersecting said
passageways 29. Moreover, a sealing edge 32 of sealing member 21
makes annular contact with bottom 20 of groove 18 on a circular
area between the through-passageways 29 and annular channel 31 and
between the central conical surface 25 of the sealing member 21 and
said channel 31. Although for purposes of convience, one of the
passageways 29 opening to channel 31 appears to be axially aligned
with passageway 13, this is not the actual structure. In the actual
construction of the invention, none of the passageways 29, for
purposes to become evident hereinafter, is permitted to coincide
axially with passageway 13.
The mode of operation of the device is described below with
reference to the right side of the double-acting cylinder 1;
In the position shown in the illustration, port 16 of the right
cylinder head 3 is being supplied with fluid pressure, while the
corresponding port 16 on the opposite cylinder head 4 is exhausted.
For purposes of convenience, port 16 in cylinder head 3 will be
referred to hereinafter as the right port, while port 16 in
cylinder head 4 will be referred to as the left port.
Now if the left port 16 is subjected to fluid pressure and the
right port 16 exhausted, then piston 5 is moved toward the right.
At this point, the compressed air located in cylinder chamber 30
escapes, at first unthrottled, through the space formed between
piston rod 6 and central opening 25 of sealing member 21, recess 15
of cylinder head 3, and the combined inlet and outlet right port 16
to atmosphere. After covering about half of the piston stroke
distance, the cylindrical portion 14 on the right side of piston 5
enters into the central conical opening 25 of sealing member 21
while causing sealing member 21 to be expanded radially by means of
the front beveled end 27. At this time, sealing member 21 tightly
encircles the cylindrical portion 14, especially at the point of
the smallest diameter 26 of said sealing member, so that
unrestricted flow of fluid pressure medium from the cylinder
chamber 30 into recess 15 of cylinder head 3 is interrupted at this
point. Thus the compressed air remaining in chamber 30 can only
escape through the through-passageways 29 and annular channel 31 of
sealing member 21 through the throttle opening 11 into recess 15
adjusted by means of needle valve 10 which is located between
passageways 12 and 13 of cylinder head 3. In this way, the piston
movement is cushioned or retarded on the last portion of the
stroke, with the partially trapped fluid pressure in cylinder
chamber 30 being compressed by such piston movement and, therefore,
acting, in addition to the friction-contact effect of the
cylindrical portion 14 on sealing member 21, to force the sealing
surface 22 and the sealing edge 32 of sealing member 21 tightly
against bottom surface 20 of groove 18, so that channel 31 is also
flattened out against said bottom surface to momentarily seal off
passageways 29 from passageway 13, so that no pressure can escape
via this route either. This is the reason, as was previously noted,
that none of passageways 29 may be in axial alignment with
passageways 13.
Shortly before reaching an inner wall 33 of cylinder head 3, piston
5 is elastically caught and braked by the beveled surface 23 of
sealing member 21 axially projecting beyond the axial limit of said
inner wall into the cylinder chamber 30, the toroidal surface 24
being the first to come into contact with piston 5. In this way,
possible damage resulting from a hard metallic contact of piston 5
with inner wall 33 of cylinder head 3, which is normally of metal
construction, is avoided, such damage being more apt to occur when
throttle opening 11 is adjusted to a relatively large opening of
needle valve 10 or a weak initial cushioning of the piston movement
is effected.
When piston 5 impinges on the toroidal buffering edge 24 of sealing
member 21, the latter is so deformed that it grips the cylindrical
portion 14 of piston 5 with an even greater encircling force and
intensifies the sealing effect.
Upon renewed venting of left port 16 or supply of fluid pressure to
right port 16, sealing memeber 21 is axially displaced leftwardly
by the measure of its axial clearance to the point of contact with
the internal beveled surface of flange 19 of annular groove 18 as a
result of the pressure building up in recess 15 of cylinder head 3
due to the concurrent choking or throttle action of needle valve 10
and the initially slowly retreating piston 5, so that the sealing
surface 22 and particularly the sealing edge 32 is loosened from
the bottom 20 of annular groove 18. The fluid pressure medium can
now enter into cylinder chamber 30 through the communication thus
produced, with a slight throttling effect, via annular channel 31
and axial passageways 29 of sealing memeber 21 to strongly act on
piston 5. After cylindrical portion 14 has emerged from central
opening 25 of sealing member 21, all barriers to unrestricted flow
of fluid pressure into chamber 30 are removed so that piston 5 can
be acted on by the full fluid pressure.
The design and installation of sealing member 21 represented is
especially simple and advantageous with respect to the flow of
pressure medium.
In the manner above described, damage to the cylinder device 1,
particularly to the piston 5 and cylinder head 3, is avoided so
that wear of the sealing member 21 occurring in the course of time
on the sealing edges of said sealing member when performing valve
functions cannot have a destructive effect on the cylinder device
as a result of the weaker initial cushioning of the piston stroke
caused by such wear. Moreover, the particular strcture of the
invention makes it possible to enlarge the throttle opening 11 by
adjustment of the needle valve 10 without risk, when a higher or
more rapid rate of piston retraction is desired, since the energy
of the more rapid retraction of the piston 5 intended and achieved
in this way is also nullified by the final cushioning action of the
frontal buffering area of toroidal surface 24.
Advisably, since the toroidal front surface 24 blends into the
central conical opening 25 via such a donut-shaped rounding, a
satisfactory deformable buffering edge is provided whose
deformation also causes an increase in the closing force and thus
the sealing of the sealing memeber 21 on the cylindrical portion 14
encircled by said conical opening.
* * * * *