U.S. patent number 3,578,889 [Application Number 04/887,472] was granted by the patent office on 1971-05-18 for rotary engine vane sealing means.
This patent grant is currently assigned to United Aircraft Corporation. Invention is credited to George A. Bonner, Louis C. Dagne, Howard J. McLean.
United States Patent |
3,578,889 |
Dagne , et al. |
May 18, 1971 |
ROTARY ENGINE VANE SEALING MEANS
Abstract
A vaned rotary-type engine having vanes with a main body portion
and a telescoping tip seal with separate means being provided to
support the main part and support the tip seal so that neither
places a radial load on the housing in which the vane rotates. The
main portion has cam rollers which ride in cam tracks so that as
the vane rotates the radial load is taken through the rollers. The
tip seal is supported at each end by two large ball bearing units
which are fixed in the housing and have carriers which abut the
ends of the tip seal.
Inventors: |
Dagne; Louis C. (Juno, FL),
McLean; Howard J. (North Palm Beach, FL), Bonner; George
A. (Palm Beach Gardens, FL) |
Assignee: |
United Aircraft Corporation
(East Hartford, CT)
|
Family
ID: |
25391213 |
Appl.
No.: |
04/887,472 |
Filed: |
December 23, 1969 |
Current U.S.
Class: |
418/147; 418/256;
418/133; 418/265 |
Current CPC
Class: |
F01C
21/0809 (20130101); F01C 21/0836 (20130101) |
Current International
Class: |
F01C
21/08 (20060101); F01C 21/00 (20060101); F01c
019/02 () |
Field of
Search: |
;418/133,147,148,256,260,264,265 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Croyle; Carlton R.
Assistant Examiner: Goodlin; Wilbur J.
Claims
We claim:
1. In combination in a rotary vane type engine, a housing having a
cylindrical surface therein, a rotor mounted in said housing having
sideplates and means connecting said sideplates, vanes being
mounted in said rotor with each vane comprising a main inner
portion and a telescoping flat tip seal, the inner portion of said
vane being retained against radial movement by means located in
said housing, annular stop means being mounted in a recess on each
side of said housing adjacent and engaging each sideplate, said
annular stop means being mounted for relative movement with said
housing, the outer end of each flat tip seal of each vane engaging
the inner diameter of its cooperating annular stop means thereby
retaining each flat tip seal against radial movement, the portion
of the outer end of each flat tip seal between said annular stops
thereby being spaced a predetermined distance from the cylindrical
surface of the housing.
2. A combination as set forth in claim 1 wherein the inner diameter
of each annular stop is less than the inner diameter of the
cylindrical surface of the housing.
3. A combination as set forth in claim 1 wherein the inner diameter
of each annular stop is greater than the inner diameter of the
cylindrical surface of the housing.
4. A combination as set forth in claim 1 wherein seal means are
provided between the housing and the adjacent side of each annular
stop means.
5. A combination as set forth in claim 4 wherein each seal means
comprises an annular seal, said annular seal being positioned in an
annular groove in said housing, spring means biasing said seal
against its annular stop means.
6. A combination as set forth in claim 1 wherein each annular stop
means includes an annular bearing means positioned in engagement
with said housing, and an annular member extending inwardly to
provide the portion engaging the flat tip seal.
7. A combination as set forth in claim 6 wherein each annular
bearing means contains an inner and outer race, each outer race
being biased outwardly from said housing to insure a positive
engagement of the adjacent annular member with its cooperating
sideplate.
8. A combination as set forth in claim 6 wherein flange means
extends around the outer periphery of each annular member for
locating its cooperating annular bearing means thereon, and means
biasing each annular member towards its flange means.
Description
BACKGROUND OF THE INVENTION
The vaned rotary engine is of the type shown in U.S. Pat. No.
3,301,233 and U.S. Pat. No. 1,986,556. However, neither of these
patents provide any mechanism for performing the function of
subject invention. In U.S. Pat. No. 3,132,632, sealing members are
made light to provide a seal between the vanes and the housing.
SUMMARY OF THE INVENTION
A primary object of the present invention is to maintain a minimal
sealing gap between the tip seal of rotary engine vanes and housing
by antifriction bearings which limit in a radial direction the
proximity of the vane tip seal to the housing. In accordance with
the present invention, sealing between the vanes and the bearing
cavity is obtained by a circumferential face seal, loaded by
springs against the bearing carrier. The combination is made
thermally compatible by making the components of material of like
or compensating coefficients of expansion.
BRIEF DESCRIPTION OF THE DRAWING
The figure is a section taken through a vaned rotary-type engine
showing the mounting of a vane having a movable vane tip seal.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The housing shown consists of an end member 10, a center section
12, and another end section 14. These sections can be fixed
together by any means desired, such as by through bolts. The center
section 12, which is of interest here, is formed having an inner
cylindrical surface 16 and is finned at 18 to provide cooling. The
vane rotor 19 mounted for rotation with respect to said housing
comprises a plurality of members 20 which extend through said
center section 12 and are fixed between sideplates 22 and 24, which
are located on each side of the center section 12, to provide slot
areas therebetween for the positioning of vanes 26 for relative
sliding movement therewith.
The vane rotor 19 is mounted for rotation off center from the
center of the cylindrical surface 16. Through this eccentric
mounting the top surface 21 of each member 20 which forms the inner
side of each chamber between the sides of vanes 26 and the
cylindrical surface 16, moves from a point adjacent the surface 16
(as shown) to a point, 180.degree. away therefrom, which is a
maximum distance away from the cylindrical surface 16 and back
during a complete revolution.
As in the patents referred to above, air is taken in a chamber at
one point, a combustible mixture is formed in one of the chambers
at one point, compressed through the action of the chambers just
referred to, ignited at another point, and exhausted from the
chamber when the chamber approaches the point at which air is taken
in.
Each vane 26 has a main body 40 which is formed as a flat plate
with its sides 41 located adjacent its cooperating sideplate, 22
and 24 respectively. The bottom of each vane has a narrowed down
width portion 32 which has a short shaft 34 extending outwardly on
each side on which cam rollers 30 are mounted. The outer end of the
vane has a slot 42 formed therein. A notch 43 is located on each
side of the vane extending from the outer end down into said slot
approximately halfway. A flat seal member 44 is positioned in said
slot and has an extension 45 on each end which fits into a notch
43. When the bottom of the seal member 44 rests on the bottom of
the slot 42, the seal member just barely projects out of the main
part of the vane 40. Since the vane rotor 19 rotates both the main
part of the vane 40 and the seal member 44, they are thrown
radially outwardly.
To prevent the outer edge of a seal member 44 from engaging the
cylindrical surface 16 as it rotates and to prevent the remainder
of the vane from having contact with the seal member 44 thereby
increasing the force acting through the seal member, two mechanisms
are employed.
One mechanism includes cam tracks 36 positioned within said
cylindrical surface 16 and between said sideplates 22 and 24 in
which the cam rollers 30 are guided. The cam tracks are
concentrically mounted with the cylindrical surface 16 so that as
the vanes 26 sweep around the housing, the outer edge is maintained
a predetermined distance from the surface while all radial forces
are taken up by the cam tracks.
A second mechanism is included which takes the radial loads of the
tip seal members 44 thrown outwardly by centrifugal force while
maintaining the seal gap A. This mechanism includes a similar
construction on each side of the center section 12. Both sides of
the center section 12 adjacent the seal member 44 are cut away
forming recesses 50 and 52 around the entire center section to
receive an annular ball bearing member 53 and 54, respectively,
along with an annular bearing carrier 56 and 58, respectively.
Each annular ball bearing member has its outer race slidably
mounted in said center section with its outer surface in contact
with the top annular surface 60 of the cutaway portion or recess.
The inner race of the ball bearing member is positioned on the
outer surface of the bearing carrier and an outwardly extending
flange 62 extends around the outer periphery of the bearing
carrier. A spring 66 of the Belleville washer type presses the
outer race away from said center section 12 of the housing and
through the balls pushes the inner race outwardly. The inner race
mounted on the outer surface of the bearing carrier abutting the
flange 62 pushes the annular bearing carrier outwardly so that it
contacts the inside of the sideplates at B. When the spring 66,
ball bearing unit 53, and bearing carrier are in position the inner
diameter of the bearing carrier extends inwardly from the surface
16 for a very small distance.
It can now be seen that each seal member 44 thrown outwardly is
supported at each end by the inner surfaces of the annular bearing
carriers 56 and 58 and is therefore automatically spaced from the
inner surface 16. An annular carbon seal 70 is positioned in each
slot 72 on each side of said center section 12 and each is biased
to engage the inner surface of its cooperating annular bearing
carrier, 56 or 58, by a wave spring 76.
An alternate construction to attain a minimum gap at A would be to
build the engine with the vane 44 engaging the adjoining housing 12
with the carriers 56 and 58, each having an inner diameter greater
than the diameter of the surface 16 forming a gap 77 at each end of
the vane with the carriers. This construction allows the vane 44 to
rub against the inside of housing 12 during rotation. As the tip of
vane 44 engaging the housing wears down, gap 77 gradually closes
until the vane comes into contact at its ends with carriers 56 and
58. Bearings 53 and 54 then pick up the centrifugal load of vane
44. The gap A would then be at a satisfactory minimum
condition.
* * * * *