U.S. patent number 3,852,003 [Application Number 05/359,030] was granted by the patent office on 1974-12-03 for pressure-sealed compressor.
This patent grant is currently assigned to Robert Bosch GmbH. Invention is credited to Gerhard Adalbert, Jurgen Hess, Ernst Linder.
United States Patent |
3,852,003 |
Adalbert , et al. |
December 3, 1974 |
PRESSURE-SEALED COMPRESSOR
Abstract
A vane compressor has a rotor with radial vanes mounted in a
housing cavity bounded by an endless actuator surface engaged by
the outer ends of the vanes, and laterally bounded by two end walls
having confronting stationary faces slidingly engaged by the rotor
end faces to form clearance gaps. The end walls have conduits
communicating with a high pressure container housing connected with
the outlet of the housing, and opening in ports on the stationary
housing faces, respectively, so as to fill and seal the gaps with
high pressure fluid. The ports are longer in circumferential than
in radial direction, and are located in an imaginary axial plane in
which the vanes, which are completely inward pushed by the actuator
surface, are located. Pressure ducts in the end walls are connected
through an annular recess in the rotor shaft with an annular space
in the rotor which is connected with the radially inner ends of the
vane slots.
Inventors: |
Adalbert; Gerhard
(Markgroningen, DT), Hess; Jurgen (Markgroningen,
DT), Linder; Ernst (Muhlacker, DT) |
Assignee: |
Robert Bosch GmbH (Stuttgart,
DT)
|
Family
ID: |
5844712 |
Appl.
No.: |
05/359,030 |
Filed: |
May 10, 1973 |
Foreign Application Priority Data
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May 12, 1972 [DT] |
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2223156 |
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Current U.S.
Class: |
418/93;
418/DIG.1; 418/268; 418/99 |
Current CPC
Class: |
F04C
29/0007 (20130101); Y10S 418/01 (20130101) |
Current International
Class: |
F04C
29/00 (20060101); F04c 027/00 () |
Field of
Search: |
;418/97,98,99,266,267,268,269,93 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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415,030 |
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Aug 1934 |
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GB |
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692,690 |
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Jun 1953 |
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GB |
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Primary Examiner: Husar; C. J.
Assistant Examiner: Smith; Leonard
Attorney, Agent or Firm: Striker; Michael S.
Claims
We claim:
1. Pressure-sealed compressor comprising housing means including a
central housing part having a cylindrical cavity surrounded by an
endless inner actuator surface, a pair of end walls closing the
ends of said cavity and having confronting stationary faces, a
tubular pintle on one of said end walls, and inlet and outlet means
for a fluid, said housing means further including a container for
high pressure fluid communicating with said outlet means and having
an outlet for high pressure fluid; rotor means mounted on said
housing means for rotation about an axis, and including a rotor
having rotor end faces slidingly engaging said stationary faces and
forming clearing gaps therewith, a drive shaft portion mounted in
said tubular pintle for rotation and including a thin shaft portion
formed with an annular recess, and a plurality of vanes
respectively mounted in radial slots of said rotor and having outer
ends slidingly engaging said actuator surface for forming expanding
and contracting chambers between said rotor and said actuator
surface, said inlet and outlet means communicating with said
chambers, said rotor being formed with an annular space surrounding
said pintle and connecting radially inner ends of said slots; said
housing means being formed with duct means connecting said outlet
means and said annular space so that high pressure in said slots
urges said vanes into engagement with said actuator surface, said
annular recess forming part of said duct means and communicating
with said annular space; and at least one of said end walls being
formed with a conduit having one end connected with said outlet
means and the other end formed as a port in said stationary face of
said end wall opening into the respective gap between the
respective stationary face and rotor end face so that fluid is
pressed into said gap for sealing the same against leakage.
2. Compressor as claimed in claim 1, wherein the other end wall is
formed with a conduit having one end communicating with said
container and the other end forming a port in the respective
stationary face of said other end wall opening into the respective
other gap between the other stationary face and the other rotor end
face so that the same axial pressure acts at opposite ends of said
rotor.
3. Pressure-sealed compressor comprising housing means including a
central housing part forming a cylindrical cavity surrounded by an
endless inner actuator surface, a pair of end walls closing the
ends of said cavity and having confronting stationary faces, and
inlet means and outlet means for a fluid; rotor means mounted in
said housing means for rotation about an axis, and including a
rotor having rotor end faces slidingly engaging said stationary
faces and forming clearance gaps therewith, and at least one vane
mounted in a radial slot of said rotor and having an outer end
slidingly engaging said actuator surface for forming expanding and
contracting chambers between said rotor and said actuator surface,
said inlet means and outlet means on said housing means
communicating with said expanding and contracting chambers,
respectively; and each of said end walls being formed with a
conduit having one end connected with said outlet means and the
other end formed as a port in the respective stationary face of the
respective end wall opening into the respective gap between the
respective stationary face and rotor end face so that fluid is
pressed into both gaps for sealing the same against leakage, each
of said ports being longer in circumferential direction than in
radial direction.
4. Compressor as claimed in claim 3, wherein said rotor means
include four vanes forming in said cavity between said rotor and
said actuator surface two expanding suction chambers and two
contracting pressure chambers alternating with said suction
chambers; wherein said actuator surface places diametrically
disposed vanes simultaneously in innermost positions when passing
through an imaginary axial plane whereby on one side of said
imaginary plane high pressure, and on the other side of said plane
low pressure prevails in said cavity; and wherein said ports are
located in said imaginary axial plane and have port portions
located on opposite sides of said imaginary axial plane.
5. Compressor as claimed in claim 4, wherein the radial outer
boundary of said port is spaced from the outer surface of said
rotor a radial distance between 2 and 5 millimeters.
6. compressor as claimed in claim 4, wherein the port portion
located on said one high pressure side of said imaginary plane is
longer in circumferential direction than the port portion located
on the other low pressure side of said imaginary plane.
7. Compressor as claimed in claim 6, wherein two-thirds of the area
of said port are located on said high pressure side and one-third
of the area is located on said low pressure side of said imaginary
plane.
8. Compressor as claimed in claim 3, wherein said rotor is formed
with an annular space connecting the radially inner ends of said
radial slots; and wherein said housing means are formed with duct
means connecting said outlet means with said annular space so that
high pressure in said slots urges said vanes into engagement with
said actuator surface.
9. Compressor as claimed in claim 8, wherein said duct means
include a throttle upstream of said annular space.
10. Compressor as claimed in claim 8, wherein said housing means
include a container for high pressure fluid communicating with said
outlet means and having an outlet for high pressure fluid; wherein
said conduit has said one end communicating with said container;
and wherein said duct means communicates with said container.
Description
BACKGROUND OF THE INVENTION
The present invention relates to rotary compressors, particularly
vane compressors which have a rotor whose end faces form clearance
gaps with lateral stationary faces.
The U.S. Pat. No. 2,654,532 discloses a rotary vane compressor in
which high pressure oil from the output is used as sealing medium
for the clearance gaps. The oil is supplied from the high pressure
outlet along the rotor shaft to the end faces of the rotor where it
is required for sealing. The actual amount of oil reaching the
clearance gaps cannot be determined and may be irregular.
The arrangement of the prior art has the disadvantage that the oil
used for sealing the clearance gaps of compressor is not used in
the optimal manner, since oil is also supplied to parts of the
compressor where the sealing is not necessary. In order to have a
sufficient amount of oil available for a complete sealing where
required, a comparatively large flow of oil along the rotor shaft
is necessary in the prior art. It cannot be avoided that such large
amounts of oil also flow in the expanding and contracting chambers
formed by the vanes and by the actuator suface surrounding the
same. The space in the contracting chambers is thus reduced, and a
lesser amount of oil is pressed into the outlet, which reduces the
efficiency of the compressor.
The U.S. Pat. No. 1,776,921 discloses a rotary vane compressor in
which oil, under the outlet pressure of the compressor, is used as
a sealing and lubricating medium. In this compressor, oil flows out
of a high pressure container through a central bore in the rotor
shaft to the radial slots in which the vanes are mounted for radial
movement. The oil serves on the one hand for pressing the vanes
against the endless actuator camming surface, and on the other hand
seals and lubricates the vanes guided in the vane slots. The
disadvantages explained above are present also in this
compressor.
SUMMARY OF THE INVENTION
It is one object of the invention to provide a compressor,
particularly a vane compressor, in which the oil required for
sealing the clearance gaps, is optimally used, so that only a
minimum of oil is used for this purpose.
Another object of the invention is to supply fluid from the high
pressure outlet of the compressor, to the clearance gaps between
the rotor end faces and lateral stationary faces of the
housing.
In accordance with the invention, the lateral end walls of the
housing which have the stationary end faces, are provided with
conduits, having one end communicating with high pressure outlet
means, and another end formed as a port in the respective
stationary face.
In the preferred embodiment of the invention, the ports in the
lateral stationary faces are oblong and curved, and longer in
circumferential direction than in radial direction. The distance
between the radially outer edge of each port, and a circle on the
stationary face having the diameter of the rotor, is between 2 and
5 mm.
It is particularly advantageous if two-thirds of the area of the
port are located on the high pressure side, and one-third of the
port is located on the low pressure side of an imaginary axial
plane passing through the diametrically located rotor portions
where the vanes assume their innermost position in the vane slots
due to the action of the endless camming actuator surface on the
outer ends of the vanes.
The novel features which are considered as characteristic for the
invention are set forth in particular in the appended claims. The
invention, itself, however, both as to its construction and its
method of operation, together with additional objects and
advantages thereof, will be best understood from the following
description of specific embodiments when read in connection with
the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is an axial sectional view taken on line I--I in FIG. 2;
and
FIG. 2 is a cross sectional view taken along line II--II in FIG.
1.
DESCRIPTION OF THE PREFERRED EMBODIMENT
The illustrated compressor has housing means which substantially
include five parts, namely a left end wall 1 covered by a cover 17,
an annular central housing part 3 having an inner ellipsoid camming
actuator face 3c, a right end wall 2, and a container 23 secured to
cover 17 by screws 17a and enveloping the end wall 2 and the
central housing part 3.
Housing parts 1, 2 and 3 form a cavity 4 bounded by confronting
stationary faces 1a and 2a of the end walls 1 and 2, and by the
inner endless actuator surface 3c. Rotor means are provided which
include a rotor 5 having end faces 5a and 5b, and a rotor drive
shaft 6 which is secured to the bottom portion 5c of rotor 5 at one
end, and has another end projecting out of the housing for being
driven by a suitable motor. The outer cylindrical surface 5' of
rotor 5 has a diameter which matches the length of the smaller axis
of the ellipsoid inner endless actuator surface 3c so that a
diametrical axial plane 29 is located between two crescentshaped
portions of the cavity 4 located between the rotor surface 5' and
the inner endless actuator surface 3c. The end wall 1 is integral
with, or secured to, a tubular pintle 9 which projects inward into
the cavity 4, and more particularly into a cylindrical bore in
rotor 5. Rotor shaft 6 passes through the interior of tubular
pintle 9 and has two journal portions 6b and 6c located in bearings
8 and 7 provided in the interior of the tubular pintle 9. Bearing 8
is located in a portion of the pintle 9 which projects outward from
end wall 1. The shaft portion between journal portions 6b and 6c
has an annular recess 6a communicating at one end through a bore
and throttle 32 in the wall of pintle 9, with an annular space 31
communicating with the inner ends of the radial slots 12 in which
vanes 13 are mounted for radial movement. The other end of recess
6a is connected by a duct 30 with liquid 27 in the lower portion of
container 23.
A thrust bearing 11, preferably a needle bearing, is mounted
between the inner free end of pintle 9 and a corresponding shoulder
of the bottom portion 5c of rotor 5 to take up axial forces between
the stationary pintle 9 and the rotor 5.
The radially outer ends of the vanes 13 abut the elipsoid inner
endless camming surface 3c due to the pressure of the fluid
supplied through the duct means 30, 6a, 32, 31 to the inner ends of
the vanes 13.
The two crescent-shaped spaces between the rotor 5 and the inner
endless actuator surface 3c are divided by diametrically disposed
vanes 13 into expanding suction chambers 14b, and contracting
pressure chambers 19c.
Suction chambers communicate through radial inlet passages 14, and
axially extending bores 14a, with the inlet means 15 through an
annular channel 16 in cover 17. Cover 17 has a tubular portion
through which shaft 6 passes, sealed by sealing means 18.
The high pressure chambers 19c communicate through outlets 19 and
leaf spring check valves 20 with axial pressure passages 21
provided with filter outlets 22 opening into the interior of the
container 23 which has an outlet 25, protected by a baffle 24, and
contains liquid 27 under high pressure.
As best seen for end wall 2, both end walls 1 and 2 are provided
with conduits 26 whose lower ends communicate with the interior of
high pressure container 23, and receive liquid therefrom. The lower
portion of conduit 26 is covered in FIG. 1 by the duct 30, but the
extension of conduit 26 in end wall 1 is the same as in end wall 2.
A portion of conduit 26 is omitted in end wall 2 for the sake of
clarity, and it will be understood that conduit 26 passes around
the recess 2c in end wall 2, and passes around the inner bore of
the tubular pintle 9 in end wall 1.
The upper ends of the two conduits 26 in end walls 1 and 2 are
provided with ports 28 which open on the confronting inner
stationary faces 2a and 1a of end members 2 and 1. Each port 28 is
arcuate and oblong in circumferential direction, so that the
circumferential extension of each port 18 is greater than its
radial dimension. The radially outer edge or boundary 28' of each
port 28 and the outer rotor surface 5' is between 2 and 5 mm., and
preferably 4 mm.
Two-thirds of the area of each port 28 are located on the high
pressure side of an imaginary diametrical axial plane 29, and
one-third on the low pressure side of plane 29 which passes through
the rotor axis, and through the generatrix of the cylindrical outer
rotor surface 5' where the vanes 13 are in the innermost positions
in slots 12. In other words, two-thirds of the area of port 28 is
located on the side of plane 29 facing the outlets 19, and
one-third of the area of port 28 is located on the side of plane 29
facing the inlets 14.
During rotation of rotor 5 in clockwise direction, the outer edges
of vanes 13 slide along the endless elipsoid inner camming actuator
surface 3c so that chambers 14b expand and suck the fluid to be
compressed from the inlet openings 14, axial conduits 14a, annular
space 16 and inlet 15. During further rotation, the spaces 19c
contract so that the compressed fluid is discharged through the
leaf spring check valves 20 into the outlet passages 21 and through
the filters 22 into the high pressure container 23 from where the
fluid is discharged through outlet 25.
Immediately after the compressor has started working, and rotor
shaft 6 with rotor 5 is driven, the interior of the housing
container 23 is subjected to high pressure.
The stored oil 27 is pressed into the conduits 26 in the end walls
1 and 2 and into the duct 30 in end wall 1. Liquid under pressure
flows out of the ports 28 in the confronting stationary faces 1a
and 2a of the end walls 1 and 2, and is pressed into the clearance
gaps between stationary faces 1a and 2a and rotating rotor end
faces 5a and 5b.
It has been found by tests that in the region where the ports 28
are located, and where the greatest pressure differentials occur
within the respective clearance gaps are safely sealed by the oil
pressed into the clearance gaps through the ports 28.
Oil is also pressed out of pressure container 23 into the duct 30
from where it flows through the recess 6a in rotor 6, the throttle
32, and annular connecting space 31 into the inner ends of the vane
slots 12 so that the vanes 13 are pressed radially outward into
engagement of their outer ends with the endless inner camming
actuator surface 3c, sealing the expanding suction chambers 14b
from the contracting pressure chambers 19b. At the same time, the
oil in shaft recess 6a, lubricates the bearings 7 and 8 of the
rotor shaft 6. The elipsoid shape of the actuator surface 3c of the
central housing wall 3 which exerts a cam action on the vanes 13,
is geometrically designed so that the radial stroke of two
diametrically arranged vanes 13 in outward and inward direction,
corresponds in every position of rotor 5 to an exactly equal length
of the strokes in inward and outward directions of the two vanes 13
which are angularly displaced 90.degree. in relation to the first
two vanes 13. This has the result that the volume of liquid in the
common annular space 31 is constant in every position of rotor 5
with vanes 13.
The quantity of oil leaking out of the clearance gaps 1a, 5a and
2a, 5b and between the outer ends of vanes 13 and the actuator
surface 3c, is replenished through throttle 32, which may be
omitted under certain circumstances, and by throttled flow along
the bearing 7 whose play permits a throttled flow. The oil volume
in the annular space 31 and in the inner parts of vane slots 12
serves as damping oil for the vanes 13 and prevents chatter of
vanes 13, which frequently occurs in vane compressors of the prior
art.
The ellipsoid inner actuator surface 3c, which is suitable for a
two-flow compressor, may be replaced with a circular inner actuator
surface having an axis eccentric to the rotor axis so that the
compressor is a single-flow compressor.
It is also possible to provide the elipsoid endless inner actuator
surface 3c with a circular portion parallel to the outer
cylindrical surface of the rotor so that the sealing between the
rotor 5 and the respective portions of the inner endless actuator
surface 3c is improved. In such an arrangement, the imaginary plane
29, which determines the position of the ports 28, passes through
the rotor axis and the generatrix of the outer rotor surface, which
is located in the center of the regions where the outer surface of
the rotor and the circular portions of the inner surface 3c are
parallel.
It will be understood that each of the elements described above, or
two or more together, may also find a useful application in other
types of pressure-sealed compressors differing from the type
described above.
While the invention has been illustrated and described as embodied
in a pressure-sealed compressor in which the clearance gaps at the
ends of the rotor are provided with high pressure oil through
conduits and ports in the end members of the housing, it is not
intended to be limited to the details shown, since various
modifications and structural changes may be made without departing
in any way from the spirit of the present invention.
Without further analysis, the foregoing will so fully reveal the
gist of the present invention that others can by applying current
knowledge readily adapt it for various applications without
omitting features that from the standpoint of prior art fairly
constitute essential characteristics of the generic or specific
aspects of this invention and, therefore, such adaptations should
and are intended to be comprehended within the meaning and range of
equivalence of the following claims.
What is claimed as new and desired to be protected by Letters
Patent is set forth in the appended claims.
* * * * *