U.S. patent number 3,893,787 [Application Number 05/451,257] was granted by the patent office on 1975-07-08 for centrifugal compressor boundary layer control.
This patent grant is currently assigned to United Aircraft Corporation. Invention is credited to Burton A. Jones.
United States Patent |
3,893,787 |
Jones |
July 8, 1975 |
Centrifugal compressor boundary layer control
Abstract
A centrifugal compressor is shown with an inlet directing a
fluid thereto and a diffuser into which the compressor directs its
output. A group or array of circumferential grooves are located in
the surface of a stationary shroud which covers the blades of the
compressor.
Inventors: |
Jones; Burton A. (North Palm
Beach, FL) |
Assignee: |
United Aircraft Corporation
(East Hartford, CT)
|
Family
ID: |
23791474 |
Appl.
No.: |
05/451,257 |
Filed: |
March 14, 1974 |
Current U.S.
Class: |
415/228;
415/173.5; 415/218.1; 415/914 |
Current CPC
Class: |
F04D
29/685 (20130101); F04D 29/162 (20130101); F04D
29/4206 (20130101); Y10S 415/914 (20130101) |
Current International
Class: |
F04D
27/02 (20060101); F04D 29/66 (20060101); F04D
29/68 (20060101); F04D 007/02 () |
Field of
Search: |
;415/213,215,DIG.1
;416/183,186,185 |
Foreign Patent Documents
|
|
|
|
|
|
|
503,332 |
|
May 1954 |
|
CA |
|
963,540 |
|
Jan 1950 |
|
FR |
|
1,057,137 |
|
May 1959 |
|
DT |
|
Primary Examiner: Raduazo; Henry F.
Attorney, Agent or Firm: McCarthy; Jack N.
Claims
I claim:
1. A centrifugal compressor being mounted for rotation having an
axial inlet for delivering a fluid thereto, and a radial outlet for
receiving a compressed fluid therefrom, said compressor having
blades thereon each blade having a continuous outer free edge from
said inlet to said outlet, said blades having an abrupt flow path
section from axial flow to radial flow, a fixed shroud located
between said inlet and outlet spaced from the edges of said blades,
said shroud having annular grooves located therearound facing said
blades, said circumferential grooves being located on the surface
of the shroud opposite the abrupt flow path section where the
flowpath from said inlet turns abruptly toward a radial direction
into said outlet.
2. A combination as set forth in claim 1 wherein the number of
grooves range from 4 to 8.
3. A combination as set forth in claim 1 wherein the grooves are
spaced one-half of a groove width apart.
Description
BACKGROUND OF THE INVENTION
This invention relates to means for increasing compressor
performance and one means previously used in the prior art has been
to incorporate bleed openings for obtaining a desired flow
characteristic.
SUMMARY OF THE INVENTION
A primary object of this invention is to provide a high-work
centrifugal compressor of good efficiency which will minimize flow
energy losses due to shroud friction heating.
It is an object of this invention to reduce local adverse pressure
gradients caused in a flowpath when the flow turns from an axial
direction to a radial direction.
Another object of the invention is to produce a shroud-side flow
profile at the impeller exit to provide good diffuser
performance.
A further object of this invention is to relieve the local
shroud-side adverse pressure gradient with a particular form of
boundary layer control that stabilizes the shroud-side flow and
improves the impeller exit flow profile and thereby increases the
efficiency of the impeller/diffuser system.
Another object of the present invention is to equilibrate
blade-to-blade pressure differences (circumferential flow
nonuniformity) that tend to produce local time-dependent high
adverse pressure gradients with respect to the tangential
direction.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a longitudinal cross section of a centrifugal
compressor.
FIG. 2 is an enlarged cross section taken along the line 2--2 of
FIG. 1.
FIG. 3 is a chart showing a comparison of compressor efficiency
with surge margin for a 6:1 pressure ratio impeller.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring to FIG. 1 a centrifugal compressor 1 having an impeller 4
with blades 6 is shown with an inlet section 2, a stationary shroud
8 adjacent the blades 6, and a diffuser 10. The impeller 4 is
splined to a shaft 12, which may form part of a gas turbine engine
and is fixed to the shaft by being bolted at its rearward side to
an annular flange 14 which is shown integral with the shaft. The
forward end of the impeller 4 is bolted to another annular flange
16 which is fixed to a sleeve 18 mounted around the shaft 12.
Sleeve 18 can be fixed with respect to shaft 12 by any means
desired. A compressor of this type is shown and described in U.S.
Pat. No. 3,420,435.
An array of circumferential grooves 20 are located in the surface
of the stationary shroud 8 exposed to the flow path between the
blades 6 and through the impeller 4. FIG. 2 shows one of the
grooves 20. Each groove 20 has a bottom surface 20a and a depth D,
while adjacent grooves are separated by a land 22 which is the
portion of the shroud wall which joins two grooves. The side of the
blade 6 facing the indicated direction X of impeller rotation is
labeled with a plus (+) to indicate high pressure; and the side of
the blade 6 facing away from the direction of rotation is labeled
with a minus sign (-) to indicate low pressure. The volume provided
by the circumferential grooves 20 accommodates low energy flow
adjacent the wall of the shroud 8. Low energy air adjacent the wall
of the shroud 8 is pumped into each groove 20 by the high pressure
side of the blades 6. In the cavity the meridional and normal
velocity components are reduced to zero, resulting in increased
static pressure and tangential velocity of the air in the cavity.
This accommodation of low-energy air reduces the size of the
boundary layer in the vicinity of the grooves. An equilibrium flow
of air into and out of the grooves is established by the relative
high and low pressure sides of the blade. The partially stagnated
air in the groove is pumped out of the groove as a result of the
pressure difference between the high pressure in the groove and the
low pressure on the low pressure side of the blade, whereupon it
mixes with the higher energy through flow and is carried
downstream. As a result of the circumferential communication
provided by the plurality of grooves, circumferential flow
nonuniformities are washed out thus attenuating time non-steady
pressure gradients.
For maximum effectiveness, grooves 20 are located near the point of
incipient boundary layer separation on the surface of the
stationary shroud 8. Conventional boundary layer calculation
techniques are used to estimate this point. It will usually be
found to occur where the surface of the shroud adjacent the
flowpath turns abruptly toward the radial direction. The depth D
and width W of each groove 20 should approximate the boundary layer
displacement thickness calculated at the point of incipient
separation. If the depth or width of a groove 20 exceeds the
boundary layer displacement thickness by a value greater than 2,
the groove volume will accommodate higher energy air and the
effectiveness will diminish. This observation has been established
from systematic experimentation with groove geometry. The optimum
number of grooves and their spacing has also been established on
the basis of systematic tests of a variety of grooved shroud
configurations. The optimum number of grooves was found to be no
less than 4 and no more than 8. The grooves were spaced one-half
groove width apart, this means that the width of the land 22 is
one-half of the width of the grooves. Where the side walls of the
grooves are tapered the average groove width is used.
FIG. 3 is a comparison of net efficiency with surge margin for a
6:1 pressure ratio impeller with various shroud configurations. The
shroud configurations which were used involved a shroud having a
smooth inner surface, a grooved inner surface having 4 grooves, and
a grooved inner surface having 8 grooves.
* * * * *