U.S. patent number 3,819,309 [Application Number 05/296,563] was granted by the patent office on 1974-06-25 for means for altering the effective displacement of an axial vane compressor.
This patent grant is currently assigned to General Motors Corporation. Invention is credited to James W. Jacobs.
United States Patent |
3,819,309 |
Jacobs |
June 25, 1974 |
MEANS FOR ALTERING THE EFFECTIVE DISPLACEMENT OF AN AXIAL VANE
COMPRESSOR
Abstract
In preferred form an axial vane compressor including a housing
enclosed by end plates having inner face cam surfaces and rotatably
supporting a drive shaft. A rotor is secured to the drive shaft for
rotation therewith within the housing between the cam surfaces of
the end plates. A specified axial clearance is provided between the
rotor and the cam surfaces at their areas of closest proximity. The
rotor contains at least one axially extending slot slidably
receiving an axially slidable pumping vane. The vane terminates in
arcuate edge surfaces in sliding engagement with the end plate cam
surfaces and is moved axially by the cam surfaces relative to the
rotor during rotation thereof so as to vary the effective volume in
fluid working chambers on either side of the rotor as the rotor
rotates through inlet and pressurization cycles. In this manner the
vane draws in and compresses fluids in the respective work
chambers. The rotor is provided with axially aligned cavities in
the opposite faces of the rotor having predetermined volumes so
that the effective displacement of the rotor in each of the
aforementioned work chambers is regulated in accordance with the
size of these cavities. This regulation occurs as a result of a
predetermined volume of pressurized fluid being carried by the
cavities into the intake cycle as the rotor rotates from the
pressurization cycle. The clearance between the rotor and the cam
surfaces allows this portion of the pressurized fluid to flow
against the vanes assisting rotation of the rotor. Therefore, the
provision of the rotor cavities and the clearance between the rotor
and the cam surfaces results in recapturing some of the work used
to pressurize the portion of the fluid carried forwardly into the
intake cycle. By providing cavities of a predetermined size in the
rotor surfaces an axial vane compressor can be suited to a range of
applications such as occurs in air conditioning systems in compact
vehicles as compared to similar systems in large vehicles.
Inventors: |
Jacobs; James W. (Dayton,
OH) |
Assignee: |
General Motors Corporation
(Detroit, MI)
|
Family
ID: |
23142555 |
Appl.
No.: |
05/296,563 |
Filed: |
October 11, 1972 |
Current U.S.
Class: |
418/219;
418/232 |
Current CPC
Class: |
F04C
18/3448 (20130101) |
Current International
Class: |
F04C
18/344 (20060101); F04C 18/34 (20060101); F04c
001/00 () |
Field of
Search: |
;418/77,79,217,219,228,229,232 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Husar; C. J.
Assistant Examiner: Smith; Leonard
Attorney, Agent or Firm: Engle; Charles R.
Claims
I claim:
1. In an axial vane compressor of the type including a housing,
said housing being enclosed by end plates, at least one of said end
plates having a cam surface on its inner face; a drive shaft
rotatably mounted in said end plates; a rotor secured to said shaft
for rotation therewith through fluid inlet and fluid pressurization
cycles within said housing between said end plates; said rotor
being in sealing engagement with the inner peripheral surface of
said housing and having a face defining at least one fluid
pressurizing chamber in association with said end plate cam
surface; at lease one axially extending slot formed in said rotor;
a compressor vane slidably received in said slot; inlet and outlet
ports connecting with said fluid pressurizing chamber; rotation of
said drive shaft axially moving said vane in said slot as the said
vane slidably engages the end plate cam surface whereby the volume
in said fluid chamber is varied during rotation of the shaft to
sequentially draw fluid into said chamber during an inlet cycle and
subsequent discharge through said outlet ports upon completion of a
pressurizing cycle; the improvement comprising: the provision of a
cavity of predetermined volume in the fluid chamber defining face
of said rotor whereby a portion of the fluid pressurized during the
pressurization cycle is carried into the inlet cycle thereby
decreasing the effective displacement of the compressor, the
pressurized fluid in the inlet cycle assisting rotation of the
rotor by virtue of application of the pressurized gas on one side
of said vane; said cavity being formed of a specific volume
sufficient to provide a predetermined desired output of pressurized
fluid from said compressor.
2. In an axial vane compressor of the type including a housing;
said housing being enclosed by a pair of end plates having a cam
surface on their inner faces; a drive shaft rotatably mounted in
said end plates; a rotor secured to said shaft for rotation within
said housing dividing the interior thereof into separate fluid
working chambers; opposite radially extending faces of said rotor
partially defining said working chambers; said rotor faces being
spaced from said cam surfaces providing a specified clearance
therebetween at the area of closest proximity, a plurality of
axially extending slots in said rotor; a pumping vane slidably
mounted in each of said slots; said vane moving through fluid inlet
and fluid pressurization cycles as said rotor rotates moving said
vanes axially thereof as they engage said cam surfaces; the
improvement comprising: axially aligned oppositely facing cavities
of a predetermined volume in the radially extending faces of said
rotor; said cavities capturing a portion of the fluid pressurized
during the pressurization cycle and carrying it into the fluid
inlet cycle where it acts against a pumping vane aiding rotation of
said rotor as it flows through the clearance provided between said
rotor and said cam surfaces; the predetermined volume of said
cavities decreasing the effective displacement of said compressor
thereby varying it for a particular work application.
3. In an axial vane compressor of the type including a cylindrical
housing; end plates having matched cam surfaces on their inner
faces enclosing said housing; a drive shaft rotatably journaled in
said end plates; a rotor secured to said drive shaft being
positioned within said housing between said cam surfaces for
rotation relative thereto; said rotor including radially extending
faces partially defining fluid chambers on either side thereof in
association with said cam surfaces; an inlet passage connecting
with each of the fluid chambers on either side of said rotor; an
inlet valve in each of said passages; a discharge passage
connecting with each of said fluid chambers on either side of said
rotor; a discharge valve in each of said passages; a plurality of
equiangular circumferentially spaced axially extending slots formed
in said rotor and said drive shaft; a compressor vane slidably
received in each of said slots and having edges in rubbing contact
with each of the end plate cam surfaces; said rotor having an outer
peripheral surface in sealing engagement with an inner peripheral
surface of said housing dividing the housing into the
aforementioned separate fluid chambers on either side of said
rotor; rotation of said drive shaft causing said compressor vanes
to move axially within their respective slots as their edges engage
the end plate cam surfaces so as to vary the volume of the
respective fluid chambers on either side of said rotor so that the
volume in each of said chambers sequentially changes from a maximum
fluid inlet volume to a minimum fluid compressing volume as said
rotor rotates and said vanes move axially in response to engagement
with said cam surfaces; the improvement comprising the provision of
preformed cavities of a specific volume less than the fluid chamber
volumes in axial alignment in the opposite radial surfaces of said
rotor whereby the effective displacement of said compressor is
regulated discharging a predetermined volume of pressurized fluid;
the pressurized fluid remaining in said rotor cavities applying a
pressure against said vanes aiding rotation of said rotor.
Description
This invention relates to rotary axial vane compressors and more
specifically to means for varying the effective displacement of
such compressors.
In general rotary axial vane compressors include a housing enclosed
by end plates having inner cam surfaces. A rotor is mounted on a
drive shaft and is positioned between the cam surfaces. Axially
movable vanes are mounted in the rotor and move relative to the
rotor as they engage and follow the cam surfaces. In so doing, they
vary the volume on either side of the rotor between an inlet
maximum volume and a compressing or pressurizing minimum volume. It
is obvious that the same results can be obtained by fixing the
shaft and rotating the housing relative thereto. While the subject
invention is described in association with an axial vane compressor
having fluid working chambers on each side of the rotor, it is also
apparent the machine can be readily designed to pump fluid on one
side of the rotor only.
Rotary axial vane compressors, by virtue of their inherent design
characteristics including that of not being adjustable, provide a
substantially constant effective fluid displacement resulting from
one complete revolution of the rotor within the housing.
Consequently, a machine of a predetermined size has a constant
capacity and therefore is not normally suitable for a range of work
loads. Of course, on the other hand, production efficiency is
enhanced and costs are reduced when a relative large number of
compressors of uniform size are produced. For these reasons, it is
a purpose of this invention to provide a means for simply and
economically adapting a standard compressor assembly to a range of
operating capacities. By practicing my invention a quantity of
compressor rotors can be produced and then be machined to provide
oppositely axially aligned cavities in the rotor radially extending
faces to adjust the effective displacement of the machine to suit a
particular use. If, for example, the compressor assembly is to be
used with an air conditioning system in a large vehicle, the rotor
can be assembled in the compressor without cavities so that a
maximum effective fluid displacement is obtained. In such
installation, a compressor having a displacement of approximately
12.6 cubic inches is desirable. In vehicles of medium size, the air
conditioning system requires a lesser effective displacement of
approximately 10.8 cubic inches. In a compact vehicle, an air
conditioning system may require as low as 7.5 cubic inches
effective displacement. By providing an air conditioning compressor
capable of adaptation to an entire line of vehicles it is obvious
that production of the resulting large quantities of components
creates a manufacturing situation wherein maximum efficiency can be
obtained and large quantities of materials can be purchased at
minimum cost.
Accordingly, it is a primary object of my invention to provide a
basic rotary fluid compressor assembly capable of slight
modification so as to adapt the compressor to a range of load
applications.
Another object of my invention is the provision of a standard
rotary axial vane compressor wherein cavities of specified size are
formed in rotor surfaces, the cavities carrying a quantity of
pressurized fluid into the intake cycle so as to prevent discharge
thereof thereby varying the effective displacement of the standard
machine.
A further object of my invention is the provision of a specific
clearance between the rotor and end plate cam surfaces at their
areas of closest proximity so that the pressurized fluid in the
rotor cavities is carried into the intake cycle of the machine and
applied against the axial vanes aiding rotation of the rotor.
The novel features which I believe to be characteristic of my
invention are set forth with particularity in the appended claims.
My invention itself, however, both as to its organization and
method of operation, may best be understood by reference to the
following description taken in connection with the accompanying
drawings in which:
FIG. 1 is an elevational view of a rotary axial vane compressor,
partly in section, illustrating the assembled relationship of a
rotor incorporating features of my invention.
FIG. 1A is an enlarged fragmentary view illustrating the detailed
structure of a vane assembly used in an axial vane compressor in
association with my invention.
FIG. 2 is an unfolded geometrically developed view of the path of a
vane as it traverses one complete revolution within the compressor
housing.
FIG. 3 is a fragmentary view, partly in section, of a rotor removed
from the compressor and including cavities in accordance with my
invention.
Referring now to the drawings, a rotary axial vane compressor
assembly 10 having particular application in vehicle air
conditioning systems has a central cylindrical housing 12 enclosed
by end plates 14 and 16 as shown in FIG. 1. The end plates 14 and
16 have bearing surfaces 18 and 20 rotatably supporting like
surfaces 22 and 24 on a drive shaft 26 which can be rotated by a
vehicle engine through a pulley and clutch assembly not shown. The
end plates 14 and 16 have cam inner faces 28 and 30 which cooperate
with cylindrical housing 12 defining a generally cylindrical fluid
chamber 32. A circular rotor 34, attached to the shaft 26, is
adapted to rotate with the shaft in chamber 32. While the rotor 34
may be formed to support any number of vanes 36, in preferred form
it contains three equally circumferentially spaced slots 38, each
axially slidably supporting a vane 36. In one form, the vanes 36
are longitudinally split into halves 40 and 42, as best shown in
FIG. 1a,and contain a centrally disposed spring 44 positioned
within a chamber 45 formed by cavities 45a and 45b molded in the
vane halves 40 and 42, respectively. The spring 44 engages
respective edges of the cavities 45a and 45b biasing the vane
halves 40 and 42 to the exaggerated position shown in FIG. 1a and
in this manner maintains positive engagement with cam faces 28 and
30. The vane halves 40 and 42, respectively, include upwardly
extending arcuate end surfaces 41 and 43 which engage the cam faces
28 and 30. These vane halves 40 and 42 terminate in rectangular
shoulders 40a and 42a which support the vane halves in the
compressor assembly. As can be seen in FIG. 1A, the contour of the
cams 28 and 30 forces the vane halves 40 and 42 axially relative to
one another against the force of spring 45 so as to insure a sealed
engagement with the cam surfaces biases their edges into engagement
with cam faces 28 and 30.
Rotation of the shaft 26 rotates rotor 34 and the vanes 36 within
the fluid chamber 32 causing the vanes to slide axially as they
engage the cam faces 28 and 30. Since an oil film on the outer
periphery of the rotor provides a seal between it and inner surface
46 of cylindrical housing 12, the fluid chamber 32 is divided by
rotor 34 into separate working chambers 48 and 50 so that each vane
36 is effective to compress fluid in both chambers as the shaft 26
is rotated. The end plate 14 has affixed an inlet fluid fitting 52
which directs the fluid to passages in both end plates 14 and 16,
not shown, which connect with fluid inlet ports 54 illustrated in
FIG. 2. Likewise, the end plates contain discharge ports 56
controlled by spring biased ball check valves 58 which regulate
flow of pressurized fluid from both fluid chambers 48 and 50 to a
combining discharge passage 60 from which the fluid exits the
compressor. With reference to the developed view in FIG. 2, it can
be seen that during a fluid inlet cycle, the fluid is drawn through
port 54 into a maximum volume chamber 62 defined by vanes 36, cam
face 28 and the rotor 34. Continued rotation of rotor 34 moves the
fluid toward a minimum volume chamber 64 during a fluid
pressurizing cycle whereupon the fluid is sufficiently pressurized
moving the ball valve 58 against its spring discharging the fluid
through passage 60. As shown, the compressor 10 is double acting
because of the vanes 36 engaging both of the cam faces 28 and 30 on
the opposite side of the rotor.
It is readily apparent from the developed view is FIG. 2, a
compressor of this type does not lend itself to adjustments for
varying its effective capacity. The rotor 34 is of a fixed size and
the housing 12 along with end plates 14 and 16 are not easily
adjustable. As a result the usual rotary axial vane compressor has
a fixed predetermined effective fluid displacement. In accordance
with my invention, cavities 66 of a predetermined size are machined
in axial alignment in opposing rotor faces as best illustrated in
FIG. 3. These cavities 66 are filled with pressurized fluid during
the compression cycle and contain the fluid as they move with the
rotor 34 into the inlet cycle where the fluid is re-expanded into
maximum volume chambers 62. The quantity of pressurized fluid
carried over decreases the effective displacement of the compressor
to the extent of the volume of cavities 66. Obviously, in
accordance with my invention a basic machine can be designed to
provide a predetermined displacement which can readily be modified
by the cavities 66 so that the unit is capable of being used in a
range of load applications. Furthermore, the quantity of fluid
re-expanding into the maximum volume chamber 62 from the cavities
66 can perform useful work. The provision of a clearance 68 in the
range of 0.010 to 0.020 inches between the rotor faces 70 and the
cam faces 28 and 30 at their areas of closest proximity, which
occurs at the conclusion of the pressurizing cycle, permits
application of the re-expanding fluid against the vanes 36 thereby
assisting rotation of the rotor 34. Use of these clearances 68
provides for recovery of approximately 93 percent of the work used
to pressurize the fluid in the cavities 66.
While I have shown and described a particular embodiment of my
invention it will, of course, be understood that various
modifications and alternative constructions thereof may be made
without departing from the true spirit and scope of my invention
and that I intend by the appended claims to cover all such
modifications and alternative constructions as fall within the true
spirit and scope of my invention.
* * * * *