U.S. patent application number 15/835788 was filed with the patent office on 2018-06-14 for vane pump with one or more less restricted vanes.
The applicant listed for this patent is Stackpole International Engineered Products, Ltd.. Invention is credited to Paul MORTON.
Application Number | 20180163543 15/835788 |
Document ID | / |
Family ID | 62489025 |
Filed Date | 2018-06-14 |
United States Patent
Application |
20180163543 |
Kind Code |
A1 |
MORTON; Paul |
June 14, 2018 |
VANE PUMP WITH ONE OR MORE LESS RESTRICTED VANES
Abstract
A vane pump that employs one or more less restricted vanes (or
looser vanes) within its rotor is described herein. The less
restricted vane(s) are configured to radially move outwardly before
the remaining vanes during startup. In one case, for example, at
least one vane has a different thickness (e.g., thinner) as
compared to the thickness of the remaining vanes. In another case,
at least one slot has a different width (e.g., wider) as compared
to the width of the other slots. The less restricted vane
facilitates a cold start in highly viscous oil by allowing easier
radial displacement and thus earlier initial build-up of pressure
in the pump. The pump may be used with an engine or
transmission.
Inventors: |
MORTON; Paul; (Mississauga,
CA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Stackpole International Engineered Products, Ltd. |
Ancaster |
|
CA |
|
|
Family ID: |
62489025 |
Appl. No.: |
15/835788 |
Filed: |
December 8, 2017 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
62432194 |
Dec 9, 2016 |
|
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|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 2/3442 20130101;
F04C 2270/701 20130101; F04C 28/06 20130101; F04C 2/3446 20130101;
F01C 21/0836 20130101; F01C 21/0809 20130101; F01C 21/0863
20130101 |
International
Class: |
F01C 21/08 20060101
F01C021/08 |
Claims
1. A vane pump comprising: an inlet for receiving fluid from a
source; an outlet for delivering pressurized fluid to a system
therefrom; a pressure chamber cam having an internal space defined
by an inside surface and communicated to the inlet and outlet; a
rotor rotatably received within the internal space of the pressure
chamber cam, the rotor having a plurality of radial slots and a
plurality of vanes received and movable within respective radial
slots radially towards the inside surface of the pressure chamber
cam; and a drive shaft connected to the rotor for rotating the
rotor to cause the vanes to draw lubricant in from the inlet and
pressurize the lubricant for expelling out through the outlet; the
rotor having the radial slots thereof communicated to the
pressurized fluid to bias the vanes radially outward therefrom
using the fluid pressure; wherein, for at least one of the
plurality of vanes, a distance between an outer face of the at
least one vane and an inner face of its respective slot is greater
than distances between outer faces of the remaining vanes and inner
faces of their respective slots to facilitate radially outward
movement thereof towards the inside surface of the pressure chamber
cam by centrifugal force during initial start-up of the pump.
2. The vane pump according to claim 1, wherein at least one of the
plurality of vanes in the rotor has a lower thickness relative to
thicknesses of the remaining vanes to facilitate radially outward
movement thereof towards the inside surface of the pressure chamber
cam by centrifugal force during initial start-up of the pump.
3. The vane pump according to claim 1, wherein at least one of the
plurality of radial slots in the rotor has a higher width relative
to widths of other slots, such that the respective vane received
within the at least one radial slot of different width is
configured for radially outward movement towards the inside surface
of the pressure chamber cam by centrifugal force during initial
start-up of the pump.
4. The vane pump according to claim 2, wherein each of the
plurality of vanes has essentially the same radial length.
5. The vane pump according to claim 2, wherein each of the
plurality of vanes has essentially the same height.
6. The vane pump according to claim 2, wherein at least two of the
plurality of vanes in the rotor have the lower thickness relative
to the thicknesses of the remaining vanes to facilitate radially
outward movement towards the inside surface of the pressure chamber
cam by centrifugal force during the initial start-up of the
pump.
7. The vane pump according to claim 6, wherein the at least two
vanes have the same thickness.
8. The vane pump according to claim 2, wherein less than half of
the plurality of vanes in the rotor have the lower thickness
relative to the thicknesses of the remaining vanes, and wherein the
less than half of the plurality of vanes have the same
thickness.
9. The vane pump according to claim 3, wherein each of the
plurality of slots has essentially the same radial length.
10. The vane pump according to claim 3, wherein each of the
plurality of vanes has essentially the same thickness.
11. The vane pump according to claim 3, wherein at least two of the
plurality of slots in the rotor have the higher width relative to
widths of the other slots, such that the at least two vanes are
configured for radially outward movement towards the inside surface
of the pressure chamber cam by centrifugal force during initial
start-up of the pump.
12. The vane pump according to claim 11, wherein the at least two
slots have essentially the same width.
13. The vane pump according to claim 9, wherein less than half of
the plurality of slots in the rotor have a different width relative
to widths of the other slots, and wherein the less than half of the
plurality of slots have the same width.
14. The vane pump according to claim 1, further comprising a first
plate and a second plate provided on either side of the pressure
chamber cam, wherein the drive shaft extends through the first
plate and into the internal space of the pressure chamber cam.
15. The vane pump according to claim 14, wherein the drive shaft is
further connected to the second plate.
16. The vane pump according to claim 2, wherein the lower thickness
of the at least one of the plurality of vanes is between
approximately 0.02 mm and approximately 0.100 mm thinner than the
thicknesses of the remaining vanes.
17. The vane pump according to claim 3, wherein the higher width of
the at least one radial slot is between approximately 0.02 mm and
approximately 0.100 mm higher than the widths of the other
slots.
18. The vane pump according to claim 1, wherein the system is a
transmission or an engine.
19. A system comprising: an engine or a transmission, and a vane
pump, the vane pump comprising: an inlet for receiving fluid from a
source; an outlet for delivering pressurized fluid to the engine or
transmission; a pressure chamber cam having an internal space
defined by an inside surface and communicated to the inlet and
outlet; a rotor rotatably received within the internal space of the
pressure chamber cam, the rotor having a plurality of radial slots
and a plurality of vanes received and movable within respective
radial slots radially towards the inside surface of the pressure
chamber cam; and a drive shaft connected to the rotor for rotating
the rotor to cause the vanes to draw lubricant in from the inlet
and pressurize the lubricant for expelling out through the outlet;
the rotor having the radial slots thereof communicated to the
pressurized fluid to bias the vanes radially outward therefrom
using the fluid pressure; wherein, for at least one of the
plurality of vanes, a distance between an outer face of the at
least one vane and an inner face of its respective slot is greater
than distances between outer faces of the remaining vanes and inner
faces of their respective slots to facilitate radially outward
movement thereof towards the inside surface of the pressure chamber
cam by centrifugal force during initial start-up of the pump.
20. The system according to claim 19, wherein at least one of the
plurality of vanes in the rotor has a lower thickness relative to
thicknesses of the remaining vanes to facilitate radially outward
movement thereof towards the inside surface of the pressure chamber
cam by centrifugal force during initial start-up of the pump.
21. The system according to claim 19, wherein at least one of the
plurality of radial slots in the rotor has a higher width relative
to widths of other slots, such that the respective vane received
within the at least one radial slot of different width is
configured for radially outward movement towards the inside surface
of the pressure chamber cam by centrifugal force during initial
start-up of the pump.
Description
CROSS REFERENCE TO RELATED APPLICATION
[0001] This patent application claims priority to provisional
patent application 62/432,194 filed on Dec. 9, 2016, and is
incorporated by reference herein in its entirety.
BACKGROUND
Field
[0002] The present disclosure is generally related to a variable
displacement vane pump for providing pressurized fluid to a system.
The vane pump has at least one vane that is less restricted and is
configured to move within its slot before other vanes, for example,
at cold start.
Description of Related Art
[0003] Vane pumps are known for use for pumping fluids or
lubricants, such as oil, to internal combustion engines. The vanes
are mounted to a rotor and engage the inner surface of a pressure
chamber to generate a pressure differential to pump the fluid. Some
vane pumps include a small spring in each vane slot, which
increases cost and manufacturing complexity. It is also known to
feed some of the pressurized fluid to the slots to bias the vanes
using the pressure, thus avoiding the need for numerous small
springs.
[0004] However, at startup of a pump where pressure is used to bias
the vanes, the vanes are typically pushed inwardly towards the
drive axis into their respective slots in the rotor by the pressure
chamber, as there is no internal pressure to push the vanes
radially out against the cam. During a normal pump start in room
temperature oil (or warmer), the vanes are more easily displaced
due to the centrifugal force. At colder oil temperatures, however,
the viscosity of the oil increases. The thicker oil makes it more
difficult for the vanes to move radially when the centrifugal force
is applied, and thus the generation of pressure is delayed until
the speed is increased sufficiently to generate enough centrifugal
force to overcome the thick oil.
SUMMARY
[0005] It is an aspect of this disclosure to provide a vane pump
having an inlet for receiving fluid from a source, and an outlet
for delivering pressurized fluid to a system therefrom. A pressure
chamber cam is also provided in the pump and has an internal space
defined by an inside surface and communicated to the inlet and
outlet. A rotor is rotatably received within the internal space of
the pressure chamber cam and has a plurality of radial slots and a
plurality of vanes received and movable within respective radial
slots radially towards the inside surface of the pressure chamber
cam. A drive shaft of the pump is connected to the rotor for
rotating the rotor to cause the vanes to draw lubricant in from the
inlet and pressurize the lubricant for expelling out through the
outlet. The rotor has the radial slots thereof communicated to the
pressurized fluid to bias the vanes radially outward therefrom
using the fluid pressure. For at least one of the plurality of
vanes, a distance between an outer face of the at least one vane
and an inner face of its respective slot is greater than distances
between outer faces of the remaining vanes and inner faces of their
respective slots to facilitate radially outward movement thereof
towards the inside surface of the pressure chamber cam by
centrifugal force during initial start-up of the pump.
[0006] Another aspect of this disclosure includes a system having
the above-noted vane pump along with an engine or transmission.
[0007] Other aspects, features, and advantages of the present
disclosure will become apparent from the following detailed
description, the accompanying drawings, and the appended
claims.
BRIEF DESCRIPTION OF THE DRAWINGS
[0008] FIG. 1 is an isometric view of a case with a vane pump in
accordance with an embodiment of the present disclosure, assembled
in the case.
[0009] FIG. 2 is a sectional view of the vane pump of FIG. 1 taken
along line 2-2.
[0010] FIG. 3 is a top isometric view of parts of the vane pump in
the case of FIG. 1 in accordance with an embodiment.
[0011] FIG. 4 is a sectional view of the vane pump as shown in FIG.
3 taken along line 4-4.
[0012] FIG. 5 is a bottom isometric view of the parts of the vane
pump in accordance with an embodiment.
[0013] FIGS. 6A and 6B are a bottom isometric view and a bottom
view, respectively, of a cam, rotor, and cover plate of the vane
pump of FIGS. 3-5.
[0014] FIG. 7A is an isometric view of a bottom of the cover plate
in the vane pump as shown in FIG. 3.
[0015] FIGS. 7B and 7C are isometric views of a top and a bottom,
respectively, of the pressure plate in the vane pump of FIG. 3.
[0016] FIGS. 8A and 8B are detailed isometric and top views,
respectively, of the vanes in the slots of the rotor in accordance
with one embodiment of the present disclosure.
[0017] FIG. 9 is detailed view of the vanes in the slots of the
rotor in accordance with another embodiment of the present
disclosure.
[0018] FIG. 10 is a schematic diagram of a system in accordance
with an embodiment of the present disclosure.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)
[0019] Generally, this disclosure relates to providing at least one
less restricted vane (or looser vane) in a rotor of a vane pump. In
one embodiment, this disclosure is directed to a vane pump having
(at least) one thinner/narrower vane (in thickness or width) such
that it is less restricted within its slot--relative to the other
vanes--for easier displacement in its respective slot of the rotor.
In another embodiment, the slot of the rotor is wider to allow the
vane to move more loosely in its slot as compared to the movement
of other vanes within their respective slots. The less restricted
vane facilitates a cold start in highly viscous oil by allowing
easier radial displacement and thus earlier initial build-up of
pressure in the pump.
[0020] The less restricted vane concepts as disclosed herein may be
implemented in different types of vane pumps. For example, in one
embodiment, the pump may be a fixed displacement pump wherein the
relationship between the rotor and pressure chamber is fixed. Such
a fixed displacement pump may be configured to provide a maximum
flow rate and pressure based on a peak demand of the system. In
another embodiment, the pump may be a variable vane pump wherein
the relationship between the rotor and pressure chamber varies,
such as by using a cam ring. The variable vane pump may have a
multi-chamber design.
[0021] Pump 10 has a housing or case associated therewith. In one
embodiment, the pump 10 has its own separate housing 12, case, or
casing (which are used interchangeably herethroughout) for
enclosing its parts as shown in FIGS. 1-2. That is, the parts of
the pump 10 are contained within a structure, such that the housing
12 forms a self-contained device around working and/or moving parts
of the pump, and thus the pump 10 may be inserted, connected,
and/or secured to another part via housing 12. FIG. 1 is an
isometric view of a case, such as a transmission case, with a pump
assembly 10 (or pump) assembled therein in accordance with an
embodiment of the present disclosure. In another embodiment, the
parts of the pump 10 may be assembled and contained within an
opening or main chamber 55 (shown in FIG. 2) formed within another
case, housing, or part (e.g., of a transmission case); thus, the
opening or chamber 55 forms the volume within pump housing 12. One
or more O-rings may be provided to secure the pump 10 within the
housing 12. The housing or chamber 55 may have an inner bore, for
example, for receiving a pressure chamber cam ring 20 (also
referred to as simply a cam or a ring), a rotor 34 (or impeller),
and a drive shaft 18 of the pump assembly 10, as is known in the
art and described in some detail later. In other types of pump
devices, the cam or cam ring 20 may sometimes be referred to as a
slide or slide ring that is capable of sliding or moving, whereas
as in the pump described herein, the cam 20 is located or secured
in its position using pins 32.
[0022] The pump has an inlet 13 and an outlet 15, which are formed
via openings 17 and 19 (respectively) through wall(s) in the
housing 12, as shown in FIG. 2. The inlet 13 and outlet 15 of the
housing 12 may be provided at an angle relative to each other, in
one embodiment. In an embodiment, the inlet 13 and outlet 15 may be
disposed such that fluid or lubricant is input and output on
opposing radial sides of the rotational axis A of the rotor 34. The
pump inlet 13 receives fluid or inputs lubricant to be pumped
(typically oil in the automotive context) from a source 52 (see
FIG. 10) and into the housing 12. The pump outlet 15 is used for
discharging or delivering the pressurized fluid or lubricant to the
system 25, e.g., transmission or engine. (The terms "fluid" and
"lubricant" are used interchangeably throughout this disclosure and
not intended to limit this disclosure in any way.)
[0023] As known in the art, the pump has at least one intake or
inlet port 28 (e.g., see FIG. 7A, which shows two ports 28) for
intaking fluid (lubricant) to be pumped (e.g., from inlet 13 of
housing 12). The inlet 13 is used for delivering or communicating
fluid into a pressure chamber 55. Port(s) 28 communicate this fluid
to the pressure cam 20 or ring. The pump also has at least one
outlet port 30 (e.g., see FIGS. 4 and 7B) for discharging the fluid
from the pump (e.g., and then out of housing 12 via outlet 15). The
inlet port(s) 28 and outlet port(s) 30 may be diametrically opposed
to each other with regards to the rotational axis A. The inlet
port(s) 28 and outlet port(s) 30 each may have a substantially
polygonal or a substantially crescent shape, for example, within
the pump and may be formed through the same wall located on one
axial side or both axial sides of the housing (with regard to the
rotational axis A of the rotor 34). Further, pockets 30A and/or
pockets 30B may be provided in the pump to assist in fluid /
lubricant delivery and discharge. Such features are also described
and referenced later with regards to FIGS. 7A-7C. Generally, these
structures are conventional, and need not be described in detail.
The shape of the pump inlet and/or pump outlet is not intended to
be limiting. Other configurations may be used, such as differently
shaped or numbered ports, etc. Further, it should be understood
that more than one inlet or outlet may be provided (e.g., via
multiple ports).
[0024] FIGS. 3 and 4 illustrate parts of the exemplary vane pump 10
of FIG. 1 in greater detail. A first plate 22 and a second plate 24
define a pressure chamber of the pump 10. More specifically, the
first plate 22 and second plate 24 are disposed at opposite sides
of the pressure chamber (such that chamber(s) are disposed axially
therebetween) and in contact therewith. The first plate 22 includes
a central opening 19B, through which the drive shaft 18 may
optionally extend. The first plate 22 includes a flange or lip 23
that may be used for fastening the pump to an adjacent vehicle
component (e.g., transmission case 12, as shown in FIG. 1). Thus,
the shaft 18 may rotate along axis A (see FIG. 3) within the
central opening 19B of the first plate 22.
[0025] The drive shaft 18 is configured to be driven by a driver
(not shown) such that it rotates about axis A to drive the vane
pump 10. Such a driver may include a drive pulley, drive shaft,
engine crank, gear, or electric motor, for example. One or more
support bearings may support the drive shaft 18. As seen in FIG. 4,
for example, the drive shaft 18 extends through the first plate 22,
and into an internal receiving space 31 (shown in FIG. 6A) of the
chamber cam 20 (or cam ring). The drive shaft 18 may also connect
to or extend at least partially into a portion of the second plate
24. In one embodiment, the drive shaft 18 is configured to extend
through a central opening 19A of the second plate 24 along axis
A.
[0026] The pressure chamber cam ring 20 is designed to be received
or contained in the chamber 55 of the pump housing 12 such that it
is in fitted relationship therewith. Pins 32 (see FIGS. 6A and 6B)
may be inserted into or through openings, holes, or slots,
generally noted as 51 in the Figures, in surrounding wall(s) of the
cam ring 20 to connect with the first and second plates 22, 24. For
example, one end of the pins 32 may be provided in receiving
openings 32A (shown in FIG. 7A) or slots in (an inner surface of)
the first plate 22 while the opposite end of the pins 32 is
provided in openings or slots 32B in (an inner surface of) the
second plate 24. Pins 32 secure the cam ring 20 relative to the
plates 22, 24 and limit (e.g., rotational or sliding) movement of
the cam. The chamber cam ring 20 has passageways 21 (see also FIG.
5) for intaking or delivery of lubricant from the inlet of the pump
10. The passageways 21 may be positioned approximately 180 degrees
from each other (e.g., diametrically opposed), on either side of
the drive shaft 18. The passageways 21 may be formed via cut-out
portions in the cam ring 20, for example. The internal receiving
space 31 of the pressure chamber cam ring 20 is defined by an inner
wall having an inner surface 33. With the flanking of the plates
22, 24 on either side of the ring 20, the internal receiving space
31 defines at least one main pressure chamber for the
fluid/lubricant (or oil). Further, the space 31 defines a rotor
receiving space for receiving rotor 34 therein. The space 31 may
have a generally oblong configuration (see FIG. 6B) or ovular
configuration such that the rotor 34 may be disposed within the
main pressure chamber while still providing at least one pressure
chamber. (As described below, in the illustrated embodiment, there
may be two pressure chambers 35, 37 provided in space 31, with the
use of the rotor 34 therein.) This space 31 or volume in the
pressure chamber communicates with the pump inlet and outlet via
the inlet and outlet (or discharge) ports for drawing in oil,
lubricant, or another fluid under negative intake pressure
(suction) through the pump inlet, and expelling the same under
positive discharge pressure (pressurized) out the pump outlet. In
one embodiment, the outer wall(s) of the cam ring 20 may have a
substantially similar shape as the receiving space 31. In another
embodiment, the outer wall(s) of ring 20 may be one shape, e.g.,
circular, while the space 31 is another, e.g., oblong or ovular. In
an embodiment, the cam ring 20 may include one or more relief
portions 47 or cut-outs in its body or wall(s) at the discharge end
thereof, such as illustrated in FIGS. 6A-6B. These portions 47 may
be provided relative to the discharge end of the pressure chambers
35, 37 (i.e., near plate 24), and are generally understood to one
of skill in the art and thus not further described here.
[0027] The rotor 34 is positioned within the main pressure chamber
or, more specifically, in space 31 of the cam ring 20 such that a
clearance is formed between the rotor 34 and inner cam surface 33.
The rotor 34 (and its vanes 42, 44) may divide the internal
receiving space 31 or pressure chamber into a first chamber 35 and
a second chamber 37 as shown in FIGS. 6A and 6B. The first chamber
35 is formed on one side of the rotor 34 and the second chamber 37
is formed on another side and separated from the first chamber 35
by the rotor 34 (and vanes 42, 44). Each of the first and second
chambers are defined as a volume between the rotor 34 and the inner
cam surface 33 of the chamber which includes at least one intake
port 28 and at least one discharge or outlet port 30 in
communication therewith. Each of the first chamber 35 and second
chamber 37 are in fluid communication with at least one of
passageways 21 (see FIGS. 6A and 6B) of the cam ring 20 and one of
the inlet and discharge ports. Accordingly, each of the inlet
port(s) 28 is configured to be in fluid communication with one of
the chambers 35 or 37 of pressure chamber 55 to deliver lubricant
thereto (see also FIG. 6B). The first plate 22 and the second plate
24 further provide upper and lower boundaries of the first chamber
35 and second chamber 37.
[0028] The rotor 34 (or impeller) is rotatably mounted in the
housing 12 within the internal receiving space 31 of the pressure
chamber cam ring 20. The rotor 34 is configured for rotation within
and relative to the cam ring 20. The rotor 34 is positioned along a
central axis (axis A) that in the illustrated type of pump is
typically coaxial with a central axis of the chamber (and/or space
31). In other types of pumps, these axes may be eccentric. As
represented in FIG. 2, the rotor 34 is connected to the drive shaft
18 for rotation therewith. The rotor 34 includes an opening or
center slot 36 configured to receive the shaft 18. The drive shaft
18 may have one or more or a series of splines 39 (see FIGS. 2 and
4) and grooves (not shown) around its outer circumference for
cooperative engagement with corresponding grooves 38A and splines
38B (shown in FIGS. 6A and 6B, for example) provided in the center
slot 36 of the rotor 34, to drivingly couple the rotor 34 to the
shaft 18. For example, male splines 39 and female grooves of the
drive shaft 18 may engage with a set of female grooves 38A and male
splines 38B, respectively, which are disposed on an inner surface
of the slot 36, in order to drivingly couple the rotor 34 to the
drive shaft 18 for rotation about the axis A together. Of course,
it should be understood that this illustrated design of the drive
shaft and rotor is exemplary only, and not intended to be limiting.
Other designs and/or devices may be used to drivingly couple the
shaft 18 and rotor 34 together.
[0029] The rotor has a number of radial slots 40 and multiple vanes
42 and at least one less restricted vane 44 (described in detail
later) that are received and movable within the radial slots 40.
The vanes 42 and 44 are configured for radial movement, e.g.,
movement radially towards the inside surface 33 of the cam ring 20,
away from an end of the slot that is closest to axis A. Centrifugal
force may force the vane(s) 42, 44 radially outwardly at the
initial stage or startup of the pump to engage and/or maintain
engagement of distal end(s) of the vane(s) 42, 44 with the inside
or inner surface 33 of the cam ring 20 during rotation of the rotor
34. Pressurized fluid further forces the vanes outwardly and in
engagement with the chamber cam 20. The vanes 42, 44 extend across
the clearance of the chambers 35, 37 and are movable with respect
to their slots 40 to accommodate variances in the clearance. Thus,
the vane(s) 42, 44 can be sealingly engaged with the inner surface
33 of the cam ring 20 such that rotating the rotor 34 draws fluid
in through the pump inlet by negative intake pressure and outputs
the fluid out through the outlet by positive discharge pressure.
Generally, this type of mounting and functionality of the pump is
conventional and well known, and need not be detailed further.
[0030] As the vanes 42, 44 are moved radially outwardly and in
contact with the inner surface 33 of the cam ring 20, the chambers
35, 37 are divided into compartments that receive lubricant.
[0031] During operation, the drive shaft 18 rotates the rotor 34 so
that the vanes 42, 44 are rotated within the cam ring 20. The
housing 12 and inlet 13 draw the lubricant into the chamber 55
through inlets 28 and the passageways 21 and then into compartments
of each of the chambers 35, 37, for pressurization. As the rotor 34
continues rotating, the vanes 42, 44 move the pressurized lubricant
to a distal side or end of the corresponding chamber (e.g., a side
that is approximately 90 degrees relative to passageway 21) to
discharge pressurized lubricant from the pressure chamber via a
corresponding discharge port(s). Additionally, as described later
below, while the rotor 34 rotates and lubricant enters the pump 10
via its inlet and exits via its outlets, centrifugal force and
hydraulic pressure up through back pressure ports 50 may push the
vanes 42, 44 radially towards the inner surface 33 of the pressure
chamber 20 (and thus towards the walls of the cam 20 (and the
housing 12)). The lubricant exits through the discharge ports and
outlet(s) of the pump (described below), to and through outlet
15.
[0032] FIG. 7A illustrates an inner face, underside, or inner side
(i.e., the side that faces chamber 20) of the first plate 22 in
accordance with an embodiment. The first plate 22 is a cover plate,
for example, and helps define the pressure chamber(s) 35, 37 within
the pump 10. The first plate 22 may be secured to the second plate
24. The first plate 22 includes central opening 19B for receipt of
at least a portion of the drive shaft 18, thus centering the first
plate 22 on axis A. Optionally, the drive shaft 18 may extend
through the opening 19B. The inner face of the first plate 22 faces
the chamber and thus the pressure chambers, rotor 34, and vanes 42,
44. The first plate 22 may be rotationally fixed to the chamber via
flanges (not shown) or O-rings, for example.
[0033] The first plate 22 also includes inner depressions 48A (or
inner portings), inlet ports 28, and pockets 30A (which may also be
referred to as ports) on its inner face or underside. When the pump
is assembled and operating, the pockets 30A of the pump intake or
receive lubricant from the chamber(s) 35, 37 to fluidly communicate
with and deliver output pressurized lubricant through the outlets
30, and thus may also be referred to as discharge ports or
"discharge pockets" 30A. The inlet ports 28 and discharge pockets
30A may be recesses formed in the first plate 22, with the inlet
ports 28 being diametrically opposed to each other (with regards to
axis A). The pockets 30A may also be diametrically opposed to each
other (with reference to axis A). The pockets 30A may be formed
between or about or at 180 degrees relative to each other and about
90 degrees relative to the inlet ports 28, as shown in FIG. 7A. The
discharge pockets 30A and outlet ports 30 are fluidly connected
(e.g., see FIG. 4) and configured to discharge fluid or lubricant
via outlet 15 (see FIG. 2) to outside the housing 12. The inner
depressions 48A of first plate 22 are also recessed portions that
are provided adjacent to the central opening 19B and at least
partially surround the opening 19B. Although two depressions 48A
are shown in FIG. 7A, the number and shape of the depressions 48A
is not intended to be limited. In an embodiment, each inner
depression 48A has an arcuate shape. In one embodiment, the inner
depressions 48A substantially surround the central opening 19B. The
depressions 48A may be positioned or spaced circumferentially
around the central opening 19B, for example. Fluid pressure
build-up in these inner depressions 48A--as a result of receiving
fluid from back pressure ports 50--causes action (i.e., fluid
pressure) on the vanes 42, 44 to thereby deliver pressurized fluid
to the rotor slots to push the vanes outwardly (away from the
central axis A) and keep the vanes 42, 44 in contact with the inner
surface 33 of the pressure chamber cam ring 20. The first plate 22
also includes receiving openings or cut-outs for receipt of first
ends of pins 32.
[0034] FIG. 7B illustrates an inner face or inner side (i.e., the
side that faces the pressure chambers) of the second plate 24 in
accordance with an embodiment. FIG. 7C illustrates an outer or
bottom side (the opposite side) of the second plate 24 of FIG. 7B.
The second plate 24 is a pressure plate that defines the pressure
chamber(s) 35, 37 within the pump 10. During operation, pressure is
applied on an outer surface (bottom) of the second plate 24, due to
fluid pressure build up, to compress the second plate 24 towards
and together with the pressure chamber and to minimize leakage
paths (further described below). The second plate 24 can also be
bolted or secured to the first plate 22 (e.g., via pins 32 at in
walls of the chamber), and may include receiving openings or
cut-outs for receipt of second ends of pins 32. As previously
noted, in one embodiment, the second plate 24 includes central
opening 19A for receipt of at least a portion of the drive shaft
18, thus centering the second plate 24 on axis A. Optionally, the
drive shaft 18 may extend through the opening 19A. The inner face
of the second plate 24 faces the main chamber 55 and thus the
pressure chambers 35, 37, rotor 34, and vanes 42, 44. The second
plate 24 may be rotationally fixed to the chamber 55 via flanges
(not shown) or O-rings, for example.
[0035] The second plate 24 also includes inner depressions 48B (or
inner portings), back pressure ports 50, outlet ports 30, and ports
or pockets 30B (also referred to as delivery ports or delivery
pockets) on its inner face or inner side. When the pump is
assembled and operating, the pockets 30B of the pump receive
lubricant from the inlet 13 to fluidly communicate with and deliver
lubricant into the pressure chamber (or chambers 35, 37), and thus
may also be referred to as inlet ports or pockets 30B. The pockets
30B may be recesses formed in the second plate 24 that are
diametrically opposed to each other (with reference to axis A). The
outlet ports 30 are openings or holes that extend through the
thickness of the second plate 24 (see bottom view in FIG. 7B and
FIG. 4) and are used to output lubricant from the chamber(s)
towards the outlet 15. In an embodiment, the outlet ports 30 allow
fluid to flow from the first chamber 35 and/or second chamber 37 to
a single outlet path of the pump. The outlet ports 30 may also be
diametrically opposed to each other (with reference to axis A). The
pockets 30B may be formed between or at or about 180 degrees
relative to each other and about 90 degrees relative to the outlet
ports 30, as shown in FIG. 7B. The inner depressions 48B are also
recessed portions that are provided adjacent to the central opening
19A and at least partially surround the opening 19A. Although two
depressions 48B are shown in FIG. 7B, the number and shape of the
depressions 48A is not intended to be limited. In an embodiment,
each inner depression 48B has an arcuate shape. The back pressure
ports 50 are provided between the inner depressions 48B, also
around and partially surrounding the central opening 19A. Although
two ports 50 are shown in FIG. 7B, the number and shape of the back
pressure ports 50 is not intended to be limited. The back pressure
ports 50 are openings or holes that extend through the thickness of
the second plate 24. In one embodiment, the inner depressions 48B
and back pressure ports substantially surround the central opening
19A. The depressions 48B and ports 50 may be positioned or spaced
circumferentially around the central opening 19A, for example. The
back pressure ports 50 may be referred to as vane pressurizing
ports. When pressurized fluid builds up under or below the second
plate 24 (e.g., in a lower portion of housing 12), the pressurized
fluid may be received through the back pressure ports 50 to
pressurize the vanes (previously noted above). Pressurized fluid
may be directed from ports 50 and partially contained in the inner
depressions 48B. Fluid pressure build-up in these inner depressions
48B causes action (i.e., pressure) on the vanes 42, 44 to thereby
deliver pressurized fluid to the rotor slots to push the vanes
outwardly (away from the central axis A) and keep the vanes 42, 44
in contact with the inner surface 33 of the pressure chamber cam
ring 20. Generally, such features are known and thus are not
further described herein.
[0036] In addition to the above described features, which are
generally understood by those of ordinary skill in the art, the
rotor 34 of the disclosed pump assembly 10 includes at least one
less restricted vane 44 therein, in addition to the remaining/other
vanes 42. The less restricted vane(s) 44 is designed to move within
its slot 40 before the other vanes 42. In accordance with one
embodiment, for example, a distance (D) between an outer face of
the at least one vane 44 and an inner face of its respective slot
is greater than distances/standard clearances between the remaining
vanes and inner sides of their respective slots, to facilitate
radially outward movement of the vane 44 towards the inside surface
33 of the pressure chamber by centrifugal force during initial
start-up of the pump, before the radial outward movement of vanes
42 towards inside surface 33. FIGS. 8A and 8B illustrate exemplary
details of one embodiment of employing a less restricted vane 44
that has a different thickness relative to thicknesses of the other
vanes 42, thus providing a greater distance D (see FIG. 9 for
example of location of D) between vane 44 and the inside surface of
its slot 40, while the remaining vanes 42 have a standard clearance
C. That is, the less restricted vane 44 has a lower thickness than
the remaining vanes 42. For illustrative purposes only, the
distance D and clearance C are shown as being on either side of the
vanes 44 and 42 (respectively) in the Figure. However, it should be
understood that the distance or clearance on either side of the
vanes 44, 42 may vary slightly, e.g., as the vanes move
therein.
[0037] In an embodiment, each of the slots 40 have an essentially
similar width W.sub.S, height, and length L.sub.S (see FIG. 8A).
Each of the vanes 42 and 44 provided in the rotor 34 have a radial
length L (defined as a measurement between a proximal end of the
vane that is near the axis A and an opposite end near the inner
surface 33) and height H (defined as a measurement between a bottom
end of the vane adjacent to the second plate 24 and a top end of
the vane adjacent to the first plate 22). In one embodiment, each
of the vanes 42, 44 has substantially similar radial length L. In
another embodiment, each of the vanes has a substantially similar
height H. In yet another embodiment, each of the vanes 42, 44 have
both substantially similar length L and height H.
[0038] Each of the vanes 42 and 44 also has a thickness, also
referred to herein as a width (defined as a measurement between
each major side of the vane that is positioned between walls of the
slot 40). For example, in accordance with an embodiment, each of
the vanes 42 has a thickness W1, and less restricted vane 44 has a
thickness W2, as shown in FIG. 8. In accordance with one
embodiment, W2<W1, such that less restricted vane 44 (W2) is
thinner or of a reduced thickness/width as compared to the
thickness or widths (W1) of vanes 42. For example, the difference
in widths (W1-W2) may be between approximately 0.020 to
approximately 0.100 millimeters (mm), both inclusive, in accordance
with an embodiment. In one embodiment, the difference in widths
(W1-W2) may be between approximately 0.020 to approximately 0.050
millimeters (mm), both inclusive. In another embodiment, the lower
thickness W2 of vane 44 is approximately less than or equal to
approximately 0.100 mm thinner than the thicknesses of the
remaining vanes 42. Accordingly, this reduced thickness allows the
less restricted vane 44 to displace within its respective slot 40
radially towards the inside surface 33 of the cam ring 20 before
the other vanes 42 move within their slots 40 (such as during cold
start). In such a case, i.e., where vanes 42 and less restricted
vane 44 have different widths, the dimensions (e.g., W.sub.S,
height, and length L.sub.S) of the slots receiving the vanes 42, 44
therein may remain the same.
[0039] In accordance with an embodiment, the width (or thickness)
of the less restricted vane(s) 44 is less than or equal to
approximately 0.100 mm thinner than the width (or thickness) of the
other vanes 42. In accordance with another embodiment, the width
(or thickness) of the less restricted vane(s) 44 is less than or
equal to approximately 0.050 mm thinner than the width (or
thickness) of the other vanes 42. In yet another embodiment, the
width (or thickness) of the less restricted vane(s) 44 is
approximately 0.020 mm thinner than the width (or thickness) of the
other vanes 42. The width of the vane(s) 44 is not equal to the
width of vanes 42. It should be understood by one of ordinary skill
in the art that the difference in thickness or width of the at
least one less restricted vane 44 (or a slot 41, as described in an
embodiment later) is designed such that the moving distance of the
less restricted vane 44 (or D*2 in slot 41) in its respective slot
is greater than mere inconsequential differences that may be caused
due to manufacturing tolerances. Generally, the manufacturing
tolerance range may also be, for example, approximately 0.020-0.060
mm.
[0040] Using the example ranges above, in one embodiment, the width
W1 of the vanes 42 may be approximately 1.0 mm to approximately 2.0
mm (inclusive), and the width W2 of the at least one less
restricted vane 44 may be approximately 0.90 mm to approximately
1.98 mm (inclusive), while still providing a difference between
approximately 0.020 to approximately 0.100 millimeters (mm) as
compared to W1. In another embodiment, the width W1 of the vanes 42
may be approximately 1.0 mm to approximately 2.0 mm (inclusive),
and the width W2 of the at least one less restricted vane 44 may be
approximately 0.95 mm to approximately 1.98 mm (inclusive), while
still providing a difference between approximately 0.020 to
approximately 0.050 millimeters (mm) as compared to W1. In yet
another embodiment, the width W1 of the vanes 42 may be
approximately 1.0 mm to approximately 2.0 mm (inclusive), while the
width W2 of the at least one less restricted vane 44 may be
approximately 0.9 mm to approximately 1.9 mm (inclusive). In still
yet another embodiment, the width W1 of the vanes 42 may be
approximately 1.0 mm, while the width W2 of the at least one less
restricted vane 44 may be approximately 0.9 mm.
[0041] The method for forming the less restricted/loose/narrower
vane as described with reference to FIG. 8 above is not intended to
be limited. Such a less restricted vane (like vane 44) may be
formed (e.g., molded or cast) to a different thickness or width, in
accordance with one embodiment. In another embodiment, an existing
vane (like vane 42) may be altered or machined by a machining
process or tool, for example, i.e., carving or shaving off a
desired thickness to reduce its width.
[0042] In accordance with another embodiment, at least two less
restricted vanes 44 of a different thickness or width W2 are
provided in the rotor 34, while the remaining vanes 42 in the rotor
34 have similar thickness W1. In yet another embodiment, less than
half of the vanes in the rotor 34 are less restricted vanes 44 that
have a different thickness or width W2 relative to widths W1 of the
remaining vanes 42. In an embodiment, the less than half of the
less restricted vanes 44 have the same thickness.
[0043] FIG. 9 illustrates another embodiment of employing a less
restricted vane in the pump assembly 10, wherein at least one
radial slot (referred to as slot 41) of the slots 40 in the rotor
34 has a different width relative to widths of the other slots.
Each of the vanes 42 provided in the slots 40 and 41 has similar or
the same width, i.e., vane width W. The width of slot 41 may be
altered by a machining process or tool, for example. In some cases,
existing or prefabricated rotors may be used to form such a radial
slot 41. In this illustrative embodiment, it is the width of the
slot 41 that changes the distance D relating to the slot for the
less restricted vane as compared to the standard clearance C or
width of slots 40 for vanes 42, while the other dimensions remain
substantially the same. For example, each of the slots 40 and 41
provided in the rotor 34 have a radial length (like L as shown in
FIG. 8A) (defined as a measurement between an end of the opening
within the rotor 34 that is near the axis A and an opposite end at
an outer surface of the rotor 34) and height (like H as shown in
FIG. 8A) (defined as a measurement between a top end of the opening
at the top surface of the rotor 34 and a bottom end of opening at
the bottom surface of the rotor 34). In one embodiment, each of the
slots 40, 41 has substantially similar radial length. In another
embodiment, each of the slots has a substantially similar height.
In yet another embodiment, each of the slots 40, 41 have both
substantially similar length and height.
[0044] Each of the slots 40 has a width W.sub.S. The width of a
slot in the rotor 34 may be defined as a measurement between the
walls defining the slot opening, that are configured to receive a
vane therebetween or therein. Width W.sub.S may be defined as W+C
or, as shown in FIG. 9, W+C*2. In accordance with an embodiment,
slot 41 may have a width W.sub.S1 that is different than the widths
W.sub.S of the slots 40. Width W.sub.S1 may be defined as W+D or,
as shown in FIG. 9, W+D*2. In accordance with one embodiment,
W.sub.S1>W.sub.S, such that the slot 41 is wider than the other
slots 40. That is, as shown in FIG. 9, W.sub.S and W.sub.S1 are not
equal and W.sub.S is less than W.sub.S1. Accordingly, the vane 42
positioned within the slot 41 as shown in FIG. 9 may be referred to
as a less restricted vane or loose vane, because such a vane
received within the slot 41 is configured for radial displacement
towards the inside surface 33 of the cam ring 20 before radial
movement of the other vanes 42 within the other slots 40, since the
associated slot 41 itself is larger (in width). This is because the
distance D between an outer face of the at least one vane 42
contained in the slot 41 and an inner face of its respective slot
is greater than a distance designed for a standard clearance C for
each [remaining] vane 42. (Thus, clearance C is less than distance
D.)
[0045] Of course, it should again be noted and understood that the
clearance C on either side of vane 42 and distance D on either side
of the less restricted vane as depicted in FIG. 9 are not intended
to be limited with regards to the referenced spacing being equal or
consistent, such that the vane 42 and/or less restricted vane is
continually equidistant relative to the inner side of its
respective slot. Rather, one of ordinary skill in the art will
understand the fluid nature of the vanes within their slots (e.g.,
in the lateral direction, or towards and away from the inner sides
or walls of its slot) based on the receipt of fluid in the
chamber(s).
[0046] For example, in one embodiment, the difference in widths
(W.sub.S1-W.sub.S) may be between approximately 0.020 to
approximately 0.100 millimeters (mm), both inclusive, in accordance
with an embodiment (i.e., width W.sub.S1 of slot 41 is between
approximately 0.02 mm and approximately 0.100 mm higher than the
widths of the other slots 40 of width W.sub.S). In one embodiment,
the difference in widths (W.sub.S1-W.sub.S) may be between
approximately 0.020 to approximately 0.050 millimeters (mm), both
inclusive. In another embodiment, the width W.sub.S of slot 40 in
FIG. 9 is approximately less than or equal to approximately 0.100
mm thinner than the width W.sub.S1 of the at least one slot 41.
Accordingly, this larger width W.sub.S1 of slot 41 allows the less
restricted vane 42 therein to displace within slot 41 towards the
inside surface 33 of the cam ring 20 before the other vanes 42 in
slots 40 move within their respective slots 40 (such as during cold
start). In such a case, each of the vanes 42 provided in rotor 34
of the illustrated embodiment of FIG. 9 have a substantially
similar thickness W, height (H), and length (L).
[0047] In accordance with an embodiment, the width W.sub.S1 of the
slot(s) 41 is at least approximately 0.020 mm greater in width as
compared to width W.sub.S. of the other slots 40. In accordance
with another embodiment, the width W.sub.S1 of the slot(s) 41 is at
least approximately 0.050 mm greater in width as compared to width
W.sub.S. of the other slots 40. In yet another embodiment, the
width W.sub.S1 of the slot(s) 41 is at least approximately 0.100 mm
greater in width as compared to width W.sub.S. of the other slots
40. In an embodiment, the width W.sub.S1 of the slot(s) 41 is not
more than approximately 0.25 mm greater in width as compared to
width W of the vanes 42. In another embodiment, the width W.sub.S1
of the slot(s) 41 is not more than approximately 0.15 mm greater in
width as compared to width W of the vanes 42. It should be
understood by one of ordinary skill in the art that the difference
in width of the at least one slot 41 is designed such that the
total distance D*2 of the slot 41 is greater than mere
inconsequential differences that may be caused due to manufacturing
tolerances. Generally, the manufacturing tolerance range may also
be, for example, approximately 0.020-0.060 mm.
[0048] In an embodiment, the distance D for the less restricted
vane in slot 41 may be between approximately 0.050 mm and
approximately 0.100 mm per side (inclusive), while the spacing or
normal clearance C between the outside surface of each vane 42 and
its slot surface (in slot 40) may be between approximately 0.010 mm
and approximately 0.025 mm per side (inclusive). In one embodiment,
the width W of the vanes 42 may be approximately 1.0 mm to
approximately 2.0 mm (inclusive). Thus, based on the examples above
for C and D, then, in accordance with one embodiment, a width
W.sub.S1 of slot 41 may be between W+approximately 0.1 mm and
W+approximately 0.2 mm (inclusive) (i.e., W+D*2), and a width of
slot(s) 40 may be between W+approximately 0.02 mm and
W+approximately 0.05 mm (inclusive) (i.e., W+C*2).
[0049] In another embodiment, the distance D for the less
restricted vane in slot 41 may be between approximately 0.0175 mm
and approximately 0.100 mm per side (inclusive), while the spacing
or normal clearance C between the outside surface of each vane 42
and its slot surface (in slot 40) may be between approximately
0.005 mm and approximately 0.05 mm per side (inclusive).
[0050] In yet another embodiment, the total distance (D*2) between
the outside surfaces of the less restricted vane and surfaces in
slot 41 may be between approximately 0.050 mm and approximately
0.100 mm (inclusive), while the total spacing or normal clearance
(C*2) between the outside surfaces of each vane 42 and its slot
surface (in slot 40) may be between approximately 0.010 mm and
approximately 0.025 mm per side (inclusive).
[0051] In an embodiment, the total clearance (C*2) for the vanes in
the slots 40 may be between approximately 15 micron and
approximately 100 micron (inclusive). Thus, if the width W of the
vanes 42 may be approximately 1.0 mm to approximately 2.0 mm
(inclusive), the widths W.sub.S of the slots 40 may be between
approximately 1.015 mm and approximately 2.1 mm (inclusive), in
accordance with an embodiment. Further, in such an embodiment, the
width W.sub.S1 of the at least one slot 41 may be approximately 35
micron and approximately 200 micron (inclusive) larger than the
width W.sub.S, i.e., width(s) W.sub.S1 of the slot(s) 41 may be
between approximately 1.035 mm and approximately 2.2 mm
(inclusive).
[0052] In another embodiment, the distances D for the vanes in the
slot 41may be between approximately 20 micron and approximately 100
micron (inclusive) larger than total clearance (C*2), i.e., total
distance (D*2) on either side of vane 41 is approximately 40 micron
to approximately 200 micron. That is, in an embodiment wherein the
width W of the vanes 42 may be approximately 1.0 mm to
approximately 2.0 mm (inclusive), the width W.sub.S1 of the at
least one slot 41 may be between approximately 1.040 mm and
approximately 2.2 mm (inclusive), while the widths W.sub.S of the
slots 40 may be between approximately 1.015 mm and approximately
2.1 mm (inclusive), wherein the widths W.sub.S of the slots 40 are
at least 10 micron smaller than the width W.sub.S1 of the slot(s)
41.
[0053] In yet another embodiment, a width W.sub.S1 of slot 41 may
be between W+approximately 0.017 mm and W+approximately 0.2 mm
(inclusive) (W+D*2), and a width W.sub.S of slot(s) 40 may be
between W+approximately 0.015 mm and W+approximately 0.1 mm
(inclusive) (W+C*2), wherein W.sub.S and W.sub.S1 are not equal and
W.sub.S is less than W.sub.S1.
[0054] In yet another embodiment, a width W.sub.S1 of slot 41 may
be between W+approximately 0.035 mm and W+approximately 0.2 mm
(inclusive) (W+D*2), and a width W.sub.S of slot(s) 40 may be
between W+approximately 0.015 mm and W+approximately 0.1 mm
(inclusive) (W+C*2), wherein W.sub.S and W.sub.S1 are not equal and
W.sub.S is less than W.sub.S1.
[0055] In still yet another embodiment, a width W.sub.S1 of slot 41
may be between W+approximately 0.05 mm (50 micron) and
W+approximately 0.1 mm (100 micron) (inclusive) (W+D*2), and a
width W.sub.S of slot(s) 40 may be between W+approximately 0.02 mm
and W+approximately 0.9 mm (inclusive) (W+C*2), wherein W.sub.S and
W.sub.S1 are not equal and W.sub.S is less than W.sub.S1.
[0056] In yet another embodiment, the width W.sub.S1 of the at
least one slot 41 may be between approximately 0.02 mm and
approximately 0.100 mm higher than the width W.sub.S of the other
remaining slots 40.
[0057] Further in accordance with an embodiment, the widths W.sub.S
of the slots 40 are between approximately 10 micron to
approximately 200 micron smaller than the width W.sub.S1 of the
slot(s) 41.
[0058] In an embodiment, each of the vanes 42 provided in rotor 34
of the illustrated embodiment of FIG. 9 may have a substantially
similar thickness W, height (H), and length (L), with
W.sub.S1>W.sub.S.
[0059] In accordance with another embodiment, at least two slots 41
of a different width are provided in the rotor 34, while the
remaining slots 40 in the rotor 34 have similar width. In yet
another embodiment, less than half of the slots 41 in the rotor 34
are of a different width (providing less than half of vanes that
are less restricted vanes) as compared to the widths of the other
slots 40. In an embodiment, these less than half of slots 41 have
the same width.
[0060] Although not explicitly detailed above, each of the
exemplary embodiments and ranges noted with respect to the widths
W.sub.S1, W.sub.S of the slot(s) 41, 40 noted above could also be
similarly applied with regards to the thicknesses/widths W1, W2 of
the vanes 42, 44 described with respect to FIG. 8.
[0061] As previously mentioned, use of at least one less restricted
vane in a rotor 34 in a pump assembly 10 as herein disclosed and
described facilitates cold start of the pump in highly viscous oil
by allowing easier radial displacement of the vane by centrifugal
force for initially moving oil and pressurizing the fluid, and thus
earlier initial build-up of pressure within the outlet of the pump,
and hence in the inner porting or depressions. The use of a less
restricted vane reduces the required amount of oil shear (breakdown
of its viscosity) at colder temperatures, thereby faster delivery
of the oil/fluid to the pressure chamber(s). The pressure in the
inner porting/depressions thereafter acts on the vanes to keep the
vanes in constant contact with the inner face of the pressure
chamber(s).
[0062] Additional parts may also be provided along with pump 10
and/or its housing 12. For example, as previously noted with
reference to FIG. 1, the pump assembly 10 may include a number of
O-rings for sealing engagement within the housing 12 or another
vehicle part. The pump 10, its housing 12, and/or parts thereof
(e.g., first and second plates 22, 24) may include grooves (not
shown) along an inner or outer periphery thereof for receipt and
installation of the O-rings.
[0063] FIG. 10 is a schematic diagram of a system 25 in accordance
with an embodiment of the present disclosure. The system 25 can be
a vehicle or part of a vehicle, for example. The system 25 includes
a mechanical system such as an engine 56 (e.g., internal combustion
engine) and/or a transmission (e.g., represented with case 12 in
FIG. 1) of an automotive vehicle for receiving pressurized
lubricant from the pump 10. The pump 10 receives (input via pump
inlet) lubricant (e.g., oil) from a lubricant source 52 and
pressurizes and delivers it to the engine 56 (output via outlet). A
sump or tank 58 may be the lubricant source 52 that inlets to the
pump 10. A controller 54 may be designed for implementing actuation
of the system 25 and/or pump 10.
[0064] While the principles of the disclosure have been made clear
in the illustrative embodiments set forth above, it will be
apparent to those skilled in the art that various modifications may
be made to the structure, arrangement, proportion, elements,
materials, and components used in the practice of the
disclosure.
[0065] It will thus be seen that the features of this disclosure
have been fully and effectively accomplished. It will be realized,
however, that the foregoing preferred specific embodiments have
been shown and described for the purpose of illustrating the
functional and structural principles of this disclosure and are
subject to change without departure from such principles.
Therefore, this disclosure includes all modifications encompassed
within the spirit and scope of the following claims.
* * * * *