U.S. patent application number 15/758161 was filed with the patent office on 2018-09-06 for cartridge vane pump.
This patent application is currently assigned to KYB Corporation. The applicant listed for this patent is KYB CORPORATION. Invention is credited to Yoshiyuki MAKI, Tomoyuki NAKAGAWA, Masamichi SUGIHARA, Koji YOSHIMURA.
Application Number | 20180252212 15/758161 |
Document ID | / |
Family ID | 58289233 |
Filed Date | 2018-09-06 |
United States Patent
Application |
20180252212 |
Kind Code |
A1 |
MAKI; Yoshiyuki ; et
al. |
September 6, 2018 |
CARTRIDGE VANE PUMP
Abstract
A cartridge vane pump includes: a body-side side plate that is
brought into contact with end surfaces of a rotor and a cam ring;
first and second discharge ports that are formed in the body-side
side plate; and an adapter that is formed with first and second
connection channels for connecting the first and second discharge
ports formed in the body-side side plate and first and second
discharge channels formed in a body.
Inventors: |
MAKI; Yoshiyuki; (Aichi,
JP) ; SUGIHARA; Masamichi; (Gifu, JP) ;
NAKAGAWA; Tomoyuki; (Gifu, JP) ; YOSHIMURA; Koji;
(Gifu, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
KYB CORPORATION |
Tokyo |
|
JP |
|
|
Assignee: |
KYB Corporation
Tokyo
JP
|
Family ID: |
58289233 |
Appl. No.: |
15/758161 |
Filed: |
September 8, 2016 |
PCT Filed: |
September 8, 2016 |
PCT NO: |
PCT/JP2016/076378 |
371 Date: |
March 7, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04C 2240/10 20130101;
F04C 2/3446 20130101; F04C 15/00 20130101; F04C 2250/102 20130101;
F05B 2250/502 20130101; F04C 2/344 20130101; F05B 2280/1021
20130101; F04C 15/06 20130101; F04C 2240/20 20130101; F04C 15/0023
20130101 |
International
Class: |
F04C 2/344 20060101
F04C002/344; F04C 15/06 20060101 F04C015/06 |
Foreign Application Data
Date |
Code |
Application Number |
Sep 18, 2015 |
JP |
2015-185584 |
Claims
1. A cartridge vane pump accommodated in a body of fluid pressure
device in an attachable and detachable manner, the cartridge vane
pump comprising: a rotor linked to a driving shaft, the rotor being
configured to be rotationally driven; a plurality of slits formed
in a radiating pattern so as to have opening portions at an outer
circumference of the rotor; vanes respectively inserted into the
slits in a freely slidable manner; a cam ring configured to have an
inner circumference cam face with which tip end portions of the
vanes are brought into sliding contact; pump chambers defined
between the rotor, the cam ring, and the adjacent vanes; a cover
member brought into contact with one end surfaces of the rotor and
the cam ring, the cover member being fixed to the body; a side
plate brought into contact with other end surfaces of the rotor and
the cam ring; a discharge port formed in the side plate, the
discharge port being configured such that working fluid discharged
from the pump chambers is guided thereinto; and an adapter formed
with a connection channel for connecting the discharge port formed
in the side plate and a discharge channel formed in the body.
2. The cartridge vane pump according to claim 1, further comprising
a biasing member configured to constantly bias the side plate
towards the rotor.
3. The cartridge vane pump according to claim 2, wherein the
biasing member is a seal member provided between the adapter and
the side plate in a compressed state, the biasing member being the
seal member configured to surround and seal an outer circumference
of the discharge port formed in the side plate.
4. The cartridge vane pump according to claim 1, wherein in a state
in which the cartridge vane pump is accommodated in the body, the
adapter defines, with a bottom surface of the body, a ring-shaped
high-pressure chamber into which high-pressure working fluid that
has been discharged from the pump chambers is guided, the adapter
being configured to bias the side plate towards the rotor by the
high-pressure working fluid that has been guided to the
high-pressure chamber.
5. The cartridge vane pump according to claim 1, wherein the side
plate is formed of a sintered metal, and the adapter is formed of
an aluminum alloy.
Description
TECHNICAL FIELD
[0001] The present invention relates to a cartridge vane pump.
BACKGROUND ART
[0002] JP2003-301781A discloses a cartridge vane pump that is
configured so as to be attachable and detachable to/from a main
body portion to be fixed to a base, a frame, and so forth.
SUMMARY OF INVENTION
[0003] In order to install such a cartridge vane pump to a fluid
pressure device, a side plate needs to be formed such that a
position and a shape of a discharge port provided in the side plate
are adapted to a discharge channel provided in the fluid pressure
device. However, the side plate is formed by using a material
having a superior durability because it slides with a rotor.
Because such a material have a poor processability and incurs a
high cost, there is a risk in that the cost is increased by forming
the side plate so as to be respectively adapted to the fluid
pressure devices with different discharge channels.
[0004] An object of the present invention is to provide a cartridge
vane pump that is capable of adapting a discharge port of a side
plate to a discharge channel of a fluid pressure device, and at the
same time, that is capable of achieving reduction in cost.
[0005] According to one aspect of the present invention, a
cartridge vane pump is accommodated in a body of fluid pressure
device in an attachable and detachable manner. The cartridge vane
pump includes: a rotor linked to a driving shaft, the rotor being
configured to be rotationally driven; a plurality of slits formed
in a radiating pattern so as to have opening portions at an outer
circumference of the rotor; vanes respectively inserted into the
slits in a freely slidable manner; a cam ring configured to have an
inner circumference cam face with which tip end portions of the
vanes are brought into sliding contact; pump chambers defined
between the rotor, the cam ring, and the adjacent vanes; a cover
member brought into contact with one end surfaces of the rotor and
the cam ring, the cover member being fixed to the body; a side
plate brought into contact with other end surfaces of the rotor and
the cam ring; a discharge port formed in the side plate, the
discharge port being configured such that working fluid discharged
from the pump chambers is guided thereinto; and an adapter formed
with a connection channel for connecting the discharge port formed
in the side plate and a discharge channel formed in the body.
BRIEF DESCRIPTION OF DRAWINGS
[0006] FIG. 1 is a front view of a cartridge vane pump according to
an embodiment of the present invention.
[0007] FIG. 2 is an exploded perspective view of the cartridge vane
pump according to the embodiment of the present invention viewed
from the cover member side.
[0008] FIG. 3 is an exploded perspective view of the cartridge vane
pump according to the embodiment of the present invention viewed
from the adapter side.
[0009] FIG. 4 is a sectional view of the cartridge vane pump
according to the embodiment of the present invention in the axial
direction.
[0010] FIG. 5 is an enlarged view of a fastening member of the
cartridge vane pump according to the embodiment of the present
invention.
[0011] FIG. 6 is a plan view of the adapter of the cartridge vane
pump according to the embodiment of the present invention.
[0012] FIG. 7 is a rear view of the adapter of the cartridge vane
pump according to the embodiment of the present invention.
DESCRIPTION OF EMBODIMENTS
[0013] An embodiment of the present invention will be described
below with reference to drawings.
[0014] A cartridge vane pump 100 according to the embodiment of the
present invention is used as a fluid pressure source for a fluid
pressure device mounted on a vehicle, such as, for example, a power
steering apparatus, a transmission, and so forth. Working oil,
aqueous alternative fluid of other types, and so forth may be used
as a working fluid.
[0015] The cartridge vane pump 100 (hereinafter, simply referred to
as "a vane pump 100") is accommodated, in a state in which
components are assembled in advance (the state shown in FIG. 1), in
an accommodating concave portion 91 formed in a body 90 of the
fluid pressure device in an attachable and detachable manner (see
FIG. 4). As a motive force from an engine (not shown) is
transmitted to an end portion of a driving shaft 1, a rotor 2
linked to the driving shaft 1 is rotated.
[0016] As shown in FIGS. 1 to 4, the vane pump 100 includes the
rotor 2 that is rotationally driven by being linked to the driving
shaft 1, a plurality of slits 2a that are formed in a radiating
pattern so as to open at an outer circumference of the rotor 2, a
plurality of vanes 3 that are respectively inserted into the slits
2a in a freely slidable manner so as to be capable of reciprocating
in the radial direction of the rotor 2, and a cam ring 4 that
accommodates the rotor 2 and that has an inner circumference cam
face 4a on which tip end portions of the vanes 3 slide by rotation
of the rotor 2.
[0017] At the base-end side of the slits 2a, back pressure chambers
5 into which discharge pressure from a pump is guided are defined.
The vanes 3 are pushed by the pressure in the back pressure
chambers 5 in the directions in which the vanes 3 are drawn out
from the slits 2a, and the tip end portions of the vanes 3 are
brought into contact with the inner circumference cam face 4a of
the cam ring 4. With such a configuration, a plurality of pump
chambers 6 are defined in the cam ring 4 by an outer
circumferential surface of the rotor 2, the inner circumference cam
face 4a of the cam ring 4, and the adjacent vanes 3.
[0018] The cam ring 4 is an annular member whose inner
circumference cam face 4a has a substantially oval shape, and the
cam ring 4 has suction regions at which the volumes of the pump
chambers 6 are expanded as the rotor 2 is rotated and discharge
regions at which the volumes of the pump chambers 6 are contracted
as the rotor 2 is rotated. The respective pump chambers 6 are
expanded/contracted by the rotation of the rotor 2. The vane pump
100 is a so-called balanced vane pump in which the cam ring 4 has
two suction regions and two discharge regions. At the positions of
both end surfaces corresponding to the two suction regions, the cam
ring 4 is formed with cut-out portions 4e through which an outside
and an inside of the cam ring 4 are communicated.
[0019] The vane pump 100 further includes a cover-side side plate
10 that is brought into contact with one end surfaces of the rotor
2 and the cam ring 4 (upper side in FIGS. 1 and 4), a body-side
side plate 20 that is brought into contact with other end surfaces
of the rotor 2 and the cam ring 4 (lower side in FIGS. 1 and 4),
and a cover 30 that is brought into contact with the cover-side
side plate 10 and fixed to the body 90 of the fluid pressure
device. A cover member is configured with the cover-side side plate
10 and the cover 30.
[0020] The cover-side side plate 10 and the body-side side plate 20
are arranged so as to sandwich the rotor 2 and the cam ring 4. Both
end surfaces of the rotor 2 and the cam ring 4 are sandwiched by
the cover-side side plate 10 and the body-side side plate 20, and
thereby, the pump chambers 6 are sealed.
[0021] As shown in FIG. 3, the cover-side side plate 10 includes
guide suction ports 11 that are formed such that parts of an outer
edge portion are cut away so as to guide working oil into the pump
chambers 6, discharging concave portions 12 that are respectively
formed at positions corresponding to the two discharge regions, and
a through hole 13 into which the driving shaft 1 is inserted.
[0022] The suction ports 11 are respectively formed at positions
corresponding to two suction regions. The respective suction ports
11 are formed to have an arc shape centered at the through hole 13.
The suction ports 11 communicate with a tank through a suction
space 70 that is defined and formed to have a ring shape between
the cam ring 4 and the body 90 of the fluid pressure device (shown
in FIG. 4) and through a suction channel 92 formed in the body
90.
[0023] The discharging concave portions 12 are formed so as to have
groove shape at positions corresponding to the two discharge
regions. The respective discharging concave portions 12 are formed
to have an arc shape centered at the through hole 13. The
discharging concave portions 12 are provided so as to face first
and second through holes 21a and 21b formed in the body-side side
plate 20, which will be described later. The first and second
through holes 21a and 21b are formed so as to sandwich the vanes 3.
Because the discharging concave portions 12 communicate with the
first and second through holes 21a and 21b through the pump
chambers 6, the level of the pressure acting on the discharging
concave portions 12 is the same as that for the first and second
through holes 21a and 21b. Therefore, a force acting on the vanes 3
by the pressure in the first and second through holes 21a and 21b
is cancelled out by the pressure in the discharging concave
portions 12, and it is possible to prevent the vanes 3 from being
pressed against the cover-side side plate 10.
[0024] As shown in FIG. 2, the body-side side plate 20 includes a
sliding contact surface 20a with which the other end surface of the
rotor 2 comes into sliding contact, the first and second through
holes 21a and 21b that are formed in the sliding contact surface
20a so as to respectively correspond to the two discharge regions
and that discharge the working oil in the pump chambers 6, a
through hole 22 into which the driving shaft 1 is inserted, and
suction concave portions 23 through which the suction space 70 is
communicated with the pump chambers 6.
[0025] The first and second through holes 21a and 21b are provided
at symmetrical positions centered around the through hole 22. The
first and second through holes 21a and 21b are formed to have an
arc shape centered at the through hole 22 and formed so as to
penetrate through the body-side side plate 20.
[0026] The suction concave portions 23 are formed in the sliding
contact surface 20a so as to correspond to the two suction regions.
Outer circumference ends of the respective suction concave portions
23 reach an outer circumferential surface of the body-side side
plate 20 and are formed to a concaved shape that opens towards the
outside in the radial direction.
[0027] The sliding contact surface 20a of the body-side side plate
20 is formed with outer notches 26 and inner notches 27 that are
grooves extending from the first and second through holes 21a and
21b in the direction opposite to the rotating direction of the
rotor 2. The outer notches 26 are arranged at the outer
circumferential side of the inner notches 27, and have longer
lengths in the rotating direction of the rotor 2 than those of the
inner notches 27.
[0028] The outer notches 26 and the inner notches 27 are both
formed so as to have a tapered shape that narrows in the dimension
in the radial direction of the rotor 2 towards the direction
opposite to the rotating direction of the rotor 2 from the first
and second through holes 21a and 21b. In addition, the outer
notches 26 and the inner notches 27 are arranged at positions
between the outer circumferential side of the outer circumferential
surface of the rotor 2 and the inner circumferential side of the
inner circumference cam face 4a of the cam ring 4.
[0029] In the sliding contact surface 20a of the body-side side
plate 20, a pair of first back pressure grooves 24a are formed at
symmetrical positions centered around the through hole 22, and a
pair of second back pressure grooves 24b are respectively formed at
the positions offset from the pair of the first back pressure
grooves 24a by 90.degree. with respect to the through hole 22 as
the center.
[0030] The first back pressure grooves 24a are formed to have an
arc shape centered at the through hole 22 and communicate with the
back pressure chambers 5. The plurality of back pressure chambers 5
that open to the first back pressure grooves 24a communicate to
each other through the first back pressure grooves 24a.
[0031] The second back pressure grooves 24b are formed to have an
arc shape centered at the through hole 22 and communicate with the
back pressure chambers 5. The plurality of back pressure chambers 5
that open to the second back pressure grooves 24b communicate to
each other through the second back pressure grooves 24b.
[0032] As shown in FIG. 3, the body-side side plate 20 further
includes first and second arc-shaped grooves 25a and 25b that open
to the end surface on the other side of the sliding contact surface
20a and that communicate with the first and second through holes
21a and 21b, respectively, a communication hole 28 through which
the first and second arc-shaped grooves 25a and 25b communicate
with the second back pressure grooves 24b and that is formed so as
to penetrate through the body-side side plate 20, and O-rings 83a
and 83b serving as seal members that respectively surround and seal
outer circumferences of the first and second arc-shaped grooves 25a
and 25b. The O-rings 83a and 83b are installed in grooves formed in
the outer circumferences of the first and second arc-shaped grooves
25a and 25b of the body-side side plate 20 and are provided in a
state in which the O-rings 83a and 83b are compressed between the
body-side side plate 20 and an adapter 40, which will be described
later.
[0033] The first and second arc-shaped grooves 25a and 25b are
formed to have an arc shape centered at the through hole 22. The
first through hole 21a and the communication hole 28 open to a
bottom surface of the first arc-shaped groove 25a, and the second
through hole 21b and the communication hole 28 open to a bottom
surface of the second arc-shaped groove 25b. With such a
configuration, the first through hole 21a communicates with the
communication hole 28 through the first arc-shaped groove 25a, and
the second through hole 21b communicates with the communication
hole 28 through the second arc-shaped groove 25b. In the vane pump
100, the first through hole 21a and the first arc-shaped groove 25a
form a first discharge port 7a, and the second through hole 21b and
the second arc-shaped groove 25b form a second discharge port
7b.
[0034] The cover 30 is formed with a through hole 31 that supports
the end portion of the driving shaft 1 via a sleeve. The cover 30
is fixed to the body 90 by inserting bolts (not shown) into a
plurality of through holes 33 formed in an outer circumference
portion of the cover 30.
[0035] The vane pump 100 further includes the adapter 40 that is
formed with first and second connection channels 41a and 41b that
respectively connect the first and second discharge ports 7a and 7b
formed in the body-side side plate 20 and two discharge channels
(first and second discharge channels 93a and 93b) formed in the
body 90 (see FIG. 4).
[0036] As shown in FIG. 4, the adapter 40 includes a main body
portion 40b having a contact surface 40a that is brought into
contact with the body-side side plate 20 and an annular surface 40f
that faces a bottom surface of a third concave portion 91c of the
accommodating concave portion 91, which will be described later, a
circular tube portion 40c that has a diameter smaller than that of
the main body portion 40b and that extends from the main body
portion 40b in the axial direction, a boss portion 40d that extends
from the main body portion 40b into the circular tube portion 40c
and that is formed with a support hole 42 for supporting the end
portion of the driving shaft 1, and an annular recessed groove 47
that is formed in the annular surface 40f of the main body portion
40b.
[0037] The main body portion 40b is formed to have a circular plate
shape. On an outer circumference of the main body portion 40b, an
ring-shaped O-ring 81 that prevents leakage of the working oil from
between the main body portion 40b and the body 90 is provided.
[0038] The circular tube portion 40c is formed coaxial with the
main body portion 40b and has an internal space 40e in the inside
thereof. On outer circumference of the circular tube portion 40c, a
ring-shaped O-ring 82 that blocks communication between the first
connection channel 41a and the second connection channel 41b is
provided.
[0039] The first connection channel 41a is formed so as to
penetrate through the main body portion 40b between the contact
surface 40a and the annular surface 40f, thereby connecting the
first discharge port 7a and the first discharge channel 93a.
Specifically, the first connection channel 41a is formed with an
arc-shaped first opening portion 44a that opens to the contact
surface 40a, the recessed groove 47 that opens to the annular
surface 40f, and a through hole 45a that allows communication
between the first opening portion 44a and the recessed groove 47.
The first opening portion 44a is formed at a position facing the
first arc-shaped groove 25a of the body-side side plate 20. The
through hole 45a is formed to have an arc shape that extends along
an outer circumferential surface of the circular tube portion 40c
(see FIGS. 6 and 7). Because the recessed groove 47 is formed to
have a ring shape, even in a case in which the first connection
channel 41a of the vane pump 100 and the first discharge channel
93a of the fluid pressure device are not provided at positions
facing each other, as long as the first discharge channel 93a opens
so as to face the recessed groove 47, the first connection channel
41a is communicated with the first discharge channel 93a through
the recessed groove 47.
[0040] As shown in FIG. 4, the second connection channel 41b is
formed so as to penetrate through the main body portion 40b and to
communicate with the internal space 40e of the circular tube
portion 40c, and thereby, the second connection channel 41b
connects the second discharge port 7b and the second discharge
channel 93b. Specifically, the second connection channel 41b is
formed with an arc-shaped second opening portion 44b that opens to
the contact surface 40a, the internal space 40e of the circular
tube portion 40c, and a through hole 45b that allows communication
between the second opening portion 44b and the internal space 40e
of the circular tube portion 40c. The second opening portion 44b is
formed at a position facing the second arc-shaped groove 25b of the
body-side side plate 20. The through hole 45b is formed to have an
arc shape that extends along an outer circumferential surface of
the boss portion 40d (see FIGS. 6 and 7). The second connection
channel 41b communicates with the second discharge channel 93b
formed in the body 90.
[0041] Next, a description will be given to a method of assembling
the vane pump 100.
[0042] First, dowel pins 60 are press-fitted into insertion holes
34 formed in the cover 30. Next, these dowel pins 60 are inserted
into through holes 15 formed in the cover-side side plate 10,
through holes 4c formed in the cam ring 4, and through holes 29b
formed in the body-side side plate 20 in this order, and finally,
the dowel pins 60 are inserted into insertion holes 46 formed in
the adapter 40. With such a configuration, the cover 30, the
cover-side side plate 10, the cam ring 4, the body-side side plate
20, and the adapter 40 are assembled in a stacked state. The
driving shaft 1, the rotor 2, and the vanes 3 are assembled inside
the cam ring 4 when the cam ring 4 is inserted. By doing so, the
dowel pins 60 penetrate through the cam ring 4 such that both ends
of the dowel pins 60 are supported by the cover 30 and the adapter
40, and thereby, relative rotation between the cover 30, the
cover-side side plate 10, the body-side side plate 20, and the
adapter 40 with respect to the cam ring 4 is prevented. In other
words, the dowel pins 60 achieve a positioning function for these
members at the time of assembling and achieve a rotation locking
function for preventing the relative rotation of the cover-side
side plate 10 and the body-side side plate 20 with respect to the
cam ring 4 after assembly.
[0043] The cover 30, the cover-side side plate 10, the cam ring 4,
the body-side side plate 20, and the adapter 40 stacked as
described above are integrally held by two head pins 50 serving as
joining members. A specific description of the head pins 50 will be
given below.
[0044] As shown in FIGS. 2 and 3, the head pins 50 have shaft
portions 51 tip ends of which are fixed to engaging holes 43 formed
in the adapter 40 and restricting portions 52 that have diameters
larger than those of the shaft portions 51 and formed on base ends
of the head pins 50. The shaft portions 51 penetrate through
through holes 32 formed in the cover 30, through holes 14 formed in
the cover-side side plate 10, through hole 4b formed in the cam
ring 4, and through hole 29a formed in the body-side side plate 20,
and the tip ends of the shaft portions 51 are press-fitted to the
engaging holes 43. With such a configuration, the cover 30, the
cover-side side plate 10, the cam ring 4, and the body-side side
plate 20 are held in an integrated state between the restricting
portions 52 of the head pins 50 and the adapter 40. Two head pins
50 are provided at symmetrical positions centered around the
driving shaft 1. The head pins 50 may be fixed to the adapter 40 by
providing male screw portions on the tip end portions of the shaft
portions 51, and by screwing the tip end portions into female screw
portions formed in the engaging holes 43.
[0045] As described above, the vane pump 100 is held in the
integrated state with the head pins 50. With such a configuration,
when the vane pump 100 is installed to the body 90, specifically,
when the vane pump 100 is transported in order to install it to the
body 90 or when the vane pump 100 is mounted to the accommodating
concave portion 91 of the body 90, it is possible to prevent the
vane pump 100 from being disassembled into separate parts.
Therefore, an installability is improved. In addition, also when
the vane pump 100 is to be removed from the body 90, because the
vane pump 100 is held in the integrated state, it is easy to remove
the vane pump 100.
[0046] In a state in which the vane pump 100 is installed to the
body 90 of the fluid pressure device, specifically, in a state in
which the vane pump 100 is accommodated in the accommodating
concave portion 91 of the body 90 and the cover 30 is fixed to the
body 90, as shown in FIG. 5, there is a gap S between the cover 30
and the restricting portions 52 of the head pins 50. When the
pressure in the pump chambers 6 has become high as the vane pump
100 is driven, there is a risk in that the cover 30 undergoes a
deformation (distortion) such that the vicinity of the central part
of the cover 30 is lifted up. With the vane pump 100, because the
gap S is formed between the cover 30 and the restricting portions
52 of the head pins 50, it is possible to allow such a deformation
of the cover 30. In other words, because a force pulling out the
head pins 50 is not applied to the restricting portions 52 of the
head pins 50 due to the deformation of the cover 30, it is possible
to prevent the head pins 50 from being loosened or damaged. As
described above, because the vane pump 100 is held in the
integrated state by the head pins 50, the vane pump 100 is not
disassembled into separate parts when the vane pump 100 is to be
removed.
[0047] In the above-mentioned embodiment, although a case in which
two head pins 50 are used is described as an example, the
configuration is not limited thereto, and the number of the head
pins 50 may be more than two (about three to six) as long as an
enough space can be secured. As the number of the head pins 50
increases, a holding force holding the integrated state of the vane
pump 100 is correspondingly improved. In contrast, as the number of
the head pins 50 decreases, the size of the vane pump 100 can be
reduced correspondingly. By providing two head pins 50 at
symmetrical positions centered around the driving shaft, it is
possible to stably hold the integrated state with the minimum
number of pins. In addition, by configuring the head pins 50 such
that the tip end portions thereof are press-fitted to the engaging
holes 43, it is possible to omit threading of the head pins 50 and
the engaging holes 43.
[0048] The vane pump 100 thus assembled is mounted in the
accommodating concave portion 91 of the body 90 and is fixed to the
body 90 by screwing, into the body 90, the bolts inserted into the
through holes 33 of the cover 30.
[0049] Next, a description will be given to the accommodating
concave portion 91 of the body 90.
[0050] As shown in FIG. 4, the accommodating concave portion 91 of
the body 90 has, in this order from the bottom surface side, a
first concave portion 91a to which the second discharge channel 93b
opens at a bottom surface thereof, a second concave portion 91b
that has the diameter larger than that of the first concave portion
91a and to which the first discharge channel 93a opens at the
bottom surface thereof, the third concave portion 91c that has the
diameter larger than that of the second concave portion 91b and
into which the main body portion 40b of the adapter 40 is inserted,
and a fourth concave portion 91d that is formed to have the
diameter larger than that of the third concave portion 91c and that
has the above-described suction space 70 formed between the fourth
concave portion 91d and the vane pump 100.
[0051] In a state in which the vane pump 100 is accommodated in the
accommodating concave portion 91, the circular tube portion 40c of
the adapter 40 is fitted into the first concave portion 91a, and
the main body portion 40b of the adapter 40 is fitted into the
third concave portion 91c. At this time, the annular surface 40f of
the main body portion 40b faces the bottom surface of the third
concave portion 91c. With such a configuration, a ring-shaped
high-pressure chamber 94 is defined by the second concave portion
91b, the third concave portion 91c, the main body portion 40b of
the adapter 40, and the outer circumference of the circular tube
portion 40c, in other words, the high-pressure chamber 94 is
defined between the main body portion 40b of the adapter 40 and the
bottom surfaces of the second concave portion 91b and the third
concave portion 91c. Into the high-pressure chamber 94, the
high-pressure working oil that has been discharged from the pump
chambers 6 is guided through the first through hole 21a, the first
arc-shaped groove 25a, the first opening portion 44a, the through
hole 45a, and the recessed groove 47. The working oil that has been
guided into the high-pressure chamber 94 then flows out to the
first discharge channel 93a.
[0052] The body-side side plate 20, the cam ring 4, and the
cover-side side plate 10 are accommodated in the fourth concave
portion 91d, and the fourth concave portion 91d is closed by
attaching the cover 30 to the body 90. The ring-shaped suction
space 70 that is in communication with the above-described suction
channel 92 is formed between the fourth concave portion 91d and the
vane pump 100 (the body-side side plate 20, the cam ring 4, and the
cover-side side plate 10).
[0053] Next, a description will be given to an operation of the
vane pump 100.
[0054] As the driving shaft 1 is rotationally driven by a motive
force generated by a driving device, such as an engine (not shown),
the rotor 2 is rotated. As the rotor 2 is rotated, the pump
chambers 6 positioned at the two suction regions are expanded. With
such a configuration, the working oil in the tank is sucked into
the pump chambers 6 through the suction channel 92, the suction
space 70, the cut-out portions 4e, the suction ports 11, and the
suction concave portions 23. In addition, the pump chambers 6
positioned at the two discharge regions are contracted as the rotor
2 is rotated. With such a configuration, the working oil in the
pump chambers 6 in the one of the discharge regions is supplied to
a hydraulic apparatus (not shown) through the first discharge port
7a (the first through hole 21a and the first arc-shaped groove
25a), the first connection channel 41a (the first opening portion
44a, the through hole 45a, and the recessed groove 47), the
high-pressure chamber 94, and the first discharge channel 93a, and
the working oil in the pump chambers 6 in the other of the
discharge regions is supplied to the hydraulic apparatus (not
shown) through the second discharge port 7b (the second through
hole 21b and the second arc-shaped groove 25b), the second
connection channel 41b (the second opening portion 44b, the through
hole 45b, and the internal space 40e), and the second discharge
channel 93b. With the vane pump 100, as the rotor 2 completes a
full rotation, the respective pump chambers 6 repeat the suction
and discharge of the working oil twice.
[0055] A part of the working oil that has been discharged to the
first and second discharge ports 7a and 7b (the first and second
arc-shaped grooves 25a and 25b) is respectively supplied to the
back pressure chambers 5 through the communication hole 28 and the
second back pressure grooves 24b, and base-end portions 3b of the
vanes 3 are pushed towards the inner circumference cam face 4a.
Therefore, the vanes 3 are biased in the directions in which the
vanes 3 project out from the slits 2a by a fluid pressure in the
back pressure chambers 5 that pushes the base-end portions 3b and
by the centrifugal force that is caused by the rotation of the
rotor 2. With such a configuration, because the rotor 2 rotated
while the tip end portions 3a of the vanes 3 are brought into
sliding contact with the inner circumference cam face 4a of the cam
ring 4, the working oil in the pump chambers 6 is discharged from
the pump chambers 6 without leaking out from between the tip end
portions 3a of the vanes 3 and the inner circumference cam face 4a
of the cam ring 4.
[0056] In the state in which the vane pump 100 is accommodated in
the accommodating concave portion 91 of the body 90, the main body
portion 40b of the adapter 40 is brought into contact with the
bottom surface of the third concave portion 91c of the
accommodating concave portion 91. Furthermore, the O-rings 83a and
83b are provided between the adapter 40 and the body-side side
plate 20 in a compressed state. With such a configuration, because
the body-side side plate 20 is constantly pushed against the end
surface of the rotor 2 by an elastic force exerted by the O-rings
83a and 83b, it is possible to prevent a leakage of the working oil
from between the body-side side plate 20 and the rotor 2.
Therefore, the discharge efficiency of the vane pump 100 is
improved. As described above, in addition to a function as seal
members that surround and seal the outer circumference of the first
and second arc-shaped grooves 25a and 25b, the O-rings 83a and 83b
also has a function of biasing members that constantly bias the
body-side side plate 20 against the end surface of the rotor 2.
[0057] As the high-pressure working oil is discharged from the pump
chambers 6, the pressure of the working oil in the first and second
arc-shaped grooves 25a and 25b is also increased. With such a
configuration, the body-side side plate 20 is pushed against the
end surface of the rotor 2. Furthermore, the high-pressure working
oil is guided from the pump chambers 6 also into the high-pressure
chamber 94 through the first discharge port 7a and the first
connection channel 41a. With such a configuration, by the pressure
of the working oil in the high-pressure chamber 94, the adapter 40
is separated away from the bottom surface of the third concave
portion 91c and is pushed against the body-side side plate 20. With
such a configuration, the adapter 40 biases the body-side side
plate 20 towards the rotor 2 by the high-pressure working oil that
has been guided into the high-pressure chamber 94 and pushes the
body-side side plate 20 against the end surface of the rotor 2.
[0058] As the pressure in the pump chambers 6 is increased, the
body-side side plate 20 is no longer pushed towards the rotor 2
sufficiently with only the elastic force exerted by the O-rings 83a
and 83b. However, as the pressure in the pump chambers 6 is
increased, in addition to the biasing force exerted by the
elasticity of the O-rings 83a and 83b, the body-side side plate 20
is pushed against the rotor 2 also by the pressure of the working
oil in the first and second arc-shaped grooves 25a and 25b and by
the pressure of the working oil acting on the adapter 40.
Therefore, even when the pressure in the pump chambers 6 is high,
it is possible to prevent the leakage of the working oil from
between the body-side side plate 20 and the rotor 2.
[0059] In addition, in a state in which the high-pressure working
oil has been guided into the internal space 40e and the
high-pressure chamber 94, because the adapter 40 is pushed against
the body-side side plate 20, the O-rings 83a and 83b are strongly
compressed between the adapter 40 and the body-side side plate 20.
With such a configuration, even if the pressure of the working oil
in the first and second arc-shaped grooves 25a and 25b is
increased, it is possible to prevent the O-rings 83a and 83b from
being squeezed out from the grooves.
[0060] According to the embodiment mentioned above, the advantages
described below are afforded.
[0061] The vane pump 100 includes the body-side side plate 20 that
is brought into contact with the other end surfaces of the rotor 2
and the cam ring 4, and the adapter 40 that is formed with the
first and second connection channels 41a and 41b for connecting the
first and second discharge ports 7a and 7b formed in the body-side
side plate 20 to the first and second discharge channels 93a and
93b formed in the body 90. By appropriately altering the
configuration of the adapter 40, regardless of positional
deviations and differences in the shape of the first and second
discharge ports 7a and 7b formed in the body-side side plate 20 and
the first and second discharge channels 93a and 93b formed in the
body 90, it is possible to connect the first and second discharge
ports 7a and 7b and the first and second discharge channels 93a and
93b, respectively. Furthermore, because there is no need to form
the first and second discharge channels 93a and 93b of the body 90
in accordance with the shapes and the positions of the first and
second arc-shaped grooves 25a and 25b, a degree of freedom for
designing is improved.
[0062] The cartridge vane pump is mounted on various fluid pressure
devices. Therefore, arrangement of the first and second discharge
channels 93a and 93b may be different depending on the fluid
pressure device. In addition, because the body-side side plate 20
slides on the rotor 2, the body-side side plate 20 is formed of an
iron-type sintered metal having superior durability. A
processability of such an iron-type sintered metal is poor, and a
cost of the material itself is high, and therefore, if the
body-side side plate 20 is formed so as to be adapted to the
positions of the first and second discharge channels 93a and 93b,
increase in the cost will be incurred. Thus, with the vane pump
100, a member for connecting the first and second discharge ports
7a and 7b formed in the body-side side plate 20 and the first and
second discharge channels 93a and 93b formed in the body 90 is
formed as the adapter 40 that is separate from the body-side side
plate 20, and the adapter 40 is further formed of an aluminum alloy
having superior processability. With such a configuration, even if
arrangements and shapes of the first and second discharge channels
93a and 93b of the fluid pressure device are different, it is
possible to use common body-side side plate 20. Furthermore,
because the processing time can be reduced by using the aluminum
alloy, the adapter 40 can be manufactured easily, and at the same
time, because the material cost can be reduced, it is possible to
suppress the increase in the cost. In addition, by using the
aluminum alloy having less relative density than an iron, it is
possible to achieve weight reduction of the vane pump 100. In
addition, because the body-side side plate 20 is formed of the
iron-type sintered metal, the durability is improved and seizing
with the rotor 2 is prevented.
[0063] Because the pressure on the discharge side is low at a
starting time of the vane pump 100, the body-side side plate 20
cannot be pushed against the end surface of the rotor 2 depending
on the discharge-side pressure. Therefore, the leakage of the
working oil in the pump chambers 6 is caused from between the
body-side side plate 20 and the rotor 2, and the discharge
efficiency of the pump is deteriorated. Thus, with the vane pump
100, the O-rings 83a and 83b are provided between the adapter 40
and the body-side side plate 20 so as to be compressed. With such a
configuration, because the body-side side plate 20 is pushed
against the end surface of the rotor 2 by the elastic force exerted
by the O-rings 83a and 83b, it is possible to prevent the leakage
from between the body-side side plate 20 and the rotor 2 even when
the pressure of the vane pump 100 is low. Furthermore, because the
O-rings 83a and 83b also function as the seal members for the first
and second arc-shaped grooves 25a and 25b, it is possible to reduce
a number of components.
[0064] In addition, because the body-side side plate 20 is
constantly pushed against the end surface of the rotor 2 by the
elastic force exerted by the O-rings 83a and 83b, a force pushing
the body-side side plate 20 against the rotor 2 need not be
generated by the head pins 50. Therefore, it is possible to make
the head pins 50 thinner or to reduce a number thereof.
[0065] With the vane pump 100, by providing the O-rings 83a and
83b, it is possible to allow dimension errors of the respective
members constituting the vane pump 100. Specifically, even if the
total dimension of the main body portion 40b of the adapter 40, the
body-side side plate 20, the cam ring 4, the cover-side side plate
10, and a part of the cover 30 that is inserted into the
accommodating concave portion 91 in the axial direction of the
driving shaft 1 is less than a depth dimension of the third concave
portion 91c to the bottom surface thereof, it is possible to allow
the dimension error by the possible compressed amount of the
O-rings 83a and 83b.
[0066] Instead of using the O-rings 83a and 83b, a biasing member
may be provided between, for example, the main body portion 40b of
the adapter 40 and the bottom surface of the third concave portion
91c of the body 90. In this case, the biasing member is not limited
to the O-ring, and a member such as a disc spring etc. may also be
employed.
[0067] With the vane pump 100, the ring-shaped high-pressure
chamber 94 into which the high-pressure working oil that has been
discharged from the pump chambers 6 is guided is defined between
the adapter 40 and the bottom surface of the body 90. Because the
high pressure discharged from the pump chambers 6 acts on the
entire annular surface 40f of the main body portion 40b, it is
possible to strongly push the body-side side plate 20 against the
end surface of the rotor 2.
[0068] With the vane pump 100, the main body portion 40b of the
adapter 40 is formed to have a circular plate shape, and the
circular tube portion 40c is formed to have circular tube shape.
With such a configuration, the O-rings 81 and 82 that are provided
in the main body portion 40b and the circular tube portion 40c can
be formed to have a ring shape. Therefore, the O-rings 81 and 82
can have a simple shape, and the O-rings 81 and 82 can be
manufactured easily. Furthermore, by forming the main body portion
40b and the circular tube portion 40c coaxially, it is possible to
make the processing of the adapter 40 easier and to improve a
processing accuracy.
[0069] In addition, by providing the O-ring 81 on the outer
circumference of the circular tube portion 40c, there is no need to
perform sealing by bringing the circular tube portion 40c into
contact with the bottom surface of the first concave portion 91a of
the body 90, and thereby, the processing accuracy is not required
in the axial direction of the adapter 40. With such a
configuration, it is possible to reduce the processing time. In
addition, because the O-rings 81 and 82 are respectively provided
on the outer circumferences of the main body portion 40b and the
circular tube portion 40c, it is possible to prevent the O-rings 81
and 82 from falling off during its installation of the vane pump
100 to the body 90.
[0070] The configurations, operations, and effects of the
embodiment of the present invention configured as described above
will be collectively described.
[0071] The cartridge vane pump 100 includes: the rotor 2 that is
rotationally driven by being linked to the driving shaft 1; the
plurality of slits 2a that are formed in a radiating pattern so as
to open at the outer circumference of the rotor 2; the vanes 3 that
are respectively inserted into the slits 2a in a freely slidable
manner; the cam ring 4 that has the inner circumference cam face 4a
with which the tip end portions of the vanes 3 are brought into
sliding contact; the pump chambers 6 that are defined by the rotor
2, the cam ring 4, and the adjacent vanes 3; the cover members (the
cover 30 and the cover-side side plate 10) that are brought into
contact with the one end surfaces of the rotor 2 and the cam ring 4
and that are fixed to the body 90;
[0072] the body-side side plate 20 that is brought into contact
with the other end surfaces of the rotor 2 and the cam ring 4; the
first and second discharge ports 7a and 7b that are formed in the
body-side side plate 20 and into which the working fluid discharged
from the pump chambers 6 is guided; and the adapter 40 that is
formed with the first and second connection channels 41a and 41b
for connecting the first and second discharge ports 7a and 7b
formed in the body-side side plate 20 and the first and second
discharge channels 93a and 93b formed in the body 90.
[0073] According to this configuration, by appropriately altering
the configuration of the adapter 40, regardless of positional
deviations and differences in the shape of the first and second
discharge ports 7a and 7b formed in the body-side side plate 20 and
the first and second discharge channels 93a and 93b formed in the
body 90, it is possible to connect the first and second discharge
ports 7a and 7b and the first and second discharge channels 93a and
93b. Furthermore, it is possible to use the common body-side side
plate 20 with which the rotor 2 is brought into sliding contact.
Therefore, it is possible to achieve reduction in the cost while
adapting the first and second discharge ports 7a and 7b of the
body-side side plate 20 to the first and second discharge channels
93a and 93b of the fluid pressure device.
[0074] In addition, the cartridge vane pump 100 further includes
the biasing members (the O-rings 83a and 83b) that constantly bias
the body-side side plate 20 towards the rotor 2.
[0075] According to this configuration, because the body-side side
plate 20 is constantly biased towards the rotor 2 by the biasing
members (the O-rings 83a and 83b), it is possible to prevent the
leakage from between the body-side side plate 20 and the rotor 2.
Therefore, the discharge efficiency of the pump is improved.
[0076] In addition, in the cartridge vane pump 100, the biasing
members (the O-rings 83a and 83b) are provided between the adapter
40 and the body-side side plate 20 in a compressed state, and the
biasing members are the seal members that surround and seal the
outer circumferences of the first and second discharge ports 7a and
7b formed in the body-side side plate 20.
[0077] According to this configuration, the seal members (the
O-rings 83a and 83b) that prevent the leakage from the first and
second discharge ports 7a and 7b function as the biasing members
(the O-rings 83a and 83b). With such a configuration, it is
possible to reduce a number of components.
[0078] In addition, with the cartridge vane pump 100, in a state in
which the cartridge vane pump 100 is accommodated in the body 90,
the ring-shaped high-pressure chamber 94 into which the
high-pressure working fluid that has been discharged from the pump
chambers 6 is guided is defined between the adapter 40 and the
bottom surface of the body 90, and the body-side side plate 20 is
biased towards the rotor 2 by the high-pressure working fluid that
has been guided to the high-pressure chamber 94.
[0079] According to this configuration, when the pressure in the
pump chambers 6 is high, the body-side side plate 20 is biased
towards the rotor 2 by the high-pressure working fluid that has
been guided to the high-pressure chamber 94, even when the pressure
is high, it is possible to prevent the leakage from between the
body-side side plate 20 and the rotor 2.
[0080] In addition, in the cartridge vane pump 100, the body-side
side plate 20 is formed of the sintered metal, and the adapter 40
is formed of the aluminum alloy.
[0081] According to this configuration, because the body-side side
plate 20 is formed of the iron-type sintered metal, the durability
is improved and seizing with the rotor 2 is prevented. In addition,
because the adapter 40 is formed of the aluminum alloy that is
lighter than the iron-type sintered metal, it is possible to
achieve the weight reduction. Furthermore, because the aluminum
alloy has an excellent processability, the adapter 40 can be
manufactured easily.
[0082] Embodiments of this invention were described above, but the
above embodiments are merely examples of applications of this
invention, and the technical scope of this invention is not limited
to the specific constitutions of the above embodiments.
[0083] Although two discharge ports are provided in the vane pump
100, only one discharge port may be provided. In addition, the
cover 30 may be formed integrally with the cover-side side plate
10. As long as the high-pressure chamber 94 is formed, the recessed
groove 47 may not be formed.
[0084] Although two discharge channels (the first and second
discharge channels 93a and 93b) are provided in the body 90, only
one discharge channel may be provided. In this case, for example,
the first and second connection channels 41a and 41b may be joined
at the high-pressure chamber 94 without providing the circular tube
portion 40c in the adapter 40.
[0085] This application claims priority based on Japanese Patent
Application No. 2015-185584 filed with the Japan Patent Office on
Sep. 18, 2015, the entire contents of which are incorporated into
this specification.
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