Title of Invention

INTERNAL GEAR OIL PUMP ROTOR ASSEMBLY

Abstract An internal gear oil pump rotor assembly which enables the construction of an oil pump that is compact and has high performance. In the oil pump rotor assembly having an inner rotor (10) and an outer rotor (20), the number of teeth "Zi" of the inner rotor (10) with trochoid tooth profiles is set to be equal to or fewer than "6", and a ratio Si/So is set so as to satisfy the following inequalities: 0.8≤Si/So≤1.3, where Si is a cross-sectional area of one external tooth (11) which is formed outside a root circle (di) that is formed along the bottoms of the external teeth (11) of the inner rotor (10), and So is a cross-sectional area of one internal tooth (21) which is formed inside a root circle (Do) that is formed along the bottoms of the internal teeth (21) of the outer rotor (20).
Full Text BACKGROUND OF THE INVENTION
Field of the Invention
This invention relates to an oil pump rotor assembly used in a trochoid internal
gear oil pump which draws and discharges fluid by volume change of cells formed
between an inner rotor and an outer rotor when the inner rotor and the outer rotor rotate
while engaging each other.
Background Art
A conventional oil pump includes an inner rotor having "n" external teeth
(hereinafter "n" indicates a natural number), an outer rotor having "n+1" internal teeth
which are engageable with the external teeth, and a casing in which a suction port for
drawing fluid and a discharge port for discharging fluid are formed, and fluid is drawn
and is discharged by rotation of the inner rotor which makes the outer rotor rotate due to
engagement of the external teeth and internal teeth, and which produces changes in the
volumes of cells formed between the inner rotor and the outer rotor.
Each of the cells is delimited at a front portion and at a rear portion as viewed
in the direction of rotation by contact regions between the external teeth of the inner
rotor and the internal teeth of the outer rotor, and is also delimited at either side portions
by the casing, so that an independent fluid conveying chamber is formed. Each of the
cells draws fluid as the volume thereof increases when the cell moves over the suction
port after the volume thereof is minimized in the engagement process between the
external teeth and the internal teeth, and the cell discharges fluid as the volume thereof


decreases when the cell moves over the discharge port after the volume thereof is
maximized.
The discharging capacity of such an oil pump could be increased, for example,
by increasing the size of the rotors, by increasing an eccentric distance between the
rotors so as to increase the volume of each of the cells, or by increasing the revolution
rate of the rotors.
However, increase in diameters or thicknesses of the rotors and increase in the
revolution rate of the rotors for increasing the discharging capacity are not preferable
because increase in diameters or thicknesses of the rotors deviates from the trend in oil
pump rotors in which small size is preferred, and increase in the revolution rate of the
rotors may cause cavitation which may iead to decrease in pump efficiency, excessive
wear, and increase in noise.
On the other hand, when the numbers of teeth of the rotors are reduced, the
eccentric distance between the rotors is increased so that the discharging capacity is
increased; however, hydraulic pulsation is increased because changes in drawing and
discharging flow velocity of oil at the ports are increased and is due to the small number
of teeth. As a result, not only does cavitation occur, but also pump efficiency is
decreased because oil is drawn from a discharging cell due to excessive negative suction
pressure, or because air is drawn through clearance in the casing.
As explained above, the above-described measures are not appropriate to
increase the discharging capacity of an oil pump, i.e., such measures cannot fulfill
recent requirements of compactness and high performance.
SUMMARY OF THE INVENTION


In view of the above circumstances, an object of the present invention is to
provide an oil pump rotor assembly for use in an oil pump that is compact and has high
performance.
In order to solve the above problems, the inventors of the present invention
conducted research and concluded that an oil pump, which exhibits high discharging
performance and low hydraulic pulsation even in an oil pump rotor assembly with a
small number of teeth, can be obtained by appropriately adjusting a cross-sectional area
ratio between the internal teeth of the outer rotor and the external teeth of the inner rotor
so that changes in drawing and discharging flow velocities of oil are reduced, and the
maximum value of the flow velocity is reduced without decreasing flow rate in one
cycle of drawing and discharging.
The present invention was conceived based on the above research results. An
internal gear oil pump rotor assembly according to the present invention includes: an
inner rotor having "Zi" external teeth with trochoid tooth profiles; and an outer rotor
having "Zo" internal teeth which are engageable with the external teeth, wherein the oil
pump rotor assembly is used in an oil pump which further includes a casing having a
suction port for drawing fluid and a discharge port for discharging fluid are formed, and
which conveys fluid by drawing and discharging fluid by volume change of cells
formed between the inner rotor and the outer rotor produced by relative rotation
between the inner rotor and the outer rotor engaging each other, and wherein the number
of teeth "Zi" of the inner rotor is set to be equal to or fewer than "6", and a ratio Si/So is
set so as to satisfy the following inequalities: 0.8≤Si/So≤1.3, where Si is a
cross-sectional area of one external tooth which is formed outside a root circle "di" that
is formed along the bottoms of the external teeth of the inner rotor, and So is a


cross-sectional area of one internal tooth which is formed inside a root circle Do that is
formed along the bottoms of the internal teeth of the outer rotor.
According to the present invention, the ratio Si/So is set so as to satisfy the
following inequalities: 0.8≤Si/So≤1.3, which means that the ratio Si/So is set to be
much greater than that in a conventional oil pump, which is approximately 0.5. As a
result, the volume change, due to rotation of the rotors, in each of the cells formed
between the rotors is reduced, and changes in drawing and discharging flow velocities at
the ports can be reduced so that the maximum value of the flow velocity is lowered.
In other words, even in an oil pump using an inner rotor having a small number
of teeth, such as six or fewer, which could not be used in a conventionci oil pump due to
problems of excessive hydraulic pulsation and cavitation, hydraulic pulsation can be
restrained while at the same time discharging capacity is increased, and thus a compact
oil pump having high discharging efficiency and high performance can be obtained.

BRIEF DESCRIPTION OF THE ACCOMPANYING DRAWINGS
FIG. 1 is a plan view showing an oil pump rotor assembly as Example 1 of the
present invention in which the inner and outer rotors thereof are formed so that a ratio
Si/So equals 0.8. where Si is a cross-sectional area of one external tooth of the inner
rotor, and So is a cross-sectional area of one internal tooth of the internal teeth of the
outer rotor.
FIG 2 is a plan view showing an oil pump rotor assembly as Example 2 of the
present invention in which the inner and outer rotors thereof are formed so that the ratio
Si/So equals 1.2.
FIG. 3 is a plan view showing an oil pump rotor assembly as Example 3 of the


present invention in which the inner and outer rotors thereof are formed so that the ratio
Si/So equals 1.3.
FIG. 4 is a plan view showing a conventional oil pump rotor assembly as
Comparative Example in which the inner and outer rotors thereof are formed so that the
ratio Si/So equals 0.618.
FIG. 5 is a graph showing comparison of flow velocity changes of the oil
pumps respectively having the oil pump rotor assemblies according to Examples 1 to 3
shown in FIGS. 1 to 3, respectively, and the oil pump rotor assembly of the
Comparative Example shown in FIG. 4.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Embodiments of an oil pump rotor assembly according to the present invention
will be explained below.
The oil pump rotor assembly shown in FIG. 1 includes an inner rotor 10
providec with "Zi" external teeth 11 with trochoid tooth profiles, an outer rotor 20
provided with "Zo" internal teeth 21 which are engageable with the external teeth 11 of
the inner rotor 10. The oil pump rotor assembly is accommodated in a casing 30.
1 he inner rotor 10 is mounted on a rotational axis (not shown) so as to be
rotatable about an axis 01. The outer rotor 20 is mounted so as to be rotatable. in the
casing 30, about an axis 02 which is disposed so as to have an offset (the eccentric
distance is "e") from the axis 01 of the inner rotor 10.
Each of the external teeth 11 of the inner rotor 10 and each of the internal teeth
21 of the outer rotor 20 are formed so that a ratio Si/So satisfies the following
inequalities: 0.8≤Si/So≤1.3. where Si is a cross-sectional area of one of the external


teeth 11 which are formed outside a root circle "di" that is formed along the bottoms of
the external teeth 11 of the inner rotor 10. and So is a cross-sectional area of one of the
internal teeth 21 which are formed inside a root circle Do that is formed along the
bottoms of the internal teeth 21 of the outer rotor 20.
Between the tooth surfaces of the inner rotor 10 and outer rotor 20. there are
formed a plurality of cells C in the direction of rotation of the inner rotor 10 and outer
rotor 20. Each of the cells C is delimited at a front portion and at a rear portion as
viewed in the direction of rotation of the inner rotor 10 and outer rotor 20 by contact
regions between the external teeth 11 of the inner rotor 10 and the internal teeth 21 of
the outer rotor 20. and is also delimited at either side portions by the casing 30. so that
an independent fluid conveying chamber is formed. Each of the cells C moves while
the inner rotor 10 and outer rotor 20 rotate, and the volume of each of the cells C
cyclically increases and decreases so as to complete one cycle in a rotation.
In the casing 30, a suction port 31 having a curved shape is formed in a region
along which each of the cells C. which are formed between the rotors 10 and 20, moves
while gradually increasing the volume thereof, and a discharge port 32 having a curved
shape is formed in a region along which each of the cells C moves while gradually
decreasing the volume thereof
Each of the cells C draws fluid as the volume thereof increases when the cell C
moves over the suction port 31 after the volume of the cell C is minimized in the
engagement process between the external teeth 11 and the internal teeth 21, and the cell
C discharges fluid as the volume thereof decreases when the cell C moves over the
discharge port 32 after the volume of the cell C is maximized.
Next, Examples 1 to 3 of the oil pump rotor assemblies according to the


present invention, in which the inner and outer rotors are formed so that the ratio Si/So
satisfies the following inequalities: 0.8≤Si/So≤1 .3. where Si is a cross-sectional area of
one of the external teeth 11 which are formed outside a root circle "di" that is formed
along the bottoms of the external teeth 11 of the inner rotor 10, and So is a
cross-sectional area of one of the internal teeth 21 which are formed inside a root circle
Do that is formed along the bottoms of the internal teeth 21 of the outer rotor 20. and a
Comparative Example of a conventional oil pump rotor assembly, in which the inner
and outer rotors are formed so that the above inequalities are not satisfied, will be more
specifically explained below.
Note that the oil pump rotor assemblies of Examples 1 to 3 and of Comparative
Example are respectively configured so as to have the same theoretical discharging
volume per revolution when being driven under conditions in which the revolution rate
is set to be 1000 rpm. and discharging pressure is set to be 200 kPa.
Example 1
The specifications of the oil pump rotor assembly of Example 1 shown in FIG.
1 are set as follows:
the diameter of the addendum circle Di of the inner rotor is 40.32 mm;
the diameter of the root circle "di" of the inner rotor is 25.36 mm:
the diameter of the root circle Do of the outer rotor is 48.20 mm:
the diameter of the addendum circle "do" of the outer rotor is 32.92 mm;
the eccentric distance "e" is 3.74 mm;
the radius of the inner rotor generating circle Ri is 10.80 mm:
the radius of the arc Ro of the tooth tip of the outer rotor is 10.80 mm;


the radius of the rounded corner "r" of the outer rotor is 3.00 mm:
the number of teeth "Zi" of the inner rotor is "4";
the number of teeth "Zo" of the outer rotor is "5";
the thickness of each of the teeth is 12.6 mm;
the theoretical discharging volume Vth is 9.32 cm3/rev. ; and
the area ratio Si/So per tooth is 0.8.
Example 2
The specifications of the oil pump rotor assembly of Example 2 shown in FIG.
2 are set as follows:
the diameter of the addendum circle Di of the inner rotor is 40.32 mm;
the diameter of the root circle "di" of the inner rotor is 25.36 mm:
the diameter of the root circle Do of the outer rotor is 48.20 mm:
the diameter of the addendum circle "do" of the outer rotor is 32.92 mm:
the eccentric distance "e" is 3.74 mm;
the radius of the inner rotor generating circle Ri is 5.90 mm;
the radius of the arc Ro of the tooth tip of the outer rotor is 5.90 mm;
the radius of the rounded corner "r" of the outer rotor is 5.00 mm;
the number of teeth "Zi" of the inner rotor is "4";
the number of teeth "Zo" of the outer rotor is "5";
the thickness of each of the teeth is 12.6 mm;
the theoretical discharging volume Vth is 9.32 cm3/rev. ; and
the area ratio Si/So per tooth is 1.2.
The oil pump rotor assembly of Example 2 differs from the oil pump rotor


assembly of Example 1 in terms of the area ratio Si/So per tooth. In order to configure
the oil pump rotor assembh' of Example 2 so as to have the above area ratio Si/So. the
radius of the inner rotor generating circle Ri, the radius of the arc Ro of the tooth tip of
the outer rotor, and the radius of the rounded corner "r" of the outer rotor are set
differently from the oil pump rotor assembly of Example 1, and the other dimensions
are set to be the same as in Example 1.
Example 3
The specifications of the oil pump rotor assembly of Example 3 shown in FIG.
3 are set as follows:
the diameter of the addendum circle Di of the inner rotor is 40.32 mm:
the diameter of the root circle "di" of the inner rotor is 25.36 mm;
the diameter of the root circle Do of the outer rotor is 48.20 mm:
the diameter of the addendum circle "do" of the outer rotor is 32.92 mm;
the eccentric distance "e" is 3.74 mm;
the radius of the inner rotor generating circle Ri is 5.30 mm;
the radius of the arc Ro of the tooth tip of the outer rotor is 5.30 mm;
the radius of the rounded corner "r" of the outer rotor is 5.00 mm;
the number of teeth "Zi" of the inner rotor is "4";
the number of teeth "Zo" of the outer rotor is "5";
the thickness of each of the teeth is 12.6 mm;
the theoretical discharging volume Vth is 9.32 cm /rev. ; and
the area ratio Si/So per tooth is 1.3.
The oil pump rotor assembly of Example 3 differs from the oil pump rotor


assemblies of Examples 1 and 2 in terms of the area ratio Si/So per tooth. In order to
configure the oil pump rotor assembly of Example 3 so as to have the above area ratio
Si/So, when compared with Example 1. the radius of the inner rotor generating circle Ri.
the radius of the arc Ro of the tooth tip of the outer rotor, and the radius of the rounded
corner "r" of the outer rotor are differently set, and the other dimensions are set to be the
same, and when compared with Example 2, the radius of the inner rotor generating
circle Ri, and the radius of the arc Ro of the tooth tip of the outer rotor are differently
set. and the other dimensions are set to be the same.
Comparative Example
FIG. 4 shows an example of a conventional oil pump rotor assembly as a
Comparative Example in which the inner and outer rotors are formed so that the
inequalities "0.8≤Si/So≤1.3" are not satisfied.
The specifications of the oil pump rotor assembly of Comparative Example
shown in FIG. 4 are set as follows:
the diameter of the addendum circle Di of the inner rotor is 40.32 mm;
the diameter of the root circle "di" of the inner rotor is 25.36 mm:
the diameter of the root circle Do of the outer rotor is 48.20 mm;
the diameter of the addendum circle 'do" of the outer rotor is 32.92 mm;
the eccentric distance "e" is 3.74 mm;
the radius of the inner rotor generating circle Ri is 15.00 mm:
the radius of the arc Ro of the tooth tip of the outer rotor is 15.03 mm;
the radius of the rounded corner "r" of the outer rotor is 3.00 mm:
the number of teeth "Zi" of the inner rotor is "4";


the number of teeth "Zo" of the outer rotor is "5";
the thickness of each of the teeth is 12.6 mm;
the theoretical discharging volume Vth is 9.32 cm3/rev. ; and
the area ratio Si/So per tooth is 0.618.
The oil pump rotor assembly of Comparative Example differs from the oil
pump rotor assemblies of Examples 1 to 3 in terms of the area ratio Si/So per tooth. In
the oil pump rotor assembly of Comparative Example, when compared with Example 1.
the radius of the inner rotor generating circle Ri. and the radius of the arc Ro of the
tooth tip of the outer rotor are differently set, and the other dimensions are set to be the
same, and when compared with Examples 2 and 3. the radius of the inner rotor
generating circle Ri, the radius of the arc Ro of the tooth tip of the outer rotor, and the
radius of the rounded corner "r" of the outer rotor are differently set, and the other
dimensions are set to be the same.
FIG. 5 is a graph showing comparison of flow velocity change in each of the oil
pumps according to the above Examples 1 to 3 and th? Comparative Example. In FIG.
5, the horizontal axis represents rotational angle of the inner rotor, and the vertical axis
represents flow velocity change which is obtained by dividing the flow volume rate due
to volume change of the cell by the cross-sectional area. The signs of the flow velocity
change are differently applied to a discharging state and a drawing state, respectively.
According to FIG. 5. in the oil pumps respectively using the oil pump rotor
assemblies of the present invention, the maximum values of the flow velocity change
are less than that in the conventional oil pump, and the curves representing flow
velocity changes are flatter than that in the conventional oil pump. It is clear that the
flow velocity change greatly varies when the area ratio Si/So is set to be less than 0.8.


The flow velocity change varies in each case as explained above, and
consequently, discharging efficiencies of the oil pumps according to respective
Examples are as follows:
in the case of Example 1 (Si/So=0.80). discharging efficiency is 85%;
in the case of Example 2 (Si/So=1.20). discharging efficiency is 87%;
in the case of Example 3 (Si/So=l .30). discharging efficiency is 90%; and
in the case of Comparative Example (Si/So=0.618). discharging efficiency is 80%.
when the revolution rate is 1000 rpm. and the discharging pressure is 200 kPa. As
described above, the oil pumps respectively having the oil pump rotor assemblies
therein exhibit higher d:scnarging efficiencies than in the case of the conventional oil
pump.
Moreover, when the shapes of the oil pump rotor assemblies according to the
above Examples are compared, the inner teeth 21 of the outer rotor 20 are made smaller
as the area ratio Si/So is set to be greater. When the inner teeth 21 are made smaller,
contact pressure between the inner roter 10 and the outer rotor 20 becomes greater.
which may degrade wear resistance and impact resistance of the rotors, and thus such
rotors are not preferable for practical use.
Accordingly, it is preferable to set the area ratio Si/So to be equal to or greater
than 0.8, with which variation in flow velocity change is restrained, and to be equal to
or less than 1.3, with which the strength of the rotors is ensured.
The preferable range of the area ratio Si/So slightly changes depending on the
number of teeth of the rotors.
For example, when the number of teeth "Zi" of the inner rotor is "6". and the
number of teeth "Zo" of the outer rotor is "7", the preferable range is as follows:


0.8≤Si/So≤0.85: when the number of teeth "Zi" of the inner rotor is "5" and the number
of teeth "Zo" of the outer rotor is "6". the preferable range is as follows: 0.8≤Si/So≤0.9:
and when the number of teeth "Zi" of the inner rotor is "4", and the number of teeth
"Zo" of the outer rotor is "5". the preferable range is as follows: 0.8≤Si/So≤1.0.
Advantageous Effects Obtainable by the Invention
As explained above, in a trochoid oil pump using the oil pump rotor assembly
according to the present invention, by setting the ratio Si/So so as to satisfy the
following inequalities: 0.8≤Si/So≤1.3. i.e.. by setting the ratio Si/So to be much greater
than that in a conventional oil pump which is approximately 0.5. the volume change,
due to rotation of the rotors, in each of the cells formed between the rotors is reduced.
and variation in flow velocity changes during drawing and discharging at the ports can
be reduced so that the maximum value of the flow velocity change is lowered.
Accordingly, even in an oil pump using an inner rotor having a small number
of teeth, such as six or fewer, which could not be used in a conventional oil pump due to
problems of excessive hydraulic pulsation and cavitation, hydraulic pulsation can be
restrained while at the same time discharging capacity is increased, and thus a compact
oil pump having high discharging efficiency and high performance can be obtained.
In addition, because pump efficiency is high, a sufficient performance can be
ensured even when side clearance is set to be greater than that in a conventional oil
pump. In other words, by using the oil pump rotor assembly according to the present
invention, a sufficient discharging performance, which could be only obtained with
accurately machined rotors in the case of a conventional oil pump, can be obtained even
when dimensional accuracy of the rotors and the casing is degraded more than that in a

conventional oil pump and thus manufacturing cost of the oil pump rotor assembly can
be reduced.

WE CLAIM:
1. An internal gear oil pump rotor assembly, comprising:
an inner rotor (10) having "Zi" external teeth (11) with trochoid tooth profiles:
and
an outer rotor (20) having "Zo" internal teeth (21) which are engageable with
the external teeth (11).
wherein the oil pump rotor assembly is used in an oil pump which further
includes a casing (30) having a suction port (31) for drawing fluid and a discharge port
(32) for discharging fluid are formed, and when conveys fluid by drawing and
discharging fluid by volume change of cells (C) formed between the inner rotor (10) and
the outer rotor (20) produced by relative rotation between the inner rotor (10) and the
outer rotor (20) engaging each other, and
wherein the number of teeth "Zi' of the inner rotor (10) is set to be equal to or
fewer than "6". and a ratio Si/So is set so as to satisfy the following inequalities:
0.8≤Si/So≤1.3, where Si is a cross-sectional area of one external tooth (11) which is
formed outside a root circle (di) that is formed along the bottoms of the external teeth
(11) of the inner rotor (10), and So is a cross-sectional area of one internal tooth (21)
which is formed inside a root circle (Do) that is formed along the bottoms of the internal
teeth (21) of the outer rotor (20).

2. An internal gear oil pump rotor assembly , substantially as herein
described particularly with reference to the accompanying drawings.


An internal gear oil pump rotor assembly which enables the construction of an
oil pump that is compact and has high performance. In the oil pump rotor assembly
having an inner rotor (10) and an outer rotor (20), the number of teeth "Zi" of the inner
rotor (10) with trochoid tooth profiles is set to be equal to or fewer than "6", and a ratio
Si/So is set so as to satisfy the following inequalities: 0.8≤Si/So≤1.3, where Si is a
cross-sectional area of one external tooth (11) which is formed outside a root circle (di)
that is formed along the bottoms of the external teeth (11) of the inner rotor (10), and So
is a cross-sectional area of one internal tooth (21) which is formed inside a root circle
(Do) that is formed along the bottoms of the internal teeth (21) of the outer rotor (20).

Documents:

377-KOL-2003-ABSTRACT 1.1.pdf

377-kol-2003-abstract.pdf

377-KOL-2003-AMANDED CLAIMS.pdf

377-KOL-2003-ASSIGNMENT.1.3.pdf

377-kol-2003-assignment.pdf

377-KOL-2003-CERTIFICATE.pdf

377-kol-2003-claims.pdf

377-KOL-2003-CORRESPONDENCE 1.1.pdf

377-KOL-2003-CORRESPONDENCE.1.3.pdf

377-kol-2003-correspondence.pdf

377-KOL-2003-DESCRIPTION (COMPLETE) 1.1.pdf

377-kol-2003-description (complete).pdf

377-KOL-2003-DRAWINGS 1.1.pdf

377-KOL-2003-DRAWINGS 1.2.pdf

377-kol-2003-drawings.pdf

377-KOL-2003-EXAMINATION REPORT.1.3.pdf

377-KOL-2003-FORM 1 1.1.pdf

377-KOL-2003-FORM 1-1.2.pdf

377-kol-2003-form 1.pdf

377-KOL-2003-FORM 13.1.3.pdf

377-KOL-2003-FORM 13.pdf

377-KOL-2003-FORM 18.1.3.pdf

377-kol-2003-form 18.pdf

377-KOL-2003-FORM 2 1.1.pdf

377-KOL-2003-FORM 2-1.2.pdf

377-kol-2003-form 2.pdf

377-KOL-2003-FORM 3 1.1.pdf

377-KOL-2003-FORM 3-1.2.pdf

377-KOL-2003-FORM 3.1.3.pdf

377-kol-2003-form 3.pdf

377-KOL-2003-FORM 5-1.1.pdf

377-KOL-2003-FORM 5.1.3.pdf

377-kol-2003-form 5.pdf

377-KOL-2003-FORM 6-1.1.pdf

377-KOL-2003-FORM 6.1.3.pdf

377-kol-2003-form 6.pdf

377-KOL-2003-FORM-27-1.pdf

377-KOL-2003-FORM-27.pdf

377-KOL-2003-GPA.1.3.pdf

377-kol-2003-gpa.pdf

377-KOL-2003-GRANTED-ABSTRACT.pdf

377-KOL-2003-GRANTED-CLAIMS.pdf

377-KOL-2003-GRANTED-DESCRIPTION (COMPLETE).pdf

377-KOL-2003-GRANTED-DRAWINGS.pdf

377-KOL-2003-GRANTED-FORM 1.pdf

377-KOL-2003-GRANTED-LETTER PATENT.pdf

377-KOL-2003-GRANTED-SPECIFICATION.pdf

377-KOL-2003-OTHERS 1.2.pdf

377-KOL-2003-OTHERS DOCUMENTS 1.1.pdf

377-KOL-2003-OTHERS.1.3.pdf

377-KOL-2003-PA.pdf

377-kol-2003-priority document.pdf

377-KOL-2003-REPLY TO EXAMINATION REPORT.1.3.pdf

377-kol-2003-reply to examination report.pdf

377-kol-2003-specification.pdf

377-kol-2003-translated copy of priority document.pdf


Patent Number 248899
Indian Patent Application Number 377/KOL/2003
PG Journal Number 36/2011
Publication Date 09-Sep-2011
Grant Date 07-Sep-2011
Date of Filing 07-Jul-2003
Name of Patentee DIAMET CORPORATION
Applicant Address 1-1, KOGANE-CHO 3-CHOME, HIGASHI-KU, NIIGATA-SHI, NIIGATA-KEN
Inventors:
# Inventor's Name Inventor's Address
1 HIRABAYASHI, KATSUMI C/O AISIN SEIKI KABUSHIKI KAISHA, 1, ASAHI-MACHI 2-CHOME, KARIYA-SHI, AICHI-KEN
2 HOSONO KATSUAKI C/O MITSUBISHI MATERIALS CORPORATION, NIIGATA PLANT, 1-1, KOGANE-CHO 3-CHOME, NIGATA-SHI, NIGATA-KEN
3 KOBAYASHI TAKASHI C/O MITSUBISHI MATERIALS CORPORATION, 5-1, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO
4 KIMURA ICHIRO C/O AISIN SEIKI KABUSHIKI KAISHA, 1, ASAHI-MACHI 2-CHOME, KARIYA-SHI, AICHI-KEN
5 KURITA HIROTAKA C/O AISIN SEIKI KABUSHIKI KAISHA, 1, ASAHI-MACHI 2-CHOME, KARIYA-SHI, AICHI-KEN
PCT International Classification Number F04C 2/08, 2/10
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 2002-201264 2004-07-10 Japan