Title of Invention

"CONTINUOUSLY VARIABLE TRANSMISSION"

Abstract A continuously variable transmission comprising: a drive face rotatably supported by a transmission main shaft; a driven face rotatably supported by said transmission main shaft; cone holders movable along said transmission main shaft; double cone supporting shafts supported by said cone holders to extend along a cone generating line centered on said transmission main shaft; double cones, each having first and second cones sharing a bottom face and being rotatably supported by each of said double cone supporting shafts, wherein said first cone is brought in contact with said drive face and said second cone is brought in contact with said driven face; and a centrifugal device for moving said cone holders along an axial line (L) of said transmission main shaft in accordance with an input rotational speed of said transmission main shaft; wherein said double cone supporting shaft is inserted in a supporting hole pierced from the transmission main shaft side so as to be prevented from being slipped-off by a bearing for supporting said cone holder onto said transmission main shaft.
Full Text [Detailed Description of the Present Invention] [0001]
[Technical Field of the Invention]
The present invention relates to a continuously variable transmission including double cones each having a first cone in contact with a drive face and a second cone in contact with a driven face, wherein a speed change ratio is varied by changing the positions of contact portions between the first cone and the drive face and between the second cone and the driven face. [0002]
[Related Art]
Continuously variable transmissions of this type have been known, for example, from Japanese Patent Publication No. Sho 47-447. In the continuously variable transmission of this type, a double cone supporting shaft
for rotatably supporting a double cone on a cone holder is inserted in a supporting hole formed in the cone holder so as to be prevented from being slipped-off. Such slip-off prevention of the double cone supporting shaft has been performed by locking the double cone supporting shaft on the cone holder using a clip, or press-fitting the double cone supporting shaft in the supporting hole formed in the cone holder.
[Problem to be Solved by the Invention]
The slip-off prevention of the double cone supporting shaft using a clip, however, has a problem in the increased number of parts. On the other hand, the slip-off prevention of the double cone supporting shaft by press-fitting has a problem that the removal of the double cone supporting shaft upon disassembly is cumbersome resulting in the reduced maintenance performance. [0004] '
In view of the foregoing, the present invention has been made, and an object of the present invention is to provide a continuously variable transmission in which a double cone supporting shaft is prevented from being slipped off without the need of provision of any special locking member such as a clip"while keeping a preferable
maintenance performance. [0005])
[Means for Solving the Problem]
To achieve the object, according to an invention described in claim 1, a double cone supporting shaft for supporting a double cone is inserted in a bottoming supporting hole pieced in a cone holder from the transmission main shaft side and thereafter the cone holder is assembled with the transmission main shaft via a bearing. With this configuration, since the radially inner end of the double cone supporting shaft is brought in contact with the bearing, the double cone supporting shaft can be prevented from being slipped off without the need of provision of any special member such as a clip or without press-fitting of the double cone supporting shaft in the supporting hole.

Accordingly there is provided a continuously variable transmission comprising:
a drive face rotatably supported by a transmission main shaft;
a driven face rotatably supported by said transmission main shaft;
cone holders movable along said transmission main shaft;
double cone supporting shafts supported by said cone holders to extend along a cone generating line centered on said transmission main shaft;
double cones, each having first and second cones sharing a bottom face and being rotatably supported by each of said double cone supporting shafts, wherein said first cone is brought in contact with said drive face and said second cone is brought in contact with said driven face; and
a centrifugal device for moving said cone holders along an axial line (L) of said transmission main shaft in accordance with an input rotational speed of said transmission main shaft;
wherein said double cone supporting shaft is inserted in a supporting hole pierced from the transmission main shaft side so as to be prevented from being slipped-off by a bearing for supporting said cone holder onto said transmission main shaft.
[Brief Description of the Drawings] [Fig. 1]
A vertical sectional view of a power unit for a vehicle. [Fig. 2]
An enlarged view of an essential portion of Fig. 1. [Fig-* 3]
A sectional view taken on line 3-3 of Fig. 2. [Fig. 4]
A sectional view taken on line 4-4 of Fig. 2. [Fig. 5]
An enlarged view of an essential portion of Fig. 2.
[Embodiments of the Invention]
Hereinafter, one embodiment of the present invention will be described with reference to the accompanying drawings. [0007]
Figs. 1 to 5 show a first embodiment of the present invention, wherein Fig. 1 is a vertical sectional view of a
power unit for a vehicle; Fig. 2 is an enlarged view of an essential portion of Fig. 1; Fig. 3 is a sectional view taken on line 3-3 of Fig. 2; Fig. 4 is a sectional view taken on line 4-4 of Fig. 2; and Fig. 5 is an enlarged view of an essential portion of Fig. 2. [0008]
As shown in Fig. 1, a power unit P, which is to be mounted on a motorcycle, includes an engine E and a casing
I containing a continuously variable transmission T. The
casing 1 is divided into three parts, a center casing 2, a
left casing 3 connected to the left face of the center
casing 2, and a right casing 4 connected to the right face
of the center casing 2. A crank shaft 6, which is
supported on the center casing 2 and the left casing 3 by
means of a pair of ball bearings 5, 5, is connected via a
connecting rod 9 to a piston 8 slidably fitted in a
cylinder block 7 supported on the center casing 2 and the
left casing 3.
[0009]
A power generator 10, provided at the left end of the crank shaft 6, is covered with a power generator cover
II connected to the left face of the left casing 3. A
drive gear 12 is relatively rotatably supported around the
outer periphery of the right end of the crank shaft 6
extending in the right casing 4. The drive gear 12 is connectable to the crank shaft 6 by means of an automatic centrifugal clutch 13 provided at the right end of the crank shaft 6. [0010]
As seen from Figs. 1 and 2, a transmission main shaft 21 of a continuously variable transmission T includes an inner side output shaft 22, and a sleeve-like input shaft 23 relatively rotatably fitted around the outer periphery of the output shaft 22 via a needle bearing 24. Both the ends of the output shaft 22 are hung between the left casing 3 and the right casing 4. A driven gear 25 meshing with the drive gear 12 is fixed on the input shaft 23. The driven gear 25 includes an inner gear half 26 spline-connected to the input shaft 23, and an outer gear half 27 slightly, relatively rotatably connected to the inner gear half 2 6 via a plurality of rubber dampers 2 8 and meshing with the drive gear 12. When an engine torque transmitted from the drive gear 12 to the input shaft 23 by way of the driven gear 25 varies, the rubber dampers 28 act to reduce shock due to variations in the engine torque by deformation thereof. [0011]
A drive face 29 having an annular contact portion
291 directed radially outward is spline-connected around the outer periphery of the input shaft 23, and a driven face 30 having an annular contact portion 301 directed radially inward is relatively rotatably supported around the outer periphery of the output shaft 22. [0012]
A first cone holder 31 formed in an approximately conical shape is supported around the outer periphery of a boss portion 302 of the driven face 30 via a needle bearing 32 in such a manner as to be relatively rotatable and to be axially slidable. As seen from Figs. 1 to 3, a torque cam mechanism 33 for stopping rotation of the first cone holder 31 with respect to the casing 1 includes a pin 34 radially planted in the outer periphery of the first cone holder 31, a roller 36 rotatably supported on the pin 34 via a ball bearing 35, and a guide groove 41 formed in the inner wall face of the right casing 4 for guiding the roller 36. The guide groove 41 is inclined by an angle a with respect to an axial line L of the transmission main shaft 21. [0013]
A plurality of double cone supporting shafts 37 are provided in such a manner as to cross a plurality of a windows 311 formed in the first cone holder 31. A double cone 39 is rotatably supported on each double cone
supporting shaft 37 via needle bearings 38. The double cone supporting shafts 37 are disposed along a cone generating line centered on the axial line L of the transmission main shaft 21, and pass through a gap between the contact portion 291 of the drive face 29 and the contact portion 301 of the driven face 30. Each double cone 39 includes a first cone 40 and a second cone 41 which have a common bottom face. The contact portion 291 of the drive face 29 is brought in contact with the first cone 40, while the contact portion 301 of the driven face 30 is brought in contact with the second cone 41. [0014]
As seen from Fig. 5, a supporting hole 313 formed in the first cone holder 31 for supporting each double cone supporting shaft 37 is a bottoming hole pierced from the inner side to the outer side in the radial direction. The radially inner side opening end of the supporting hole 313 faces to the needle bearing 32 supporting the first cone holder 31 around the outer periphery of the boss portion 302 of the driven face 30 rotated integrally with the transmission main shaft 21. Accordingly, the double cone supporting shaft 37 and the double cone 39 are assembled with the first cone holder 31 by inserting the double cone supporting shaft 37 in the opening end of the supporting
hole 313 of the first cone holder 31 to pass through the double cone 39 in a state that the double cone 39 is fitted in the window hole 311 of the first cone holder 31. Then, by assembling the first cone holder 31 and the driven face 30 around the outer periphery of the transmission main shaft 21, the radially inner end of the double cone supporting shaft 37 is brought in contact with the needle bearing 32 provided between the outer periphery of the boss portion 302 of the driven face 30 and the first cone holder 31, to thereby prevent the slip-off of the double cone supporting shaft 37 from the opening end of the supporting hole 313. [0015]
In this way, the supporting hole 313 is formed as a bottoming hole pierced in the first cone holder 31 from the inner side to the outer side in the radial direction and the radially inner end of the double cone supporting shaft 37 inserted in the supporting hole 313 is prevented from being slipped-off by the needle bearing 32, so that it is possible to reduce the number of parts without the need of provision of a special slip-off preventive member such as a clip, and also to make easy the disassembly as compared with the slip-off preventive mechanism of type press-fitting the double cone supporting shaft 37 in the
supporting hole 313, resulting in the improved maintenance
performance.
[0016]
A window 312 is opened in the upper portion of the first cone holder 31 facing to the crank shaft 6. The tooth face of the driven gear 25 contained in the first cone holder 31 faces to the window 312, and the drive gear 12 meshes with the driven gear 25 through the window 312-[0017]-
A centrifugal mechanism 51 is provided on the right side of the driven gear 25 for changing the speed change ratio of the continuously variable transmission T by axially sliding the first cone holder 31 in accordance with the rotational speed of the input shaft 23. The centrifugal mechanism 51 includes a sleeve 52 fixed around the outer periphery of the input shaft 23, a cam member 54 slidably fitted around the outer periphery of the sleeve 52 via a bush 53, and a plurality of centrifugal weights 55 disposed between a fixed cam face 261 formed on the right face of the inner gear half 26 of the driven gear 25 and a movable cam face 541 formed on the left face of the cam member 54. The outer periphery of the second cam holder 56 covering the centrifugal mechanism 51 is fixed by a clip 57 at the right end of the first'cone holder 31, and the inner
periphery of the second cone holder 56 is supported on the
cam member 54 by means of a ball bearing 58.
[0018]
The first and second cone holders 31 and 56 cooperate to define a space surrounding the transmission main shaft 21. The driven gear 25, drive face 29, and centrifugal mechanism 51 are contained in the space. The space is also communicated to the inner space of the casing 1 through the window 312 to which the tooth face of the driven gear 25 faces and through the windows 311 supporting the double cones 39. [0019]
A stepped collar 59 fitted to the right end of the sleeve 52 is supported around the outer periphery of the right end of the output shaft 22 by means of a ball bearing 60, and the right face of the ball bearing 60 is fixed to the output shaft 22 by means of a cotter 61. The transmission main shaft 21 including the output shaft 22 and the input shaft 23 is supported on the right casing 4 by means of a ball bearing 62 fitted around the outer periphery of the input shaft 23. A spring 64 is provided in a contracted state between a spring retainer 63 supported by the ball bearing 62 and the second cone holder 56. The second cone holder 56 and the first cone holder 31
are biased in the left direction by an elastic force of the
spring 64.
[0020]
When the rotational speed of the input shaft 23 is increased, the centrifugal weights 55 are moved radially outward by centrifugal forces applied to the centrifugal weights 55, and both the cam faces 26lf 541 are pressed by the centrifugal weights 55. As a result, the cam member 54 is moved in the right direction against the elastic force of the spring 64, so that the second cone holder 56 connected to the cam member 54 by means of the ball bearing 58 and the first cone holder 31 are moved in the right direction. [0021]
A pressure adjusting cam mechanism 67 is provided between the right end of an output gear 66 spline-connected to the left end of the output shaft 22 and fixed thereto by a cotter 65 and the left end of the driven face 30. As seen from Fig. 4, the pressure adjusting cam mechanism 67 is so configured that balls 68 are each held between a plurality of recessed portions 661 formed at the right end of the output gear 66 and a plurality of recessed portions 303 formed at the left end of the driven face 30, and a disc spring 69 for imparting a rightward biasing pre-load
to the driven face 30 is interposed between the output gear 66 and the driven face 30. When the driven face 30 is applied with a toque and is rotated relative to the output gear 66, it is biased by the pressure adjusting cam mechanism 67 in the direction being separated from the output gear 66 (right direction, in the figure). [0022]
Referring to again to Fig. 1, a third reduction gear 71 is rotatably supported on the left casing 3 by means of a ball bearing 70, and the left end of the output shaft 22 is coaxially supported on the third reduction gear 71 by means of a needle bearing and a ball bearing 73. A reduction gear 75 is supported on the left casing 3 and the center casing 2 by means of a pair of ball bearings 74, 74, and first and second reduction gears 76, 77 provided on the reduction shaft 75 mesh with the output gear 66 and the third reduction gear 71, respectively. A drive sprocket 79, around which an endless chain 78 is wound, is provided at the leading end of the shaft portion of the third reduction gear 71 projecting outward from the left casing 4. The rotation of the output shaft 22 is thus transmitted to a drive wheel via the output gear 66, first reduction gear 76, second reduction gear 77, third reduction gear 71, drive sprocket 79, and endless chain 78.
[0023]
An oil passage 42 formed in the right casing 4 is communicated to an oil passage 22]. axially passing through the output shaft 22, and each portion of the continuously variable transmission T is lubricated by an oil supplied from the oil passage 221 to the inner space surrounded by the first and second cone holders 31, 56. [0024]
- Next, the function of this embodiment of the present invention having the above-described configuration will be described. [0025]
As shown in Fig. 2, a distance A between the contact portion 291 of the drive face 29 and the axial line L of the transmission main shaft 21 is constant, while a distance B between the contact portion 291 of the drive face 29 and the double cone supporting shaft 37 is variable (BL, BT). A distance C between the contact portion 301 of the driven face 30 and the double cone supporting shaft 37 is variable (CL, CT), while a distance D between the contact portion 301 of the driven face 30 and the axial line L of the transmission main shaft 21 is constant. [0026]
A speed change ratio R is given by
R = NDR/NDN = (B/A)X(D/C) where NDR is a rotational speed of the drive face 29 and NDN is a rotational speed of the driven face 30. [0027]
When the engine E is rotated at a low speed, the rotational speed of the driven gear 25 driven by the driven gear 12 is low. At this time, as shown on the upper half in Fig. 2, since centrifugal forces applied to the centrifugal weights 55 of the centrifugal mechanism 51 are low, the second cone holder 56 and the first cone holder 31 are moved in the left direction by the elastic force of the spring 64. As the first cone holder 31 is moved in the left direction, the contact portion 291 of the driven face 29 is moved on the bottom face side of the first cone 40 of the double cone 39 and thereby the distance B is increased to the maximum value BL, while the contact portion 301 of the driven face 30 is moved on the vertex side of the second cone 41 of the double cone 39 and thereby the distance C is decreased to the minimum value CL. [0028]
When the distance B is increased to the maximum value BL and the distance C is decreased to the minimum value CL as described above (the distances A, D are constant), the speed change ratio R is increased into a LOW
ratio. [0029]
On the other hand, when the engine E is rotated at a high speed, the rotational speed of the driven gear 25 driven by the drive gear 12 is high. At this time, as shown on the lower half in Fig. 2, since centrifugal forces applied to the centrifugal weights 55 of the centrifugal mechanism 51 are high, the second cone holder 56 and the first cone holder 31 are moved in the right direction against the elastic force of the spring 64 by the action of the centrifugal weights 55 moved radially outward by the centrifugal forces. As the first cone holder 31 is moved in the right direction, the contact portion 291 of the drive face 29 is moved on the vertex side of the first cone 40 of the double cone 39 and thereby the distance B is decreased to the minimum value BT, while the contact portion 301 of the driven face 30 is moved on the bottom face side of the second cone 41 of the double cone 39 and thereby the distance C is increased to the maximum value
[0030]
When the distance B is decreased to the minimum value BT and the distance C is increased to the maximum value CT as described above (the distances A, D are
constant), the speed change ratio R is decreased into a TOP
ratio.
[0031]
In this way, the speed change ratio of the continuously variable transmission T can be continuously changed between the LOW and TOP sides in accordance with the rotational speed of the engine E. Furthermore, since the speed change ratio is automatically controlled by the centrifugal mechanism 51, it becomes possible to reduce the cost due to simplification of the structure and to make smaller the size of the continuously variable transmission T, as compared with the case of provision of a speed change controller for manually controlling speed change from the outside of the casing 1 or of provision of an electronic speed change controller. [0032]
The rotation of the drive face 2 9 is thus transmitted at a specified speed change ratio R to the driven face 30 via the double cones 39 and the rotation of the driven face 30 is transmitted to the output gear 66 via the pressure adjusting cam mechanism 67. At this time, when a relative rotation is generated between the driven face 30 and the output gear 66 by a torque applied to the driven face 30, the driven face 30 is biased in the
direction where it is separated from the output gear 66 by the pressure adjusting cam mechanism 67. The biasing force generates, in co-operation with the biasing force by the disc spring 69, a face pressure for pressing the contact portion 291 of the drive face 29 to the first cone 40 of the double cone 39 and a face pressure for pressing the contact portion 301 of the driven face 30 to the second cone 41 of the double cone 39. [0033]-
Incidentally, while the biasing force by the pressure adjusting cam mechanism 67 presses the output gear 66 in the left direction, the leftward pressing force is transmitted to the output gear 22 because the left end of the output gear 66 is fixed to the left end of the output shaft 22 by the cotter 65. Furthermore, while the biasing force by the pressure adjusting cam mechanism 67 presses the driven face 30 in the right direction, the rightward pressing force is transmitted from the driven face 30 to the right end of the output shaft 33 by way of the double cones 39, drive face 29, inner gear half 26, sleeve 52, ball bearing 62, collar 59, ball bearing 60, the cotter 61. [0034]
Accordingly, the load applied from the pressure adjusting cam mechanism 67 to'the output gear 66 and the
driven face 30 for respectively pressing them in the left and right directions, acts as a tensile load for the output shaft 22, and the tensile load is canceled by an internal stress of the output shaft 22. As a result, the pressing load of the pressure adjusting cam mechanism 67 is not transmitted to the casing 1. This eliminates the need of reinforcing the strength of the casing 1 to such an extent as to withstand the pressing load, thereby reducing the weight-of the continuously variable transmission T. Also, since the drive face 29 and the driven face 30 are biased only by one pressure adjusting cam mechanism 67, it is possible to reduce the number of parts and the cost, as compared with the case where they are biased by individual pressure cam mechanisms 67. [0035]
Although the first cone holder 31 is intended to be rotated around the transmission main shaft 21 by a reaction force to the transmission torque of the drive face 29 upon speed change operation by the continuously variable transmission T, the reaction force to the transmission torque is received by engagement between the roller 36 of the torque cam mechanism 33 supported by the first cone holder 31 and the guide groove 41 formed in the right casing 4, and consequently the first cone holder 31 can be
slid in the axial direction without any rotation. [0036]
When an engine torque is rapidly increased for rapid acceleration during running of a vehicle, a reaction force to a transmission torque, which is applied to the first cone holder 31, is increased along with the rapid increase in the engine torque. Consequently, as shown in Fig. 3, the roller 36 is brought in press-contact with the wall face of the inclined guide groove 41 by a load F, and the first cone holder 31 is biased on the left side (on the LOW ratio side) in Fig. 2 by a component F1 of the load F applied in the direction of the guide groove 41. Namely, the speed change ratio is automatically changed on the LOW ratio side by the action of the torque cam mechanism 33, so that the so-called kick-down effect is exhibited and the vehicle can be effectively accelerated. [0037]
Furthermore, the speed change ratio control upon kick-down can be automatically performed by the torque cam mechanism 33 in accordance with a change in engine torque without the need of provision of any special speed change controller, so that it is possible to reduce the cost due to simplification of the structure and to make smaller the size of the continuously variable transmission T. In
addition, the change characteristic of the speed change ratio can be easily adjusted only by changing the shape of the guide groove 41 of the torque cam mechanism 33. [0038]
Although the lower portions of the first and second cone holders 31, 56 of the continuously variable transmission T are immersed in oil stored in the bottom portion of the casing 1, a large amount of oil does not permeate from the bottom portion of the casing 1 into the inner space surrounded by the first and second cone holders 31, 56 because the windows 311 supporting the double cone 39 and the windows 322 to which the gear tooth of the driven gear 25 faces are positioned higher than an oil level OL of the oil (see Fig. 2). Even if a lubricating oil is supplied from the oil passage 221 passing through the output shaft 22 into the inner space surrounded by the first and second cone holders 31, 56, the oil is scattered outward by the centrifugal force generated by rotation of the driven gear 25. As a result, the minimum oil required for lubrication is held in the inner space surrounded by the first and second cone holders 31, 56. [0039]
Since the driven gear 25 stirs only a small amount of oil as described above, it"is possible to suppress a
loss in power due to the stirring of unnecessary oil at minimum. Furthermore, since the oil permeation is prevented by the first and second cone holders 31, 56, it is possible to eliminate the need of provision of any special oil preventive member and hence to reduce the number of parts. [0040]
As described above, the arrangement of the driven gear 25 in the space defined by the first and second cone holders 31, 56 makes it possible to reduce the oil stirring resistance as compared with the case of arrangement of the driven gear 25 outside the space. Furthermore, the arrangement of the drive face 29 and the centrifugal mechanism 51 on the right and left sides of the driven gear 25 makes it possible to make use of the capacity of the above space and hence to make compact the continuously variable transmission T. [0041]
While the embodiments of the present invention have been described in detail, such description is for illustrative purposes only, and it is to be understood that changes and modifications may be made without departing from the scope of the present invention. [0042]
For example, although in this embodiment, the needle bearing 32 for preventing the slip-off of the double cone supporting shaft 37 is not directly disposed between the first cone holder 31 and the transmission main shaft 21 but is indirectly disposed while putting the boss portion 302 of the driven face 30 therebetween, it may be directly disposed between the first cone holder 31 and the transmission main shaft 21. In other words, the needle bearing 32 may have a function to directly or indirectly support the first cone holder 31 on the transmission main shaft 21. The needle bearing 32 may be also replaced with other bearings such as a ball bearing. [0043]
[Effect of the Invention]
As described above, according to the invention described in claim 1, since a double cone supporting shaft is inserted in a bottoming supporting hole pieced in a cone holder from the transmission main shaft side and is prevented from being slipped off by a bearing for supporting the cone holder on the transmission main shaft, it is possible to prevent the double cone supporting shaft from being slipped off without the need of provision of any special member such as a clip or without press-fitting of the double cone supporting shaft in the supporting hole, resulting in the reduced number of parts and the improved maintenance performance.
[Explanation of Characters] 21: transmission main shaft, 29: drive face, 30: driven face, 31: first cone holder (cone holder); 313: supporting hole, 32: needle bearing (bearing); 37: double cone supporting shaft, 39: double cone; 40: first cone, 41: second cone, 51: centrifugal mechanism, 56: second cone holder (cone holder), L: axial line





WE CLAIM:-
1. A continuously variable transmission comprising:
a drive face (29) rotatably supported by a transmission main shaft
(21);
a driven face (30) rotatably supported by said transmission main shaft (21);
cone holders (31, 56) movable along said transmission main shaft
(21);
double cone supporting shafts (37) supported by said cone holders (31, 56) to extend along a cone generating line centered on said transmission main shaft (21);
double cones (39), each having first and second cones (40, 41) sharing a bottom face and being rotatably supported by each of said double cone supporting shafts (37), wherein said first cone (40) is brought in contact with said drive face (29) and said second cone (41) is brought in contact with said driven face (30); and
a centrifugal device (51) for moving said cone holders (31, 56) along an axial line (L) of said transmission main shaft (21) in accordance with an input rotational speed of said transmission main shaft (21);
wherein said double cone supporting shaft (37) is inserted in a supporting hole (313) pierced from the transmission main shaft (21) side so as to be prevented from being slipped-off by a bearing (32) for supporting said cone holder (31, 56) onto said transmission main shaft (21).
2. A continuously variable transmission substantially as hereinbefore
described with reference to and as illustrated in the accompanying
drawings.

Documents:

1418-DEL-1997-Form-1.pdf

1418-DEL-1997-Form-3.pdf

1418-DEL-1997-Form-6.pdf

1418-del-200-abstract.pdf

1418-del-200-claims.pdf

1418-del-200-correspondence-others.pdf

1418-del-200-correspondence-po.pdf

1418-del-200-description (complete).pdf

1418-del-200-drawings.pdf

1418-del-200-form-1.pdf

1418-del-200-form-13.pdf

1418-del-200-form-19.pdf

1418-del-200-form-2.pdf

1418-del-200-form-3.pdf

1418-del-200-form-4.pdf

1418-del-200-form-6.pdf

1418-del-200-gpa.pdf

1418-del-200-pettition-137.pdf


Patent Number 242479
Indian Patent Application Number 1418/DEL/1997
PG Journal Number 36/2010
Publication Date 03-Sep-2010
Grant Date 27-Aug-2010
Date of Filing 28-May-1997
Name of Patentee HONDA GIKEN KOGYO KABUSHIKI KAISHA
Applicant Address 1-1, MINAMIAOYAMA 2-CHOME, MINATO-KU, TOKYO, JAPAN.
Inventors:
# Inventor's Name Inventor's Address
1 YOSHIAKI TSUKADA C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, OF 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
2 KAZUHIKO NAKAMURA C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, OF 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
3 HIROAKI KAYAMA C/O KABUSHIKI KAISHA HONDA GIJUTSU KENKYUSHO, OF 4-1, CHUO 1-CHOME, WAKO-SHI, SAITAMA, JAPAN.
PCT International Classification Number F16G 5/16
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 HEI-8-351225 1996-12-27 Japan