GB1581289A - Transmissions - Google Patents

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Publication number
GB1581289A
GB1581289A GB4460377A GB4460377A GB1581289A GB 1581289 A GB1581289 A GB 1581289A GB 4460377 A GB4460377 A GB 4460377A GB 4460377 A GB4460377 A GB 4460377A GB 1581289 A GB1581289 A GB 1581289A
Authority
GB
United Kingdom
Prior art keywords
gear
sun gear
planet
sun
carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
GB4460377A
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Deere and Co filed Critical Deere and Co
Publication of GB1581289A publication Critical patent/GB1581289A/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Description

(54) IMPROVEMENTS IN TRANSMISSIONS (71) We, DEERE & COMPANY, a corporation organised and existing under the laws of the State of Delaware, United States of America, of Moline, Illinois 61265, United States of America, do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed. to be particularly described in and by the following statement: The present invention relates generally to vehicle power shift transmissions and more particularly to a planetary transmission which is capable of being shifted between six forward speeds and two reverse speeds.
In the past, a relatively complex system of gears, brakes, and clutches were required in order to provide a large number of speed ratios as shown in the U.S Patent 3,298,252 granted to K. J. Harris et al which provided eight forward and four reverse speeds. With further development of planetary transmissions simple arrangements have been devised such as that shown in the U.S. Patent 3,381,546 granted to H.H. Holl; however, with simplification. the number of speed ratios has been decreased, for example with the Holl transmission only four forward and three reverse speeds are available.
The present invention is defined in claim 1 and provides six forward and two reverse speeds while requiring a minimum number of gears, brakes. and clutches.
In the drawings: Figure 1 is a diagrammatic longitudinal view. partially in section. of a planetary transmission embodying the present invention; Figure 2 is a cross-sectional view taken along the line 2~ 2 of Figure 1: and Figure 3 is a cross-sectional view taken along the line ~3 of Figure 1.
Referring now to Figure 1. therein is shown a planetary transmission 10. The transmission 10 is driven by a drive shaft 12 which is generally connected to an internal combustion engine (not shown). The drive shaft 12 is splined to an input hub 14 which includes a first clutch 16 having conventional clutch components. The first clutch 16 is clutchable to couple the input hub 14 to a common planet carrier generally designated by the numeral 18 which is positioned rearwardly of the input hub 14. The expression "rearwardly" is used on the basis of a typical fore and aft disposition of the transmission in a vehicle; however, it will be realized that such an expression is used for purposes of convenience and not by way of limitation.
The planet carrier 18 is relatively long in fore and aft extension and has front and rear walls 20 and 22, respectively, coaxial apertured at 24 and 26, respectively. The planet carrier 18 has means rigidly interconnecting the front and rear walls 20 and 22. and this means includes several shafts, for carrying planet gears to be hereinafter described, together with circumferentially spaced wall portions.
The drive shaft 12 extends through the aperture 24 in the front wall 20 of the planet carrier 18 and has secured thereto a first sun gear 28 and rearwardly therefrom a second sun gear 30.
The first sun gear 28 meshes with a first planet gear set 32 which consists of three gears as shown in Figure 2 and which are bearing-mounted on a set of three equilaterally spaced first shafts 34. The first shafts 34 are rigidly secured to the planet carrier 18 so as to allow the first planet gear set 32 to protrude from the planet carrier 18 and mesh with a first ring gear 36. The first ring gear 36 concentrically encircles the first sun gear 28 and is floatingly carried by the first planet gear set 32. The first ring gear 36 is associated with a first brake 38 having conventional components which allow the first ring gear 36 to be selectively braked and released relative to a transmission housing 40.
The second sun gear 30 meshes with a second planet gear set 42 which is similar to the first planet gear set 32 in consisting of three gears which are bearing-mounted on a set of three equilaterally spaced second shafts 44. Only the second planet gear 42 and one second shaft 44 is shown in the drawings. The second shafts 44 are rigidly secured to the planet carrier 18 and positioned so as to allow the second planet gear set 42 to protrude therefrom to engage a second ring gear 46. The second ring gear 46 concentrically encircles the second sun gear 30 and is floatingly carried by the second planet gear set 42. The second ring gear 46 is associated with a second brake 48 having conventional components for selectively braking and releasing the second ring gear 46 relative to the transmission housing 40.
The second shaft set 44 extends rearwardly from the second planet gear set 42 into the rear wall 22 of the planet carrier 18. On the second shaft set 44, just forwardly of the rear wall 22 are bearing-mounted the gears of a third planet gear set 50 which consists of three equilaterally spaced gears as shown in Figure 3.
The third planet gear set 50 protrudes from the planet carrier 18 to mesh with a third ring gear 52. The third ring gear 52 concentrically encircles a third sun gear 56 and is floatingly carried bv the third planet gear set 50. The third ring gear 52 is associated with a third brake 54 having conventional components for selectively braking and releasing the third ring gear 52 relative to the transmission housing 40. The third planet gear set 50 further meshes with the centrally apertured third sun gear 56.
The third sun gear 56 is connected by a hollow intermediate portion 58 to a third sun gear hub 60 which is associated with a fourth brake 62 having conventional components for selectively braking and releasing the third sun gear 56 relative to the transmission housing 40.
The third planet gear set 50 still further meshes with a fourth planet gear set 64 consisting of three gears which are bearingmounted on a set of three equilaterally spaced third shafts 66 so as to not protrude from the planet carrier 18. The fourth planet gear set 64 meshes with a fourth sun gear 68 forward of the third sun gear 56: The fourth sun gear 68 is secured to a driven shaft 70 which extends rearwardly from the planet carrier 18 through the centrally apertured third sun gear 5(7 and the hollow intermediate portion 58 to the exterior of the transmission housing 4(). Just rearwardly of the third sun gear hub 6() is secured a second clutch 72 having conventional components for selectively coupling and uncoupling the third sun gear hub 60 and the driven shaft 70; i.e. coupling and uncoupling the third and fourth sun gears 56 and 68.
From the description thus far, and noting that drive shaft 12 may be connected to a power source such as an internal combustion engine by a clutch or other torque transmitting mechanism, it will be seen that the drive shaft 12 may be regarded as a constantly rotating part.
A first forward speed is obtained by anchoring the first brake 38 and the second clutch 72. The rotation of the drive shaft 12 is transmitted through the first sun gear 28 to the first planet gear set 32 which is forced to translate because the first ring gear 36 is braked by the first brake 38. The translation of the first planet gear set 32 causes rotation of the planet carrier 18. The rotation of the planet carrier 18 is transmitted through the third and fourth planet gears 50 and 64 to the third and fourth sun gears 56 and 68 which are prevented from rotating relative to one another due to the engagement of the second clutch 72 which causes the driven shaft 70 to rotate at the same speed as the planet carrier 18.
A second forward speed is obtained by actuating the second brake - 48 while the second clutch 72 remains engaged. The rotation of the drive shaft 12 is then transmitted through'the second sun gear 30 to the second planet gear set 42 which is forced to translate since the second ring gear 46 is braked by the second brake 48. The translation of the second planet gear 42 causes rotation of the planet carrier 18 at a speed different from that in the first forward speed. Since the second clutch 72 is engaged the driven shaft 70 will again rotate at the same speed as the planet carrier 18.
A third forward speed is obtained by actuating the first brake 38 and the fourth brake 62. The rotation of the drive shaft 12 is transmitted through the first sun gear 28 to the first planet gear set 32 which is forced to translate because of the first ring gear 36 is held by the first brake 38. The translation of the first planet gear set 32 causes rotation of the planet carrier 18 and thus translation of the third planet gear set 50. With the fourth brake 62 braking the third sun gear hub 60 and therefore the third sun gear 56, the translation of the third planet gear set 50 around the third sun gear 56 causes rotation of the third planet gear set 50. The rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70.
A fourth foward speed is obtained by braking the second brake 48 and the fourth brake 62. The rotation of the drive shaft 12 is then transmitted through the second sun gear 30 to the second planet gear set 42 which translates because the second ring gear 46 is braked by the second brake 48.
The translation of the second planet gear set 42 causes rotation of the planet carrier 18 which causes translation of the third planet gear set 50. The third planet gear set 50 rotates because the third sun gear 56 is braked by the fourth brake 62 and the rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70.
A fifth forward speed is obtained by clutching the first and second clutches 16 and 72. The rotation of the drive shaft 12 is transmitted through the first clutch 16 to the planet carrier 18 and thence through the second clutch 72 into the driven shaft 70 so as to provide a direct mechanical drive from the drive shaft 12 to the driven shaft 70.
A sixth forward speed may be obtained by clutching the first clutch 16 and actuating the fourth brake 62. The rotation of the drive shaft 12 is transmitted through the first clutch 16 to the planet carrier 18 to cause translation of the third planet gear set 50 and rotation thereof since the third sun gear 56 is braked by the fourth brake 62. The rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70.
A first reverse speed is obtained by actuating the first and third brakes 38 and 54. The rotation of the drive shaft 12 is transmitted through the first sun gear 28 to the first planet gear set 32 which is forced to translate and cause rotation of the planet carrier 18 since the first ring gear 36 is braked by the first brake 38. The rotation of the planet carrier 18 causes translation of the third planet gear set 50 which rotates in an opposite direction from that of the forward speeds since the third ring gear 52 is braked by the third brake 54. The reverse rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70 to cause rotation thereof at a first reverse speed.
A second reverse speed is obtained by actuating the second and third brakes 48 and 54. The rotation of the drive shaft 12 is transmitted through the second sun gear 30 to the second planet gear set 42 which is forced to translate and rotate the planet carrier 18 due to the braking of the second ring gear 46 by the second brake 48. The translation of the planet carrier 18 causes translation of the third planet gear set 50 and reverse rotation thereof due to the third ring gear 52 being braked by the third brake 54. The reverse rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70 to cause rotation thereof at a second reverse speed.
WHAT WE CLAIM IS: 1. A transmission comprising a drive shaft, a driven shaft and first, second, and third axially spaced planetary units having a rotatable common planet carrier spanning the shafts; said first planetary unit including a first sun gear secured to the drive shaft, a first rotatable ring gear surrounding the first sun gear, a first planet gear journaled in the planet carrier meshing with the first sun gear and the first ring gear, first brake means for selectively braking and releasing the first ring gear and first clutch means for selectively coupling the planet carrier and the drive shaft together; said second planetary unit including a second sun gear secured to the drive shaft axially spaced from the first sun gear, a second rotatable ring gear surrounding the second sun gear, a second planet gear journaled in the planet carrier meshing with the second sun gear and the second ring gear and second brake means for selectively braking and releasing the second ring gear; said third planetary unit including a third and fourth relatively rotatable sun gears, a third ring gear surrounding said third sun gear, a third planet gear journaled in the planet carrier meshing with the third sun gear and the third ring gear, a fourth planet gear journaled in the planet carrier meshing with the third planet gear and the fourth sun gear, third brake means for selectively braking and releasing the third ring gear fourth brake means for selectively braking and releasing the third sun gear and second clutch means for selectively coupling the third and fourth sun gears together, whereby the driven shaft is rotatable at six different forward ratios when the first, second, and fourth brakes are selectively actuated and released with the first and second clutches coupled or released and whereby the driven shaft is rotatable at two different reverse ratios when the first and second brakes are actuated or released with the third brake actuated.
2. A transmission according to claim 1, wherein the second planetary unit is coaxially behind the first planetary unit and the fourth sun gear is located ahead of the third sun gear and rearwardly of the first and second sun gears, the third sun gear is axially hollow and the driven shaft extends coaxially therethrough and is connected to the fourth sun gear, and the fourth brake means includes a hollow portion coaxially surrounding the driven shaft and coaxially connected to the third sun gear.
3. A transmission according to claim 1, wherein the drive shaft. the planet carrier, and the driven shaft are coaxial on a fore and aft axis, the second sun gear is spaced
**WARNING** end of DESC field may overlap start of CLMS **.

Claims (6)

**WARNING** start of CLMS field may overlap end of DESC **. which translates because the second ring gear 46 is braked by the second brake 48. The translation of the second planet gear set 42 causes rotation of the planet carrier 18 which causes translation of the third planet gear set 50. The third planet gear set 50 rotates because the third sun gear 56 is braked by the fourth brake 62 and the rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70. A fifth forward speed is obtained by clutching the first and second clutches 16 and 72. The rotation of the drive shaft 12 is transmitted through the first clutch 16 to the planet carrier 18 and thence through the second clutch 72 into the driven shaft 70 so as to provide a direct mechanical drive from the drive shaft 12 to the driven shaft 70. A sixth forward speed may be obtained by clutching the first clutch 16 and actuating the fourth brake 62. The rotation of the drive shaft 12 is transmitted through the first clutch 16 to the planet carrier 18 to cause translation of the third planet gear set 50 and rotation thereof since the third sun gear 56 is braked by the fourth brake 62. The rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70. A first reverse speed is obtained by actuating the first and third brakes 38 and 54. The rotation of the drive shaft 12 is transmitted through the first sun gear 28 to the first planet gear set 32 which is forced to translate and cause rotation of the planet carrier 18 since the first ring gear 36 is braked by the first brake 38. The rotation of the planet carrier 18 causes translation of the third planet gear set 50 which rotates in an opposite direction from that of the forward speeds since the third ring gear 52 is braked by the third brake 54. The reverse rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70 to cause rotation thereof at a first reverse speed. A second reverse speed is obtained by actuating the second and third brakes 48 and 54. The rotation of the drive shaft 12 is transmitted through the second sun gear 30 to the second planet gear set 42 which is forced to translate and rotate the planet carrier 18 due to the braking of the second ring gear 46 by the second brake 48. The translation of the planet carrier 18 causes translation of the third planet gear set 50 and reverse rotation thereof due to the third ring gear 52 being braked by the third brake 54. The reverse rotation of the third planet gear set 50 is transmitted through the fourth planet gear set 64 to the fourth sun gear 68 and thence to the driven shaft 70 to cause rotation thereof at a second reverse speed. WHAT WE CLAIM IS:
1. A transmission comprising a drive shaft, a driven shaft and first, second, and third axially spaced planetary units having a rotatable common planet carrier spanning the shafts; said first planetary unit including a first sun gear secured to the drive shaft, a first rotatable ring gear surrounding the first sun gear, a first planet gear journaled in the planet carrier meshing with the first sun gear and the first ring gear, first brake means for selectively braking and releasing the first ring gear and first clutch means for selectively coupling the planet carrier and the drive shaft together; said second planetary unit including a second sun gear secured to the drive shaft axially spaced from the first sun gear, a second rotatable ring gear surrounding the second sun gear, a second planet gear journaled in the planet carrier meshing with the second sun gear and the second ring gear and second brake means for selectively braking and releasing the second ring gear; said third planetary unit including a third and fourth relatively rotatable sun gears, a third ring gear surrounding said third sun gear, a third planet gear journaled in the planet carrier meshing with the third sun gear and the third ring gear, a fourth planet gear journaled in the planet carrier meshing with the third planet gear and the fourth sun gear, third brake means for selectively braking and releasing the third ring gear fourth brake means for selectively braking and releasing the third sun gear and second clutch means for selectively coupling the third and fourth sun gears together, whereby the driven shaft is rotatable at six different forward ratios when the first, second, and fourth brakes are selectively actuated and released with the first and second clutches coupled or released and whereby the driven shaft is rotatable at two different reverse ratios when the first and second brakes are actuated or released with the third brake actuated.
2. A transmission according to claim 1, wherein the second planetary unit is coaxially behind the first planetary unit and the fourth sun gear is located ahead of the third sun gear and rearwardly of the first and second sun gears, the third sun gear is axially hollow and the driven shaft extends coaxially therethrough and is connected to the fourth sun gear, and the fourth brake means includes a hollow portion coaxially surrounding the driven shaft and coaxially connected to the third sun gear.
3. A transmission according to claim 1, wherein the drive shaft. the planet carrier, and the driven shaft are coaxial on a fore and aft axis, the second sun gear is spaced
rearwardly of the first sun gear, the first clutch means is secured to the drive shaft ahead of the first sun gear, and the second clutch means is secured to the driven shaft behind the third sun gear.
4. A transmission according to claim 3, wherein the third sun gear is axially hollow and is spaced rearwardly from the fourth sun gear, the fourth brake means includes a hollow intermediate portion coaxially connected to and extending rearwardly from said third sun gear, and said fourth sun gear is coaxially between the second and third sun gears and is secured to the driven shaft which extends rearwardly through said hollow intermediate portion.
5. A transmission according to claim 1, wherein the carrier has spaced apart, centrally apertured front and rear walls and means rigidly interconnecting said walls and having openings therein exposing the interior of said carrier radially outwardly; the first sun gear being within the carrier just behind the front wall; the second sun gear coaxial with the first sun gear being within the carrier just rearwardly of the first sun gear; the first and second relatively rotatable ring gears encircling the carrier and being respectively concentric with the first and second sun gears; the first and second planet gears journaled in the carrier meshing respectively with the first and second sun via at least one of the aforesaid openings; the third sun gear being a centrally apertured sun gear separate from the other sun gears and disposed within the carrier ahead of said rear wall and spaced rearwardly from the second sun gear; the fourth sun gear being separate from the other sun gears and disposed within the carrier intermediate the second and third sun gears, and the third rotatable ring gear encircling the carrier in concentric relation to the third sun gear; the third planet gear journaled in the carrier and meshing with the third sun gear being in mesh with the third ring gear via at least one of the aforesaid openings; the drive shaft extending through the carrier front wall and being secured to the first and second sun gears; a hollow intermediate shaft extending coaxially through the carrier rear wall and being fixed to the third sun gear; and the driven shaft extending axially through the intermediate shaft and being fixed to the fourth sun gear.
6. A transmission substantially as de scribed hereinbefore with reference to and as shown in the accompanying drawings.
GB4460377A 1976-10-26 1977-10-26 Transmissions Expired GB1581289A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US73537976A 1976-10-26 1976-10-26

Publications (1)

Publication Number Publication Date
GB1581289A true GB1581289A (en) 1980-12-10

Family

ID=24955521

Family Applications (1)

Application Number Title Priority Date Filing Date
GB4460377A Expired GB1581289A (en) 1976-10-26 1977-10-26 Transmissions

Country Status (8)

Country Link
JP (1) JPS6035577B2 (en)
AR (1) AR215484A1 (en)
BR (1) BR7707022A (en)
CA (1) CA1069735A (en)
DE (1) DE2745623C3 (en)
FR (1) FR2369465A1 (en)
GB (1) GB1581289A (en)
MX (1) MX144748A (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60208659A (en) * 1984-03-31 1985-10-21 Takashi Takahashi Multistage variable speed clutch apparatus
DE59206334D1 (en) * 1991-03-30 1996-06-27 Volkswagen Ag Planetary gear arrangement with hydraulic torque converter

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE712527C (en) * 1937-11-14 1941-10-21 Werke Kiel Akt Ges Deutsche Revolving gear change and reversing gear, especially for vehicles
US3234821A (en) * 1961-07-05 1966-02-15 Caterpillar Tractor Co Planetary transmission
US3298252A (en) * 1964-01-17 1967-01-17 Deere & Co Transmission
US3274858A (en) * 1964-01-17 1966-09-27 Deere & Co Transmission
US3381546A (en) * 1966-01-21 1968-05-07 Caterpillar Tractor Co Power transmitting mechanism

Also Published As

Publication number Publication date
DE2745623C3 (en) 1981-07-16
AR215484A1 (en) 1979-10-15
BR7707022A (en) 1978-07-18
DE2745623B2 (en) 1980-09-25
FR2369465B1 (en) 1980-06-13
MX144748A (en) 1981-11-19
DE2745623A1 (en) 1978-04-27
CA1069735A (en) 1980-01-15
JPS6035577B2 (en) 1985-08-15
JPS5354659A (en) 1978-05-18
FR2369465A1 (en) 1978-05-26

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Legal Events

Date Code Title Description
PS Patent sealed
PCNP Patent ceased through non-payment of renewal fee