CN2683939Y - Hydrodynamic torque-converter with double clutch - Google Patents
Hydrodynamic torque-converter with double clutch Download PDFInfo
- Publication number
- CN2683939Y CN2683939Y CN 200420011574 CN200420011574U CN2683939Y CN 2683939 Y CN2683939 Y CN 2683939Y CN 200420011574 CN200420011574 CN 200420011574 CN 200420011574 U CN200420011574 U CN 200420011574U CN 2683939 Y CN2683939 Y CN 2683939Y
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- oil
- turbine
- pump
- torque converter
- clutch
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Abstract
Disclosed is a hydrodynamic torque-converter with double clutch which relates to an automatic speed changing system of carrying vehicles, in particular to an automatic speed changing system of a hydrodynamic torque-converter and a fixed-spindle mechanical speed changing box, aiming to remodel the mechanical speed changing box into an automatic speed changing box. The utility model adopts a double clutch structure, and the gear shift sleeve and the lockup clutch of the double clutch structure are overlapped in radial direction on a turbine. A pump impeller is connected with a pump impeller flange driving an oil pump, and the pump impeller flange is connected with the oil resource through an oil channel board. The oil pump is a crescent gear pump and is integrated with the oil channel board. All the oil channels connected with the oil source are integrated on the oil channel board. The oil channels entering the hydrodynamic torque-converter are distributed in circumferential direction at an annular circumferential face where the oil channel board is integrated with the base of a guide wheel, and the base of the guide wheel is in interference fit with the oil channel board. The utility model can reduce the cost of the automatic speed changing system and improve dynamic performance, economic performance and riding comfort.
Description
Technical field
The utility model relates to the haulage vehicle automatic speed-changing system, particularly relates to a kind of fluid torque converter and fixed shaft type mechanical gear box automatic speed-changing system (TC+AMT)
Technical background
At present automatic speed-changing system is a lot, and as automatic mechanical transmission (AMT), hydraulic automatic speed variator system (AT) and stepless automatic transmission system (CVT) etc., but AT, CVT technical difficulty are bigger, and investment is many, takes effect slowly; The AMT cost is low, the efficient height, but starting, the gear shift smoothness is relatively poor.
Summary of the invention
The purpose of this utility model is to form automatic speed-changing system, the especially fluid torque converter with double clutch that designs at conventional fixed shaft type mechanical gear box for finishing fluid torque converter (TC) with AMT or DVT (double-clutch type gearbox) mechanical gearbox.
For making existing machinery formula gearbox be transformed into automatic transmission case, adopt fluid torque converter (TC) to add mechanical gear box and automatic gear-selecting-shifting mechanism, require torque-converters to have two clutch configurations, promptly one is lockup clutch, and road conditions are better after vehicle start quickens, when the advantage of fluid torque converter is no longer outstanding, turbine is become to be rigidly connected with the torque-converters housing, to realize the mechanical type transmission, outputting power improves transmission efficiency and adopts.Another is a gear shift sleeve, i.e. during AMT gear shift, input shaft and engine power disconnect, and reducing rotary inertia, thereby guarantees the smooth gear shift of AMT mechanical gearbox.
Above-mentioned purpose of the present utility model is achieved in that accompanying drawings is as follows, fluid torque converter with double clutch, it is by motor 41, mechanical gear box 43, bent axle 1, pump impeller 4, turbine 5, guide wheel 6, unidirectional freewheel 7, wheel stand 8, oil pump 10, lockup clutch 12, shock-absorbing spring 13, shift clutch 16, input shaft 38, locking platen 42 compositions such as grade, wherein the hub splines 23 in the shift clutch 16 links to each other with input shaft 38, outer shroud 19 links to each other with turbine 5, ring 11 on the turbine 5 is connected with lockup clutch 12 by shock-absorbing spring 13, and shift clutch 16 selectively connects and break away from the power of turbine 5 and input shaft 38.Lockup clutch 12 can be connected with fluid torque converter housing 3 by friction plate 15 under the oil pressure effect, makes turbine 5 rotate 50 one-tenth locking working staties of fluid torque converter with fluid torque converter housing 3.Lockup clutch 12 also can make fluid torque converter housing 3 and turbine 5 break away under the oil pressure effect, makes its independent rotation separately, 50 one-tenth release working staties of fluid torque converter.Shift clutch 16 are motors 41 with mechanical gear box 43 between unique driving be connected, promptly turbine 5 is connected with unique driving between the input shaft 38.Lockup clutch 12 and gear shift sleeve 16 can independently separately be controlled, to adapt to different operating mode needs.Shift clutch 16 and lockup clutch 12 radially arranged superposed on turbine 5.Pump impeller 4 connects pump impeller flange 40, and pump impeller flange 40 drives oil pump 10, and links to each other with oil sources 26 by oil duct plate 27.
Consisting of of shift clutch 16, outside friction disc 17 outer ends are with spline and 19 inner connections of outer shroud, outer shroud 19 is fixed on the turbine 5, outside friction disc 17 can move radially on outer shroud 19, interior friction plate 18 the inners are connected with hub splines 23 with spline, outside friction disc 17 and interior friction plate 18 alternate layouts, hub splines 23 links to each other with input shaft 38.Cylinder body 20 is fixing with turbine 5, and piston 21 moves to left under by the gallery pressure effect on the wheel stand 8 and compresses outside friction disc 17 and interior friction plate 18 on cover plate 24, turbine 5 transferring power that links to each other with input shaft 38.Piston 21 oil pocket emptyings move to right piston 21 under dish-shaped return spring 22 effects, and outside friction disc 17 is separated with interior friction plate 18, and turbine 5 is thrown off power with input shaft 38.In shift clutch 16 joints and separation process, lubricant oil enters lubricant reservoir 37 by oil leab 34, lubricating cylinders hydraulic fluid port 31 and piston oil slot 33.
Consisting of of lockup clutch 12, locking platen 42, shock-absorbing spring 13 and shock-absorbing spring shell 44 fuse by rivet.Lockup clutch 12 can move axially on turbine 5, and can constitute passage or two each self-enclosed Seal cages by seal ring 14 and friction plate 15.Connect a ring 11 on the turbine 5, the shock-absorbing spring of stirring on the lockup clutch 12 by ring 11 13 is connected with lockup clutch 12.The right chamber 36 of lockup clutch moves to left lockup clutch 12 and presses to friction plate 15 under the oil pressure effect, and turbine 5 is rotated with fluid torque converter housing 3, makes 50 one-tenth locking working staties of fluid torque converter.Lockup clutch left side chamber 35 oil-feeds, under the oil pressure effect, lockup clutch 12 is moved to right, chamber 35, a lockup clutch left side connects with the right chamber 36 of lockup clutch, turbine 5 is thrown off with fluid torque converter housing 3 to be connected, fluid torque converter housing 3 and turbine 5 are broken away from, form independent rotation separately, 50 one-tenth release working staties of fluid torque converter this moment.
Pump impeller 4 connects pump impeller flange 40, and pump impeller flange 40 drives oil pump 10, and links to each other with oil sources 26 by oil duct plate 27.Oil pump 10 is a crescent gear pump, and oil pump 10 links into an integrated entity with oil duct plate 27, and oil duct plate 27 links to each other with oil sources 26.All oil ducts that link to each other with oil sources 26 all are integrated on the oil duct plate 27, and the oil duct that enters fluid torque converter 50 circumferentially distributes at the annular circumferential face that oil duct plate 27 combines with wheel stand 8, and oil duct plate 27 and wheel stand 8 interference fit, play seal action.
All oil ducts all place wheel stand 8 inwalls, have selenodont control and oil leab on wheel stand 8 inwalls, and by stuffing box gland 25 sealings.The control oil of oil sources 26 is connected with wheel stand 8 by oil duct plate 27, is assigned to each control oil pocket by the oil duct on the wheel stand 8 again.
This programme is how to design around the torque-converters layout for solving two clutches, and its technical characteristics is:
A. adopt double clutch construction, with lockup clutch 12 and gear shift sleeve 16 radially arranged superposed on turbine 5, make compact structure;
B., shock-absorbing spring 13 is installed in the lockup clutch 12, is played buffering, damping effect, can improve the smoothness of joint;
C. gear shift sleeve 16 adopts sliding bush type recloser holes, gear shift sleeve 16 is engaged and separation process in have lubricant oil to pass through, take away the heat of generation, prevent to burn sheet and raising friction plate working life; When thoroughly separating, the lubricating oil inlet is closed, lubricant oil is thrown out of under centrifugal action in the lubricant reservoir 37, reduced the thickness resistance between outside friction disc 17 and the interior friction plate 18, the rotary inertia of input shaft 38 reduces, and makes the raising in working life of smoothness of pick-up and the synchronizer and the gear of AMT gear shift;
D. pump impeller 4 directly drives oil pump 10 by pump impeller flange 40 and rationally utilizes the space, and oil pump 10 fuses with oil duct plate 27, and oil duct plate 27 links to each other with oil sources 26.All oil ducts that link to each other with oil sources 26 all are integrated into oil duct plate 27, enter the circumferential distribution of ring surface that the oil duct of fluid torque converter 50 combines with wheel stand 8 at oil duct plate 27, and oil duct plate 27 and wheel stand 8 interference fit play seal action, also are convenient to make and install;
E. all oil ducts that enter fluid torque converter 50 all place on wheel stand 8 inwalls, make compact structure.
Description of drawings
Fig. 1 is the torque-converters schematic diagram with double clutch;
Wherein: 1-bent axle, 3-fluid torque converter housing, 4-pump impeller, 5-turbine, the unidirectional freewheel of 6-guide wheel 7-, the 8-wheel stand, 10-oil pump, 12-lockup clutch, 13-shock-absorbing spring, 16-shift clutch, the 38-input shaft, 41-motor 42-locking platen, 43-gearbox, 50-fluid torque converter
Fig. 2 is the torque-converters overall structure figure with double clutch;
Wherein: the 1-bent axle, 2-crosses scale, 3-fluid torque converter housing, 4-pump impeller, 5-turbine, the unidirectional freewheel of 6-guide wheel 7-, 8-wheel stand, 9-torque-converters case, 10-oil pump.11-ring 12-lockup clutch, 13-shock-absorbing spring, 14-seal ring, 15-friction plate 16-shift clutch, friction plate in the 17-outside friction disc, 18-, 19-outer shroud 20-cylinder body, 21-piston, 22-dish return spring, the 23-hub splines, 24-cover plate, 25-stuffing box gland, the 26-oil sources, 27-oil duct plate, 28-hydraulic fluid port, 29-cylinder body hydraulic fluid port 30-oil duct, 31-lubricating cylinders hydraulic fluid port, 33-piston oil slot 34-oil leab, chamber, a 35-lockup clutch left side, the right chamber of 36-lockup clutch, the 37-lubricant reservoir, 38-input shaft, 40-pump impeller flange, 42-locking platen, the 50-fluid torque converter.
Fig. 3 is the local amplification assumption diagram of torque-converters with double clutch;
Wherein: 3-fluid torque converter housing, 5-turbine, 8-wheel stand, 11-ring, the 12-lockup clutch, 13-shock-absorbing spring, 14-seal ring, the 15-friction plate, 16-shift clutch, 17-outside friction disc, friction plate in the 18-, 19-outer shroud, 20-cylinder body, the 21-piston, 22-dish return spring, 23-hub splines, the 24-cover plate, 25-stuffing box gland, 29-cylinder body hydraulic fluid port, the 30-oil duct, 31-lubricating cylinders hydraulic fluid port, 32-lubricating oil return road, the 33-piston oil slot, 34-oil leab, chamber, a 35-lockup clutch left side, the right chamber of 36-lockup clutch, 37-lubricant reservoir, 38-input shaft, the 39-thrust bearing, 42-locking platen, 44-shock-absorbing spring shell
Fig. 4 is the torque-converters oil duct connection diagram with double clutch.
Wherein: 8-wheel stand, 10-oil pump, 25-stuffing box gland, 26-oil sources, 27-oil duct plate, 34-oil leab, 40-flange pump impeller, 45-oil pump cover
Beneficial effect: the utility model is according to automobile market is set to the widespread demand of automatic speed-changing system at present Meter has low cost of manufacture, and investment for trnasforming urban land is few, and risk is little, and benefit is big, and performance improves the advantages such as remarkable.
Embodiment
1) vehicle start: stationary vehicle, gearbox 43 is in neutral gear, gear shift sleeve 16 is in separated state, ato unit 41, motor 41 power drive pump impeller 4 by bent axle 1 and drive oil pump 10, the control valve of oil sources 26 makes gear shift sleeve 16 keep separated state, input shaft 38 disconnects with motor 41 power, the control valve of oil sources 26 is separated lock control oil by oil duct plate 27 with lockup clutch 12 simultaneously, wheel stand 8, oil duct 30 enters chamber 35, a lockup clutch left side, promoting lockup clutch 12 moves to right, control oil continues to enter into the right chamber 36 of lockup clutch, enter fluid torque converter 50 whole cavity volumes simultaneously, and get back to oil sources 26 by oil 28 and wheel stand 8 oil duct plates 27, and form fluid torque converter 50 release working staties, play the hydraulic moment changeable effect.Vehicle will move, earlier gearbox 43 is changed to low grade, the control valve of oil sources 26 is oily by oil duct and cylinder body hydraulic fluid port 29 on oil duct plate 27 and the wheel stand 8 with gear shift sleeve 16 combinations, pressure oil is pressed into piston cavity makes piston 21 to left translation, outside friction disc 17 and interior friction plate 18 are pressed on the cover plate 24, gear shift sleeve 16 combinations, vehicle operating.Owing to the effect of fluid torque converter 50 is arranged, makes vehicle launch steady.
2) Vehicular shift: after the vehicle operating steadily, in the time of need changing to top gear, the control valve of oil sources 26 unloads gear shift sleeve 16 separating controlling oil to get back to oil sources 26 by cylinder body hydraulic fluid port 29 and wheel stand 8, oil duct plate 27, and belleville spring 22 is pushed piston 21 to limit on the right-right-hand limit simultaneously, and gear shift sleeve 16 separates.When gear shift sleeve 16 thoroughly separates, lubricating cylinders hydraulic fluid port 31 on the cylinder body disconnects with piston oil slot 33, the lubricating oil inlet is closed, lubricant oil no longer enters lubricant reservoir 37, lubricant oil in the lubricant reservoir 37 is thrown to lubricating oil return road 32 and flows back to oil sources 26 under centrifugal action, oil in the lubricant reservoir 37 throws away and has reduced the thickness resistance between the friction plate 18 in outside friction disc and 17, and the inertia of input shaft only is the rotary inertia of input shaft 38 and hub splines 23.Half of rotary inertia when the rotary inertia of the utility model structural design only is dry clutch band driven disc, this improves property of automatic shft to AMT formula gearbox, and it is necessary and essential improving working life.After gear shift sleeve 16 thoroughly separates, gearbox 43 gear shift, after gear shift is finished, the control valve of oil sources 26 engages oil by oil duct and cylinder body hydraulic fluid port 29 on oil duct plate 27 and the wheel stand 8 with gear shift sleeve 16, make pressure oil be pressed into piston cavity, to left translation, outside friction disc 17 and interior friction plate 18 are pressed on the cover plate 24 with piston 21, gear shift sleeve 16 combinations, vehicle travels with new shelves.
3) torque converter locking and release: when vehicle according to the locking of control law needs when raising the efficiency, control oil in the oil sources 26, enter in the fluid torque converter 50 by hydraulic fluid port 28, and enter the right chamber 36 of lockup clutch, promote lockup clutch 12 and move to left, and be pressed on the friction plate 15, become one with fluid torque converter housing 3, stirring ring 11 by the shock-absorbing spring on it 13 makes turbine 5 and torque-converters housing 3 become one torque converter locking.At this moment engine power becomes mechanical transmission directly by turbine 5 and hub splines 23 outputting powers, has played the effect of raising the efficiency.In lockup clutch 12 locking processes, shock-absorbing spring 13 has a buffer function, and it is little that engaging process is impacted, and transmission of power is smooth-going, and mechanical transmission afterwards has damping effect when exercising.During lockup clutch 12 releases, the control valve of oil sources 26 is separated lock control oil with lockup clutch 12 and is entered chamber 35, a lockup clutch left side by oil duct plate 27, wheel stand 8 and oil duct 30, promoting lockup clutch 12 moves to right, control oil continues to enter the right chamber 36 of lockup clutch, enter fluid torque converter 50 whole cavity volumes simultaneously, and get back to oil sources 26 by hydraulic fluid port 28, wheel stand 8 and oil duct plate 27, and form fluid torque converter 50 release working staties, play the hydraulic moment changeable effect.
4) gear shift sleeve 16 is lubricated: in gear shift sleeve 16 combinations and the separation process, piston 21 is not all in its limit on the right-right-hand limit position, piston oil slot 33 on the piston 21 connects with lubricating cylinders hydraulic fluid port 31 at this moment, lubricant oil enters lubricant reservoir 37 and flows back to fuel tank 26 from lubricating oil return road 32 by oil leab 34, the heat that produces in gear shift sleeve 16 combinations and the separation process is taken away, prevent that friction plate from burning sheet, and improve the working life of friction plate.After gear shift sleeve 16 thoroughly separates, piston 21 is under dish-shaped return spring 22 effects, make it be in the limit on the right-right-hand limit position, piston oil slot 33 on the piston 21 is obstructed with lubricating cylinders hydraulic fluid port 31 at this moment, lubricant oil can not enter lubricant reservoir 37 by oil leab 34, and lubricant oil is thrown to lubricating oil return road 32 and flows back to fuel tank 26 in the lubricant reservoir 37 under centrifugal action simultaneously.37 lubricant oil throws away the thickness resistance that has reduced between outside friction disc 17 and the interior friction plate 18 in the lubricant reservoir.
According to the difference of driving conditions, lockup clutch 12 and gear shift sleeve 16 can independently separately be controlled, to adapt to the needs of different operating modes.
Claims (6)
1. fluid torque converter with double clutch, it by motor (41), mechanical gear box (43), bent axle (! ), pump impeller (4), turbine (5), guide wheel (6), unidirectional freewheel (7), wheel stand (8), oil pump (10), lockup clutch (12), shock-absorbing spring (13), shift clutch (16), input shaft (38), locking platen compositions such as (42), wherein the hub splines (23) in the shift clutch (16) links to each other with input shaft (38), outer shroud (19) links to each other with turbine (5), ring (11) on the turbine (5) is connected with lockup clutch (12) by shock-absorbing spring (13), it is characterized in that shift clutch (16) and lockup clutch (12) radially arranged superposed on turbine (5), pump impeller (4) connects pump impeller flange (40), pump impeller flange (40) drives oil pump (10), and links to each other with oil sources (26) by oil duct plate (27).
2. the fluid torque converter with double clutch according to claim 1, it is characterized in that, outside friction disc (17) outer end in the shift clutch (16) is connected so that spline and outer shroud (19) are inner, outer shroud (19) is fixed on the turbine (5), and outside friction disc (17) can move radially on outer shroud (19).Interior friction plate (18) is inner to be connected on the hub splines (23) with spline, outside friction disc (17) and the alternate layout of interior friction plate (18), and hub splines (23) links to each other with input shaft (38).Cylinder body (20) and turbine (5) are fixing, and piston (21) moves to left under by the gallery pressure effect on the wheel stand (8) and compresses outside friction disc (17) and interior friction plate (18) on cover plate (24), and turbine (5) links to each other with input shaft (38).
3. the fluid torque converter with double clutch according to claim 1 is characterized in that, lockup clutch (12) is fused by rivet by locking platen (42), shock-absorbing spring (13) and shock-absorbing spring shell (44).Lockup clutch (12) can move axially on turbine (5), and constitutes passage or two each self-enclosed Seal cages by seal ring (14) and friction plate (15); Turbine (5) is gone up and is connected ring (11), is connected with lockup clutch (12) through shock-absorbing spring (13).
4. the fluid torque converter with double clutch according to claim 1, pump impeller (4) is connected with pump impeller flange (40), pump impeller flange (40) drives oil pump (10), and link to each other with oil sources (26) by oil duct plate (27), it is characterized in that, oil pump (10) is a crescent gear pump, oil pump (10) fuses with oil duct plate (27), all oil ducts that link to each other with oil sources (26) all are integrated on the oil duct plate (27), the oil duct that enters fluid torque converter (50) circumferentially distributes with the annular circumferential face that wheel stand (8) combines at oil duct plate (27), and oil duct plate (27) and wheel stand (8) interference fit.
5. the fluid torque converter with double clutch according to claim 1 is characterized in that, gear shift sleeve (16) adopts sliding bush type recloser hole.
6. the fluid torque converter with double clutch according to claim 2 is characterized in that, all oil ducts all place wheel stand (8) inwall, has selenodont control and oil leab on wheel stand (8) inwall, and is sealed by stuffing box gland (25).The control oil of oil sources (26) is connected with wheel stand (8) by oil duct plate (27), is assigned to each control oil pocket by the oil duct on the wheel stand (8) again.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420011574 CN2683939Y (en) | 2004-02-20 | 2004-02-20 | Hydrodynamic torque-converter with double clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420011574 CN2683939Y (en) | 2004-02-20 | 2004-02-20 | Hydrodynamic torque-converter with double clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2683939Y true CN2683939Y (en) | 2005-03-09 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200420011574 Expired - Fee Related CN2683939Y (en) | 2004-02-20 | 2004-02-20 | Hydrodynamic torque-converter with double clutch |
Country Status (1)
| Country | Link |
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| CN (1) | CN2683939Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1327148C (en) * | 2004-02-20 | 2007-07-18 | 吉林大学 | Hydraulic pitch changing device with double-clutch |
| WO2009049514A1 (en) * | 2007-10-08 | 2009-04-23 | Haiping Liu | Mechanical-hydraulic continuously variable transmission, and the method thereof, and vehicle mechanical-hydraulic continuously variable transmission |
| CN102155527A (en) * | 2011-05-16 | 2011-08-17 | 山推工程机械股份有限公司 | Lock-type hydraulic torque converter with double clutches |
| CN103711898A (en) * | 2012-10-02 | 2014-04-09 | 福特全球技术公司 | System for supplying fluid to transmission control elements |
| CN107100979A (en) * | 2017-04-13 | 2017-08-29 | 祁晋 | A kind of new automobile fluid torque-converter and the automobile with the fluid torque-converter |
-
2004
- 2004-02-20 CN CN 200420011574 patent/CN2683939Y/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1327148C (en) * | 2004-02-20 | 2007-07-18 | 吉林大学 | Hydraulic pitch changing device with double-clutch |
| WO2009049514A1 (en) * | 2007-10-08 | 2009-04-23 | Haiping Liu | Mechanical-hydraulic continuously variable transmission, and the method thereof, and vehicle mechanical-hydraulic continuously variable transmission |
| CN101408244B (en) * | 2007-10-08 | 2010-12-01 | 刘海平 | Mechanical hydraulic stepless speed changer and method and vehicle mechanical hydraulic stepless speed changer |
| CN102155527A (en) * | 2011-05-16 | 2011-08-17 | 山推工程机械股份有限公司 | Lock-type hydraulic torque converter with double clutches |
| CN103711898A (en) * | 2012-10-02 | 2014-04-09 | 福特全球技术公司 | System for supplying fluid to transmission control elements |
| CN107100979A (en) * | 2017-04-13 | 2017-08-29 | 祁晋 | A kind of new automobile fluid torque-converter and the automobile with the fluid torque-converter |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |