CN102359516A - High-power low-speed clutch with synchronous mechanism - Google Patents
High-power low-speed clutch with synchronous mechanism Download PDFInfo
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- CN102359516A CN102359516A CN2011102629495A CN201110262949A CN102359516A CN 102359516 A CN102359516 A CN 102359516A CN 2011102629495 A CN2011102629495 A CN 2011102629495A CN 201110262949 A CN201110262949 A CN 201110262949A CN 102359516 A CN102359516 A CN 102359516A
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- end gear
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- clutch
- lock pin
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- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a high-power low-speed clutch with a synchronous mechanism. Outer splines which are connected with inner splines of a sliding gear are arranged outside a driving end gear and a driven end gear respectively; a pressing block is arranged in one end of the sliding gear; a friction mechanism is arranged between the pressing block and the driven end gear; a piston and the driving end gear are slidably connected in the other end of the sliding gear through the inner splines from inside to outside in sequence; the driving end gear passes through the piston through a locking pin to be connected with the pressing block; a step of the locking pin is provided with a tapered corner and is in contact with a taper hole of the piston; a clutch connecting and tripping oil chamber is formed between the driving end gear and the piston; and an oil hole which is communicated with the clutch connecting and tripping oil chamber is formed in the driving end gear. The clutch can realize that a driving end and a driven end of a shafting are connected with and tripped from the clutch in a rotation speed difference range of 60r/min; transfer of torque of the shafting in the rotation speed of 200r/min by a metal tooth is realized after joint; and the clutch has the characteristics of wide connecting or tripping range, convenience in operation, compact structure, high power density and the like, and is particularly suitable for a ship power transmission system of a low-speed high-torque shafting.
Description
Technical field
The present invention relates to the clutch in a kind of ship power transmission system, especially a kind of high-power low-speed clutch.
Background technique
The clutch of ship power transmission system mainly contains pneumatic tyre friction clutch, tooth inserted tooth formula clutch and SSS clutch, is applied to the preceding two types of clutches of being mainly of low-speed big occasion at present.
Pneumatic tyre friction clutch typical products is the Airflex VC of EATON company type pneumatic tyre friction clutch and CB type pneumatic tyre friction clutch.Maximum Torque 633kNm, the diameter 2100mm of VC type pneumatic tyre friction clutch.Friction clutch have transmitting torque big, connect and take off steadily, handle characteristics such as rapid, being suitable for big-and-middle-sized boats and ships and general industry axle is that transmission system is used.But, the be bullied restriction of tire pressure and friction plate friction factor of pneumatic tyre friction clutch, its structure weight is often bigger, has limited it and has arranged application that the compact field sympodium is fastened in the cabin.
Tooth inserted tooth formula clutch has compact structure, characteristics that specific power is high, and is general under static or extremely low speed discrepancy, connects through manual mode and takes off.To take off the speed discrepancy scope little because it connects, and can not connect automatically and take off, and influenced the mobility of marine shafting powershift, brought unfavorable and restriction therefore for the application of tooth inserted tooth formula clutch.
Summary of the invention
The present invention will solve the naval vessel joins the automatic conversion of synchronization of tooth-like joint to the low-speed big clutch friction technical problem; Improve engaging rotating speed scope and the specific power of naval vessel, and a kind of high-power low-speed clutch with lazy-tongs is provided with the low-speed big clutch.
For realizing above-mentioned purpose; Technological scheme of the present invention is: a kind of high-power low-speed clutch with lazy-tongs; Mainly form by driven end gear, sliding gear, compact heap, steel disc, friction plate, lock pin, piston, drive end gear; Be characterized in: sliding gear is provided with internal spline in the two ends; The drive end gear is respectively equipped with the external splines that is connected with the sliding gear internal spline outward with the driven end gear, in sliding gear one end compact heap is housed, and between compact heap and the driven end gear friction mechanism is housed; Through internal spline from inside to outside be slidingly connected successively piston and drive end gear, the drive end gear passes piston through lock pin and is connected with compact heap in the sliding gear the other end; Lock pin is the step axle, and there is a cone angle at the step place, and contacts with the piston taper hole through cone angle, is provided with clutch between drive end gear and the piston and connects the de-oiling chamber, has oilhole in the drive end gear shaft, and oilhole connects the de-oiling chamber with clutch and is connected.
The drive end gear is connected with the power input device, and the driven end gear is connected with motive power outputting apparatus.
Friction mechanism is made up of friction plate and steel disc, and friction plate is installed in through inner splined hole on the male splined shaft of driven end gear, and steel disc is installed on the inner splined hole of compact heap through external splines.
Lock pin quantity is 12 or 16, and between compact heap and drive end gear, circumferentially is uniformly distributed with, and the lock pin two ends are individually fixed in the mounting hole of compact heap and drive end gear.
The step axle path of lock pin is less than piston mounting hole diameter, the big footpath of lock pin step axle and piston mounting hole equal diameters.
Beneficial effect of the present invention:
The present invention adopts friction mechanism, lock pin lazy-tongs and tooth-like structure.The lock pin lazy-tongs can be realized the automatic conversion of clutch from frictional engagement to tooth-like joint.Clutch set inside of the present invention the pressurization of hydraulic jack to friction structure, lazy-tongs and tooth-like structure, easy to operate.
Clutch among the present invention can realize that the driven termination of axle owner is taken off in the 60r/min speed discrepancy scope; Engaging the axle of realizing that metal-toothed is transmitted in the 200r/min rotating speed in the back is moment of torsion; Have characteristics such as connecing the scope of taking off is wide, handiness, compact structure, specific power height, be specially adapted to the ship power transmission system of low-speed big axle system.
Description of drawings
Fig. 1 is a structure sectional view of the present invention.
Embodiment
Below in conjunction with accompanying drawing and embodiment the present invention is further described.
As shown in Figure 1, the high-power low-speed clutch of band lazy-tongs of the present invention mainly is made up of driven end gear 1, sliding gear 2, compact heap 3, steel disc 4, friction plate 5, lock pin 6, piston 7, drive end gear 8 etc.
In sliding gear 2 one ends compact heap 3 is housed, between compact heap 3 and the driven end gear 1 friction mechanism is housed; Through internal spline from inside to outside be slidingly connected successively piston 7 and drive end gear 8, drive end gear 8 passes piston 7 through lock pin 6 and is connected with compact heap 3 in sliding gear 2 the other ends.
Drive end gear 8 connects with the power input device, and driven end gear 1 is connected with motive power outputting apparatus.Friction mechanism and lazy-tongs etc. are arranged on sliding gear 2 inside.
Drive end gear 8 is the external splines structural type, and sliding gear 2 is the internal spline structural type, mounted in pairing mode, and through the spline transmitting torque.Piston 7 is installed in the internal spline of sliding gear 2 one ends, can promote sliding gear 2 and on drive end gear 8, move axially.
Driven end gear 1 is the external splines structural type, and sliding gear 2 is the internal spline structural type, and two ends are handled through correction of the flank shape.Under the throw-out-of clutch state, driven end gear 1 axially has certain spacing with sliding gear 2.During joint, sliding gear 2 is realized axial mating engagement with moved end gear 1, and sliding gear 2 can move axially on driven end gear 1.
Have two oilholes in the drive end gear 8, lead to drive end gear 8 respectively and connect the de-oiling chamber with the clutch that piston 7 constitutes.The thrust that engages the oil pocket generation realizes that the pressurization of friction structure and driven end gear 1 axially mesh with sliding gear 2.
Working principle of the present invention:
When clutch; Oil cylinder engages the oil pocket oil-feed, and lock pin 6 relative pistons 7 circumferentially rotate back cone angle contact, and piston 7 cone angles promote compact heap 3 pressurizations through lock pin 6 cone angles; Steel disc 4 is realized the flexible engagement of clutch principal and subordinate moved end with friction plate 5, and driven end gear 1 rotating speed rises.When clutch rotational speed synchronous; After the control oil pressure continued to rise, lock pin 6 set right with respect to piston 7 holes, and lock pin 6 is freed with piston 7 cone angles; Piston 7 drives sliding gears 2 direction of engagement and moves axially and realize and the engaging of driven end gear 1 that oil pressure unloads automatically on the friction plate 5 at this moment.After tooth clutch engaged, clutch rotational speed rose, and can transmit rated torque.
The high-power low-speed clutch of band lazy-tongs is realized automatic joint by the hydraulic control mode.When throw-out-of clutch, oil cylinder is thrown off the oil pocket oil-feed, and piston 7 drives sliding gear 2 and breaks away from the disengaging that direction moves axially realization and driven end gear 1.
Claims (5)
1. high-power low-speed clutch with lazy-tongs; Mainly form by driven end gear (1), sliding gear (2), compact heap (3), steel disc (4), friction plate (5), lock pin (6), piston (7) and drive end gear (8); It is characterized in that: said sliding gear (2) is provided with internal spline in the two ends; Drive end gear (8) and the outer external splines that is connected with sliding gear (2) internal spline that is respectively equipped with of driven end gear (1); In sliding gear (2) one ends compact heap (3) is housed, between compact heap (3) and the driven end gear (1) friction mechanism is housed; Through internal spline from inside to outside be slidingly connected successively piston (7) and drive end gear (8), drive end gear (8) passes piston (7) through lock pin (6) and is connected with compact heap (3) in sliding gear (2) the other end; Lock pin (6) is the step axle; There is a cone angle at the step place; And contact with piston (7) taper hole through cone angle; Be provided with clutch between drive end gear (8) and the piston (7) and connect the de-oiling chamber, have two oilholes in the drive end gear (8), and two oilholes connect the de-oiling chamber with clutch respectively and are connected.
2. the high-power low-speed clutch of band lazy-tongs according to claim 1 is characterized in that: said drive end gear (8) is connected with the power input device, and said driven end gear (1) is connected with motive power outputting apparatus.
3. the high-power low-speed clutch of band lazy-tongs according to claim 1; It is characterized in that: said friction mechanism is made up of friction plate (5) and steel disc (4); Friction plate (5) is installed in through inner splined hole on the male splined shaft of driven end gear (1), and steel disc (4) is installed on the inner splined hole of compact heap (3) through external splines.
4. the high-power low-speed clutch of band lazy-tongs according to claim 1; It is characterized in that: said lock pin (6) quantity is 12 or 16; And between compact heap (3) and drive end gear (8), circumferentially be uniformly distributed with, lock pin (6) two ends are individually fixed in the mounting hole of compact heap (3) and drive end gear (8).
5. the high-power low-speed clutch of band lazy-tongs according to claim 1 is characterized in that: the step axle path of said lock pin (6) is less than piston (7) mounting hole diameter, the big footpath of lock pin (6) step axle and piston (7) mounting hole equal diameters.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102629495A CN102359516A (en) | 2011-09-07 | 2011-09-07 | High-power low-speed clutch with synchronous mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011102629495A CN102359516A (en) | 2011-09-07 | 2011-09-07 | High-power low-speed clutch with synchronous mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102359516A true CN102359516A (en) | 2012-02-22 |
Family
ID=45584883
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011102629495A Pending CN102359516A (en) | 2011-09-07 | 2011-09-07 | High-power low-speed clutch with synchronous mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102359516A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023110007A1 (en) * | 2021-12-13 | 2023-06-22 | Schaeffler Technologies AG & Co. KG | Clutch comprising a double-acting piston, and axially elastic end stop disc for a sliding sleeve |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3071224A (en) * | 1959-09-16 | 1963-01-01 | Dynetics | High speed synchronizing clutch |
| CN101365892A (en) * | 2005-12-23 | 2009-02-11 | 阿瑟·诺尔斯 | Drive engagement apparatus |
| CN202274016U (en) * | 2011-09-07 | 2012-06-13 | 中国船舶重工集团公司第七〇四研究所 | Large-power low-speed clutch with synchronization mechanism |
-
2011
- 2011-09-07 CN CN2011102629495A patent/CN102359516A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3071224A (en) * | 1959-09-16 | 1963-01-01 | Dynetics | High speed synchronizing clutch |
| CN101365892A (en) * | 2005-12-23 | 2009-02-11 | 阿瑟·诺尔斯 | Drive engagement apparatus |
| CN202274016U (en) * | 2011-09-07 | 2012-06-13 | 中国船舶重工集团公司第七〇四研究所 | Large-power low-speed clutch with synchronization mechanism |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023110007A1 (en) * | 2021-12-13 | 2023-06-22 | Schaeffler Technologies AG & Co. KG | Clutch comprising a double-acting piston, and axially elastic end stop disc for a sliding sleeve |
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| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20120222 |