CN201137650Y - Friction clutch automatic pressing device - Google Patents

Abstract

An automatic pressing device for a friction clutch belongs to the field of ship machinery. The existing structure is disengaged in forward and reverse directions, poorly connected, slipping under rated working conditions, difficult to adjust the wear gap of the friction plate, and excessive operating force. The utility model includes a driving shaft, a driven shaft, two driven gears, a pressure plate, a clutch slip ring and a spline seat, and is characterized in that a pair of disks are respectively fixedly connected to the opposite axial end faces of the two driven gears. A pressure plate is provided on both sides of the spline seat, and the opposite axial end faces of the spline seat and the pressure plate are respectively provided with pressure grooves that can be connected with each other, and pressure steel balls are arranged in the pressure grooves; friction The plate group includes the left friction plate connected to the driven gear and the right friction plate connected to the pressure plate. It has the advantages of small operating force, automatic compression and automatic compensation of wear gap, and reliable power transmission.

Description

Friction clutch automatic pressing device

【Technical field】

The utility model relates to an automatic pressing device for a friction clutch, which belongs to the field of ship machinery.

【Background technique】

In the ship power plant system below 100 horsepower, the forward and reverse rotation is mainly realized by the friction clutch. The friction plates in the clutch rely on axial pressure to generate friction, thereby forming a friction torque that transmits torque. When starting, the inertia of all driven parts has a great influence on the ability of the clutch to transmit torque, especially in the case of high speed difference, the larger the inertia of the engaged follower, the greater the inertial load. In the process of clutch engagement, if the engagement time is required to be short, the clutch must transmit greater torque, and the clutch size needs to be increased accordingly; if a clutch that only meets the workload is selected, the clutch will slip severely or the engagement time will be prolonged.

The pressing device of the mechanical clutch in the prior art is usually a pressing device using a steel ball or lever pressurized structure. The pressing force is constant during the working process, which is obtained according to the maximum load. When working below the maximum load, the pressing force is excessive, thus reducing the efficiency and life of the transmission; when exceeding the maximum load , The pressing force is not enough, causing the friction plate to slip, causing friction and affecting the normal operation of the clutch.

Due to the limitations of the inherent structure, although many improvements have been made, some commonly used mechanical clutches (such as: tangential lever compression friction clutches, steel ball compression friction clutches, etc.) still have large operating forces and force systems. Due to the disadvantages of poor performance, small overload capacity, and difficult clearance adjustment, it is difficult to meet actual needs. In the actual application process, it often occurs that the positive and negative rotation is disconnected, the connection is not smooth, the slippage is slipped under the rated working condition, the wear clearance of the friction plate is not easy to adjust, and the operating force is too large.

Therefore, it is necessary to provide a friction clutch that is reliable in engagement and has a locking device; easy to connect and disengage; easy to adjust the gap between the friction plates; the pressing force is in the axial direction, and the additional force in other directions is small; device.

【Content of utility model】

The technical problem to be solved and the technical task proposed by the utility model are to overcome the defects of the prior art and provide a function of automatic compression and automatic compensation of the wear gap, with small operating force, joint characteristics, working reserve characteristics, and automatic pressurization. A friction clutch automatic pressing device with good characteristics. For this reason, the utility model adopts following technical scheme:

The friction clutch automatic compression device includes two driven gears respectively sleeved on the driving shaft and the driven shaft, a plurality of friction plate sets, a pressure plate and a spline seat fixed on the driven shaft. The outer periphery of the spline seat is equipped with a clutch slip ring that can move in the axial direction, and it is characterized in that a pair of disk springs are fixedly connected to the opposite axial end faces of the two driven gears; the spline seat There is a pressurizing plate on both sides, and the opposite axial end surfaces of the spline seat and the pressurizing plate are respectively provided with pressurizing grooves that can be connected with each other, and pressurizing steel balls are arranged in the pressurizing grooves; the two sets of pressurizing There is a set of friction plates between the disk and the disc spring respectively, and the set of friction plates includes a left friction plate and a right friction plate, the left friction plate is connected to the driven gear, and the right friction plate is connected to the pressure plate. The aforementioned structure combines the steel ball rolling pressurization structure with the disc spring to form a composite friction clutch automatic pressing device. By turning the slip ring of the clutch, the separation and cooperation of the left and right friction plates are controlled, combined with the rotation direction of the pressure plate and the spline seat and the cooperation of the steel ball and the pressure groove, it can not only generate a large pressing force, but also It can realize axial automatic compression and automatic compensation of wear gap, and the characteristics of combination, working reserve and automatic pressure are good.

For the perfection and supplement of the above technical solutions, the following technical features can be added:

The clutch slip ring is provided with spiral grooves evenly distributed along the circumference.

One end of the pressure groove is shallow and the other end is deep, and the direction of the pressure grooves of the spline seat and the pressure plate is opposite. Relying on the helix angle of the spiral groove on the clutch slip ring and the wedging angle (angle) formed between the shallow end and the high end of the pressure groove on the pressure plate, it can realize automatic compression and automatic compensation of the wear gap of the friction plate in the engaged state. Function, small operating force, highlighting good joint characteristics, working reserve characteristics, and automatic pressurization characteristics.

The two pressure plates are connected through double-ring springs arranged on opposite axial end faces.

A plurality of positioning pins are evenly distributed on the radial end surface of the spline seat. For use with clutch slip rings.

The driven gear is respectively socketed with the drive shaft and the driven shaft through needle bearings. When the clutch slip ring is in the middle position, the friction plate is in a idling state and does not transmit torque.

The utility model makes the operation force of clutch disengagement and connection small, and has the functions of automatic compression and automatic compensation of the wear gap. When the load increases, the axial pressing force of the friction plate is increased, and the power transmission is reliable.

【Description of drawings】

Fig. 1 is the sectional structure schematic diagram of the present utility model;

Fig. 2 is the side view structural representation of the utility model;

Fig. 3 is the side view structural representation of the clutch slip ring in the utility model;

Fig. 4 is the sectional structure schematic diagram of clutch slip ring in the utility model

Fig. 5 is a side view structural schematic diagram of the pressure plate in the utility model;

Fig. 6 is a schematic cross-sectional structure diagram of the pressure plate in the utility model;

Fig. 7 is another side view structural schematic diagram of the pressure plate in the utility model;

Fig. 8 is a partial cross-sectional view taken along line A-A of Fig. 7 .

In the figure: 1. Spline seat, 2. Clutch slip ring, 3. Pressure steel ball, 4. Pressure plate, 5. Friction plate group, 5a, left friction plate, 5b, right friction plate, 6. Disc spring , 7, driven gear, 8, needle bearing, 9, driven shaft, 10, positioning pin, 11, driving shaft, 12, double-ring spring, 13, pressure groove, 14, spiral groove, γ, helix angle, λ, wedge angle.

[specific implementation method]

The substantive features of the present utility model will be further described below in conjunction with the accompanying drawings and specific embodiments.

As shown in Figures 1, 2, 3, and 7, the friction clutch automatic pressing device includes two driven gears 7 and a plurality of friction plates that are respectively sleeved on the driving shaft 11 and the driven shaft 9 through needle bearings 8. Group 5, pressure plate 4 and spline seat 1 fixed on the driven shaft 9, the outer periphery of the spline seat 1 is equipped with a clutch slip ring 2 that can move in the axial direction, and its two driven gears 7 are opposite to each other. A pair of disk springs 6 are fixedly connected to the axial end surfaces of the two; a pressure plate 4 is respectively provided on both sides of the spline seat 1, and a pressure plate 4 is respectively provided on the opposite axial end surfaces of the spline seat 1 and the pressure plate 4. Pressure groove 13, pressure steel ball 3 is arranged in pressure groove 13; There is a friction plate group 5 between two groups of pressure plates 4 and disc spring 6 respectively, and friction plate group 5 includes left friction plate 5a and right friction plate Plate 5b, the left friction plate 5a is connected on the driven gear 7, and the right friction plate 5b is connected on the pressure plate 4. Three helical grooves 14 are evenly distributed on the circumference of the clutch slip ring 2 . One end of the pressure groove 13 is shallow and the other end is deep, and the direction of the pressure groove 13 of the spline seat 1 and the pressure plate 4 is opposite. The two pressure discs 4 are connected by double-ring springs 12 arranged on opposite axial end faces. Three positioning pins 10 are evenly distributed on the radial end surface of the spline seat 1 .

The inner and outer friction plates can be cast by steel-copper base powder metallurgy.

As shown in FIG. 4 , the helix angle γ of the helical groove 14 on the clutch slip ring 2 is 9°45'.

As shown in Figures 5 and 6, the setting position of the double ring spring 12.

As shown in Figures 7 and 8, the setting position of the pressure groove 13 on the pressure plate 4, the wedging angle λ is 30°.

When working, the left friction plate 5a and the right friction plate 5b play the role of driving the driving shaft 11 and the driven shaft 9 forward and reverse. The clutch slip ring 2 can be located in the middle position, move to the left to make the right friction plate 5b compress, and move to the right to make the left friction plate 5a compress three positions.

The clutch is in a disengaged state: the clutch slip ring 2 is in the neutral position, the clutch slip ring 2 is positioned by three positioning pins 10 in the spline seat 1 fixed on the driven shaft 9, and the driven gear 7 is positioned by the driving gear (not shown in the figure). (shown) is driven to rotate, the left friction plate 5a and the right friction plate 5b are not compressed, the supporting needle roller bearing 8 on the driven shaft 9 is idling, and the pressure plate 4 is not connected to the spline seat 1 and the driven shaft 9 turn.

When the clutch is engaged in forward rotation, the clutch slip ring 2 is moved to the right by the operating mechanism (not shown in the figure), and the clutch slip ring 2 drives the pressure plate 4 to guide and compress the left friction plate 5a, the right friction plate 5a along the spiral groove 14 thereon. The friction plate 5b combines the disk spring 6 fixed on the driven gear 7 with the left friction plate 5a, the right friction plate 5b and the pressure plate 4, and the pressure plate 4 and the spline seat 1 are formed by the pressure steel ball 3 Drive wedge tight, thereby drive driven shaft 9 to rotate together, at this moment clutch is in engaged state. As the load increases, the pressing force between the left friction plate 5a and the right friction plate 5b also increases to ensure the transmission of torque. Clutch slip ring 2 moves to the left, also same principle, realizes reverse.

The utility model relies on the helix angle γ of the spiral groove 14 on the clutch slip ring 2 and the wedging angle λ on the pressure plate 4, and has the functions of automatic compression and automatic compensation of the wear gap of the friction plate in the engaged state, and the operating force is small. It highlights the better joint characteristics, working reserve characteristics, and automatic pressurization characteristics.

Joint characteristic refers to: under static high slip conditions, the utility model combines the pressurized plate 4 with the spline seat 1, and the wedging effect of the pressurized steel ball 3 is temporarily lost, thereby entering a rigid joint state, realizing large transmission torque and joint The time is short and without slippage, eliminating the need to oversize the clutch.

During normal operation, it relies on the mutual compression between the joint elements and friction plates after contact, and uses the friction force generated after compression to transmit torque, enters a flexible joint state, reduces mechanical impact, and works smoothly. The normal working state of the utility model is flexible joint.

Working reserve characteristics: when the clutch transmits torque, it should have certain working reliability. Therefore, it is necessary to select an appropriate working reserve coefficient β in clutch design to guarantee it. The value of β is related to factors such as the prime mover, the performance of the working machine, and the structure of the clutch. If the β value is too small, the engagement time will be prolonged, the friction elements will be overheated, and the friction will be accelerated; 3 to 5 times the load. Therefore, in the initial compression state of the automatic compression friction clutch, the compression force is applied to the matched disc spring in advance by the compression positioning, and sufficient pressure is generated between the friction plates; in actual work, as the work load increases, the friction The pressing force between the plates also increases correspondingly, so that the dynamic characteristics of the clutch are in an ideal state.

The automatic pressurization feature refers to: when engaged, through the force transmission route of the clutch slip ring 2, pressurized plate 4, pressurized steel ball 3 and spline seat 1, the clutch will be automatically pressurized, the positive pressure of the friction plate will increase, and the pressure will increase. The tightening force automatically increases with the increase of the load. Selecting the appropriate β value ensures reliable operation under the rated load and ensures that the clutch is always working in an ideal state. Its advantages are no impact, no noise, and sensitive response during the reversing process. , compact structure.

The utility model can be used as a fast reversing device in a gear box, and has high reversing speed, small operating force and reliable torque transmission.

Claims (6)

1. friction clutch automatic compacting device, comprise two driven gears (7), a plurality of friction plate group (5), the pressurization disk (4) that is socketed in respectively on driving shaft (11) and the driven shaft (9) and be fixed in spline fitting (1) on the driven shaft (9), described spline fitting (1) outer periphery are combined with axially displaceable clutch slip ring (2), it is characterized in that the last relative axial end of described two driven gears (7) is connected with a pair of belleville spring (6) respectively; Described spline fitting (1) both sides are respectively equipped with a pressurization disk (4), are respectively equipped with the pressurized tank (13) that can be connected mutually on spline fitting (1) axial end relative with pressurization disk (4), are provided with pressurization steel ball (3) in the pressurized tank (13); Between described two groups of pressurization disk (4) and the belleville spring (6) a friction plate group (5) is arranged respectively, described friction plate group (5) comprises left friction plate (5a) and right friction plate (5b), left side friction plate (5a) is connected on the driven gear (7), and right friction plate (5b) is connected on the pressurization disk (4).

2. friction clutch automatic compacting device according to claim 1 is characterized in that described clutch slip ring (2) is provided with along the equally distributed spiral chute of circumference (14).

3. friction clutch automatic compacting device according to claim 1 is characterized in that described pressurized tank (13) one ends are shallow, an end is dark, and it is opposite that spline fitting (1) and both pressurized tank of pressurization disk (4) (13) are provided with direction.

4. according to claim 2 or 3 described friction clutch automatic compacting device, it is characterized in that dicyclo spring (12) connects described two pressurization disk (4) on the axial end in opposite directions by being arranged on.

5. friction clutch automatic compacting device according to claim 4 is characterized in that being evenly distributed with a plurality of locating studs (10) on the radial end face of described spline fitting (1).

6. friction clutch automatic compacting device according to claim 5, it is characterized in that described driven gear (7) by needle bearing (8) respectively with driving shaft (11) and driven shaft (9) socket.

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