CN111075855A - Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof - Google Patents

Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof Download PDF

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Publication number
CN111075855A
CN111075855A CN202010062018.XA CN202010062018A CN111075855A CN 111075855 A CN111075855 A CN 111075855A CN 202010062018 A CN202010062018 A CN 202010062018A CN 111075855 A CN111075855 A CN 111075855A
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China
Prior art keywords
pressure plate
plate
disc spring
disc
inner hub
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CN202010062018.XA
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Chinese (zh)
Inventor
楚汉昆
梁琼
岳汉奇
林志斌
高炳钊
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Qingdao Laiji Transmission System Technology Co Ltd
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Qingdao Laiji Transmission System Technology Co Ltd
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Priority to CN202010062018.XA priority Critical patent/CN111075855A/en
Publication of CN111075855A publication Critical patent/CN111075855A/en
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    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F16D13/54—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member
    • F16D13/56—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member with means for increasing the effective force between the actuating sleeve or equivalent member and the pressure member in which the clutching pressure is produced by springs only
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/644—Hub construction
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D28/00—Electrically-actuated clutches
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/20—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection for measuring, monitoring, testing, protecting or switching
    • H02K11/21—Devices for sensing speed or position, or actuated thereby
    • H02K11/22—Optical devices
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/706—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the axially movable pressure plate is supported by leaf springs

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

The invention provides a normally closed wet type multi-plate clutch, an actuating mechanism and a control method thereof, wherein in the clutch, an outer hub, a lower pressure plate, a friction component and an inner hub are sequentially installed in a sliding manner, a second disc spring is pre-tightened between the inner hub and a second pressure plate, a first disc spring is pressed between the first pressure plate and the second pressure plate, the second pressure plate is fixedly connected with the lower pressure plate penetrating through the inner hub, the first pressure plate and the second pressure plate are axially connected in a sliding manner, and a release bearing is installed in a bearing seat on the first pressure plate; in the actuating mechanism, the direct current motor drives the screw nut mechanism to move, the output end of the actuating mechanism is connected with the release bearing, and the release bearing pushes the first pressure plate to move axially under the driving of the actuating mechanism so as to control the friction assembly to compress or separate, so that the clutch is combined or separated. The invention can control the pressure between the friction plate and the steel sheet of the clutch to change stably without using a hydraulic control system.

Description

Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof
Technical Field
The invention belongs to the technical field of vehicle transmission systems, is suitable for a two-gear gearbox of a pure electric vehicle, and particularly relates to a normally closed wet type multi-plate clutch, an actuating mechanism and a control method thereof.
Background
The wet-type multi-plate clutch has the advantages of stable friction coefficient, smooth engagement, low noise, small rotational inertia, long service life, low manufacturing cost, convenience in design, high applicability and the like, and is widely applied to automobile transmission systems AT present, wherein the wet-type multi-plate clutch comprises transmission system parts such as an automobile Automatic Transmission (AT), a double-clutch transmission (DCT/DSG), a four-wheel drive system central differential and the like. The motor is used as a power source of the pure electric vehicle, the working rotating speed is higher than the rotating speed of a common engine, and compared with a dry diaphragm spring clutch, the wet multi-plate clutch with the advantages has more remarkable advantages when being applied to the pure electric vehicle.
As shown in fig. 1, the pressing force of the conventional normally closed diaphragm spring clutch is provided by a diaphragm spring a with a release finger, and a diaphragm spring release bearing b pressed on the release finger moves axially to push the release finger of the diaphragm spring a to displace so as to realize the engagement and the disengagement of the clutch. The diaphragm spring release bearing b is fitted over the drive shaft d or the release sleeve c on the drive shaft, so that the minimum radial dimension of the diaphragm spring release bearing b is limited. Under the condition of transmitting the same torque, compared with a diaphragm spring clutch, the radial size of the multi-plate clutch is small, if a diaphragm spring is used as a pressing element, the stress point of a diaphragm spring separation finger is far away from an axis, the arrangement on the space is unreasonable, and the supporting point of the diaphragm spring is relatively difficult to arrange. Furthermore, since the release bearing has a large axial dimension, the axial dimension of the multi-plate clutch is increased in use, resulting in a large axial dimension of the transmission case.
The combination and separation of the existing wet-type multi-plate clutch are generally controlled by hydraulic pressure, and a hydraulic control system is composed of a mechanical oil pump or an electronic oil pump, an energy accumulator, a pressure control valve, an electromagnetic valve and the like. The hydraulic control system can control the pressing force of the clutch to change stably, and also has the function of gear selecting and shifting of the gearbox, so as to provide power for the gear selecting and shifting actuating mechanism. At present, most pure electric automobile two-gear gearboxes do not need to select and shift gears. For example, in the patent CN201610473243.6, an electric vehicle non-power-interruption shifting transmission and a shifting control method thereof, a pure electric vehicle two-gear transmission is proposed, which does not need a shifting mechanism. Under the condition of no need of a gear selecting and shifting mechanism, a hydraulic driving system is established to independently provide power for the multi-plate clutch actuating mechanism, the cost is relatively high, and the cost performance is low.
Disclosure of Invention
In view of the defects in the prior art, the invention provides a normally closed wet type multi-plate clutch, an actuating mechanism and a control method thereof, which can control the pressure between a clutch friction plate and a steel plate to change stably under the condition of not using a hydraulic control system. The technical scheme of the invention is as follows by combining the attached drawings of the specification:
a normally closed wet type multi-plate clutch is composed of an outer hub 1, a first thrust bearing 2, a lower pressing plate 3, a friction component, an inner hub 6, a second disc spring 7, a second pressing plate 8, a first disc spring 9, a first pressing plate 10 and a release bearing 11;
the outer hub 1, the lower pressing plate 3 and the inner hub 6 are sequentially arranged on an input shaft 26 of the gearbox, the first thrust bearing 2 is arranged between the outer hub 1 and the inner hub 6, the friction assembly is arranged between the lower pressing plate 3 and the inner hub 6, the circumferential inner side of the friction assembly is relatively fixed with the outer hub 1 in the circumferential direction, and the circumferential outer side of the friction assembly is relatively fixed with the inner hub 6 in the circumferential direction;
the inner hub 6 is fixed on the input shaft 26 of the gearbox, and the lower pressure plate 3 is connected with the inner hub 6 in a sliding mode along the axial direction;
a second disc spring clamping jaw of the second disc spring 7 is clamped on the circumferential outer edge of the inner hub 6, an upright post 3A is arranged on the lower pressure plate 3, and the second pressure plate 8 is fixedly connected with the upright post 3A penetrating through the inner hub 6 through a first fastening bolt 13, so that the second disc spring 7 is pre-tightened between the inner hub 6 and the second pressure plate 8;
a first disc spring clamping jaw of the first disc spring 9 is clamped on the circumferential outer edge of the second pressure plate 8, the first pressure plate 10 is connected with the second pressure plate 8 through a shoulder bolt 14, so that the first disc spring 9 is pressed between the first pressure plate 10 and the second pressure plate 8, and the first pressure plate 10 axially slides relative to the shoulder bolt 14;
the release bearing 11 is installed in a bearing seat arranged in the center of the first pressure plate 10, and the release bearing 11 pushes the first pressure plate 10 to slide along the axial direction under the action of external force.
Further, the friction assembly consists of friction plates 4 and steel sheets 5 which are sequentially staggered and stacked;
rectangular teeth are uniformly arranged on the outer side of the circumference of the friction plate 4 along the radial direction, and the friction plate 4 is axially and slidably arranged in a rectangular tooth groove formed in the side wall of the outer hub 1 through the rectangular teeth;
rectangular teeth are uniformly arranged on the inner side of the circumference of the steel sheet 5 along the radial direction, and the steel sheet 5 is axially and slidably arranged in a rectangular tooth socket formed on the outer side of the side wall of the inner hub 6 through the rectangular teeth;
the outermost friction plate 4 positioned on one side of the outer hub 1 is in sliding and grinding contact with an annular boss on a bottom plate of the lower pressing plate 3;
the outermost friction plate 4 positioned on one side of the inner hub 6 is in sliding contact with the annular outer edge plate of the inner hub 6;
under the axial sliding of the lower pressure plate 3 and the inner hub 6, the friction plates 4 are pressed or separated from the steel sheets 5, so that the transmission or the interruption of the power between the inner hub 6 and the outer hub 1 is realized.
Further, the first disc spring 9 and the second disc spring 7 are in the shape of conical discs with the same structure, and the ratio of the height of the inner cone of the first disc spring 9 to the thickness of the second disc spring 7 in a free state is larger than that of the inner cone of the second disc spring 7 in a free state
Figure BDA0002374794610000021
Furthermore, the end face of the outer hub 1 is provided with a positioning hole for being matched and positioned with an external flange and a bolt hole for being fixedly connected with the external flange, and the outer hub 1 is matched and connected with the external flange to transmit the power transmitted by the friction assembly outwards.
Furthermore, the center of the inner hub 6 is a base provided with a central hole, the inner side wall of the central hole of the base is provided with a spline groove, the base of the inner hub 6 is in matched connection with an external spline at the shaft end of the transmission input shaft 26, so that the inner hub 6 rotates synchronously with the transmission input shaft 26, one end of the base of the inner hub 6 penetrates through the central hole of the bottom plate of the lower pressure plate 3 and is directly pressed on the end surface of the outer hub 1 through the first thrust bearing 2, and the other end of the base of the inner hub 6 is axially fixed in the snap spring groove on the external spline of the transmission input shaft 26 through the first snap spring 27, so that the inner hub 6 is axially fixed;
the inner hub 6 extends from the axial middle position of the outer side wall of the base to the circumferential outer side to form an annular bottom plate, a plurality of unthreaded holes are uniformly formed in the annular bottom plate along the circumferential direction, and the upright columns 3A of the lower pressing plate 3 penetrate through the unthreaded holes in the annular bottom plate of the inner hub 6 in a one-to-one correspondence manner;
the outer edge of the annular bottom plate of the inner hub 6 extends rightwards along the axial direction to form a cylindrical side wall, the surface of the outer side wall of the cylindrical side wall is provided with a plurality of rectangular tooth grooves arranged along the axial direction, and the outer side of the cylindrical side wall of the inner hub 6 is in sliding connection with the rectangular teeth on the inner side of the lower pressing plate 3 through the rectangular tooth grooves;
the outer edge of the annular outer edge plate of the inner hub 6 is provided with a circle of annular boss, a plurality of second disc spring clamping grooves are uniformly formed in the radial inner side of the annular boss, and the second disc spring clamping claws of the second disc springs 7 are correspondingly clamped in the second disc spring clamping grooves one by one.
Further, the second pressure plate 8 is a circular plate with a central hole, a plurality of through holes corresponding to the upright posts 3A one by one are uniformly formed in the circumferential direction of the central hole of the second pressure plate 8, and the first fastening bolts 13 penetrate through the through holes to be in threaded connection with the upright posts 3A;
a circle of annular boss is arranged on the outer edge of the circumference of the end face of the second pressure plate 8 matched with the first disc spring 9, a plurality of first disc spring clamping grooves are uniformly formed in the radial inner side of the annular boss, and the first disc spring clamping claws of the first disc spring 9 are correspondingly clamped in the first disc spring clamping grooves one by one;
second pressure disk 8 matches with second belleville spring 7 and opens the one side end outside and has annular groove of dodging, when second pressure disk 8 compressed tightly second belleville spring 7 to the biggest deformation along the axial, second pressure disk 8 avoided taking place to interfere with interior hub 6 through dodging the groove.
Further, the release bearing 11 is an angular contact bearing.
The actuating mechanism of the normally closed wet type multi-plate clutch consists of a direct current motor 16, a bottom plate 19, a needle bearing 20, a second thrust bearing 21, a second snap spring 22, a guide plate 23, a trapezoidal lead screw 24 and a lead screw sliding sleeve 25;
a direct current motor flange 16A, a bottom plate 19 and a guide plate 23 at the output end of the direct current motor 16 are sequentially arranged and fixed on the gearbox shell 18;
one end of a trapezoidal lead screw 24 is coaxially connected with an output shaft of the direct current motor 16, an optical axis section of the trapezoidal lead screw 24 is installed in the bottom plate 19 through a needle bearing 20, the inner side of a lead screw sliding sleeve 25 is in threaded connection with a threaded shaft section of the trapezoidal lead screw 24, the outer side of the lead screw sliding sleeve 25 is installed on the inner side of the guide plate 23 in a sliding mode through a guide spline, and the lead screw sliding sleeve 25 slides linearly along the guide plate 23 under the driving of the trapezoidal lead screw 24;
the second thrust bearing 21 is arranged at a shaft shoulder between a smooth shaft section and a threaded shaft section of the trapezoidal lead screw 24, the second thrust bearing 21 is tightly pressed in an annular groove at the outer end of the bottom plate 19 under the action of the axial force of the trapezoidal lead screw 24, and the second snap spring 22 is arranged in a snap spring groove of the trapezoidal lead screw 24 and is in contact with the side surface of the bottom plate 19, so that the axial fixation of the trapezoidal lead screw 24 is realized;
the end part of the screw rod sliding sleeve 25 is connected with the release bearing 11 in a matching mode, wherein the end part of the screw rod sliding sleeve 25 is provided with a guide sleeve and a limiting shaft shoulder, an inner ring of the release bearing 11 is sleeved on the guide sleeve at the end part of the screw rod sliding sleeve 25, the end face of the inner ring of the release bearing 11 abuts against the limiting shaft shoulder at the end part of the screw rod sliding sleeve 25, and the release bearing 11 moves linearly along the axial direction under the driving of the screw rod sliding sleeve 25.
Further, the actuator further comprises a photoelectric encoder 15;
the photoelectric encoder 15 is installed at the rear end of the direct current motor 16 and used for measuring the photoelectric pulse number generated when the output shaft of the direct current motor 16 rotates;
the photoelectric encoder 15 is in signal connection with the gearbox controller, and sends the measured photoelectric pulse number generated when the output shaft of the direct current motor 16 rotates to the gearbox controller, and determines and controls the axial displacement of the release bearing 11 through the gearbox controller.
A control method of a normally closed wet type multiple disc clutch, wherein:
the combination control method of the clutch comprises the following steps:
when the first disc spring 9 and the second disc spring 7 have no external force, under the fixed connection of the first fastening bolt 13, the second disc spring 7 is pre-tightened between the second pressure plate 8 and the inner hub 6, the forces of the second disc spring 7 acting on the second pressure plate 8 and the inner hub 6 are respectively the same in magnitude and opposite in direction, wherein the force of the second disc spring 7 acting on the second pressure plate 8 is sequentially transmitted through the bolt 13 and the lower pressure plate 3 and acts on the friction assembly, under the extrusion of the acting force, the friction assembly is pressed, the acting force is finally transmitted to one end face of the inner hub 6 through the friction assembly, finally the acting force is offset with the force which is the same in magnitude and opposite in direction and acts on the other end face of the inner hub 6 by the second disc spring 7, at the moment, the normally closed wet type multi-disc clutch is in a combined state and transmits power, and the power is transmitted to the friction assembly through the inner hub 6, the friction component transmits power to the outer hub 1, and the power is finally output through an external flange plate connected with the outer hub 1;
the clutch release control method comprises the following steps:
under the action of an actuating mechanism, a release bearing 11 pushes a first pressure plate 10 to move linearly to one side of a second pressure plate 8, under the pre-tightening of a shaft shoulder bolt 14, a first disc spring 9 arranged between the first pressure plate 10 and the second pressure plate 8 generates certain deformation, along with the movement of the first pressure plate 10 to one side close to the second pressure plate 8, the deformation of the first disc spring 9 is gradually increased, the deformation force of the first disc spring 9 is also increased, the force of the first disc spring 9 acting on the second pressure plate 8 is gradually increased, the second pressure plate 8 transmits the acting force to the second disc spring 7, as the second disc spring 7 is in a pre-tightening state between an inner hub 6 and the second pressure plate 8, and the second pressure plate 8 is fixed on the inner hub 6 through a first fastening bolt 13, therefore, the acting force with the same size as the pre-tightening force of the second disc spring 7 exists on the acting surface of the first fastening bolt 13 in contact with the second pressure plate 8, when the deformation force of the first disc spring 9 is smaller than the pretightening force of the second disc spring 7, under the pretightening force of the second disc spring 7, the acting force still exists on the acting surface of the first fastening bolt 13 contacted with the second pressure plate 8, the acting force is equal to the difference between the deformation force of the first disc spring 9 and the pretightening force of the second disc spring 7, and the acting force is the pressing force between the friction plate 4 and the steel sheet 5, so when the pressing force exists between the friction components, the pressing force is the difference between the deformation force of the first disc spring 9 and the pretightening force of the second disc spring 7, the slow change of the pressing force between the friction components is realized by controlling the deformation amount of the first disc spring 9, and the separation or combination of the clutch can be accurately and smoothly controlled by an actuating mechanism;
with the continuous promotion of actuating mechanism first pressure disk 10 to second pressure disk 8 one side removal, when the deformation power that first dish spring 9 deformation produced just equals the pretightning force of second belleville spring 7, the effort on the action face that first fastening bolt 13 and second pressure disk 8 contacted is equal to zero, does not have the effort on the action face that first fastening bolt 13 and second pressure disk 8 contacted, also does not have the effort between the friction pack, and at this moment, no longer transmits friction torque between friction disc 4 and the steel sheet 5, the clutch will be in the disconnect state, the unpowered transmission of clutch.
Compared with the prior art, the invention has the beneficial effects that:
1. the normally closed wet type multi-plate clutch adopts two disc springs, wherein one disc spring is used as a pre-tightening element, and the other disc spring converts the axial displacement of an actuating mechanism into the deformation force of the spring, so that the pressing force between a friction plate and a steel plate is slowly changed, and the smooth conversion from input to output torque is realized through the normally closed wet type multi-plate clutch.
2. The actuating mechanism of the normally closed wet type multi-plate clutch adopts an electromechanical structure, a complex hydraulic system actuating mechanism is not required to be established, and the processing difficulty and the manufacturing cost of the gearbox can be greatly reduced.
3. The elastic element adopted by the normally closed wet type multi-plate clutch is a disc spring, and compared with the traditional diaphragm spring, the disc spring and the diaphragm spring have the same excellent mechanical property on the corresponding relation of deformation quantity and spring force, but the disc spring is easier to process than the diaphragm spring and has lower processing cost, and in addition, the unique mechanical property of the disc spring can ensure that the friction plate and the steel plate can be quickly separated after no sliding friction exists.
4. The release bearing adopted by the normally closed wet type multi-disc clutch is an angular contact ball bearing, and compared with the traditional release bearing, the normally closed wet type multi-disc clutch has stronger universality and lower cost; and the release bearing is arranged in the first pressure plate, so that the radial size is small, the axial size is not occupied, and the space occupied by the clutch is greatly saved.
Drawings
FIG. 1 is a schematic structural diagram of a conventional diaphragm spring clutch;
FIG. 2 is an exploded view of the normally closed wet multiplate clutch and its actuator according to the present invention;
FIG. 3 is an exploded view of an actuator of the normally closed wet multiplate clutch of the present invention;
FIG. 4 is a cross-sectional view of the normally closed wet multiplate clutch of the present invention in a compression engaged state under control of the actuator; fig. 5 is a spring force-deformation characteristic diagram of a disc spring in the normally closed wet multi-disc clutch according to the present invention.
In the figure:
a diaphragm spring, b diaphragm spring release bearing, c release sleeve and d transmission shaft;
1 outer hub, 2 first thrust bearing, 3 lower pressure plate, 4 friction plate,
5 steel sheets, 6 inner hubs, 7 second disc springs, 8 second pressure plates,
9a first disc spring, 10 a first pressure plate, 11 a release bearing, 12 an actuator,
13 first fastening bolts, 14 shaft shoulder screws, 15 photoelectric encoders, 16 direct current motors,
17 second fastening bolts, 18 transmission housing, 19 bottom plate, 20 needle bearing,
21 a second thrust bearing, 22 a second clamp spring, 23 a guide seat, 24 a trapezoidal lead screw,
25 lead screw sliding sleeves, 26 gearbox input shafts and 27 first clamp springs;
3A-upright post, 6A-second disc spring clamping groove, 7A-second disc spring clamping jaw, 8A-first disc spring clamping groove,
9A-first disc spring clamping claw, 16A-DC motor flange.
Detailed Description
For clearly and completely describing the technical scheme and the specific working process thereof, the specific implementation mode of the invention is as follows by combining the attached drawings of the specification:
for clarity, the left or right in this embodiment refers to the left or right in fig. 4.
As shown in fig. 2 and 4, the present invention provides a normally closed wet type multiple disc clutch including: the brake device comprises an outer hub 1, a first thrust bearing 2, a lower pressure plate 3, a friction plate 4, a steel sheet 5, an inner hub 6, a second disc spring 7, a second pressure plate 8, a first disc spring 9, a first pressure plate 10 and a release bearing 11.
The outer hub 1 is a thin-wall cylinder with an end face on one side, rectangular tooth grooves parallel to the axis of the outer hub 1 are uniformly distributed on the side wall of the outer hub 1 along the circumferential direction, and the rectangular tooth grooves are used for being matched and inserted with rectangular teeth on the circumferential outer edge of the friction plate 4; six countersunk bolt holes are uniformly distributed on the end surface of the outer hub 1 along the circumferential direction, and the outer hub 1 is fixedly connected with an external flange through the countersunk bolt holes; the central position of the end face of the outer hub 1 is also provided with a central stepped hole, the hole with the larger diameter at the left side of the central stepped hole is an external flange positioning hole, the outer end of the external flange can be processed with a positioning boss and is arranged in the external flange positioning hole of the central stepped hole of the outer hub 1 in a matching way so as to ensure the coaxiality of the outer hub 1 and the external flange, and the hole with the smaller diameter is used for the transmission input shaft 26 to pass through; the outer hub 1 is coaxially mounted with the transmission input shaft 26, and both axial and radial positioning of the outer hub 1 is achieved by a fixed connection with an external flange.
The first thrust bearing 2 is sleeved on the transmission input shaft 26, the left end face of the first thrust bearing 2 abuts against the inner side of the end face of the outer hub 1, and the right end face of the first thrust bearing 2 abuts against the outer side of the end face of the inner hub 6.
The end part of the input shaft 26 of the gearbox is provided with a section of external spline, the external spline is also provided with a snap spring groove, the input shaft 26 of the gearbox is supported and installed on the gearbox shell 18 through a bearing, and the input shaft 26 of the gearbox only rotates along the axial direction and does not move linearly along the axial direction under the limitation of the gearbox shell 18.
An annular boss is arranged on a bottom plate of the lower pressing plate 3, rectangular teeth matched with the sliding grooves in the outer circumferential side wall of the inner hub 6 are machined on the radial inner side of the annular boss of the lower pressing plate 3, the lower pressing plate 3 is axially and slidably connected to the end part of the rectangular tooth socket in the outer circumferential side wall of the inner hub 6 through the rectangular teeth, and a certain space is reserved between the bottom plate of the lower pressing plate 3 and the outer hub 1 to ensure the axial movement space of the lower pressing plate 3; six upright posts 3A vertical to the bottom plate are uniformly arranged on the bottom plate at the radial inner side of the annular boss of the lower pressing plate 3 along the circumferential direction, and internal threads are formed in the upright posts 3A; the center of the bottom plate of the lower press plate 3 is provided with a center hole.
The center of the inner hub 6 is a base provided with a central hole, the inner side wall of the central hole of the base is provided with spline grooves, an annular bottom plate extends from the axial middle position of the outer side wall of the base to the outer side of the circumference, the annular bottom plate is uniformly provided with six unthreaded holes along the circumferential direction, the outer edge of the annular bottom plate extends rightwards along the axial direction to form a cylindrical side wall, the surface of the outer side wall of the cylindrical side wall is provided with five groups of rectangular tooth grooves arranged along the axial direction, the top of the cylindrical side wall extends to the outer side of the circumference to form an annular outer edge plate, the right side end face of the annular outer edge plate is provided with a circle of annular boss along the outer edge of the annular outer edge plate, and the radial inner side of the annular boss is uniformly provided; the inner hub 6 is coaxially arranged at the inner side of the outer hub 1, after the gearbox input shaft 26 sequentially passes through the outer hub 1, the first thrust bearing 2 and the lower pressing plate 3, the base of the inner hub 6 is matched and connected with an external spline at the shaft end of the input shaft 26 of the gearbox, so that the inner hub 6 rotates synchronously with the input shaft 26 of the gearbox, one end of the base of the inner hub 6 passes through a central hole of a bottom plate of the lower pressure plate 3 and is directly pressed on the end surface of the outer hub 1 through the first thrust bearing 2, the other end of the base of the inner hub 6 is axially fixed in a clamp spring groove on the external spline of the input shaft 26 of the gearbox through a first clamp spring 27, the axial fixation of the inner hub 6 is realized, the outer side of the cylindrical side wall of the inner hub 6 is in sliding connection with the rectangular teeth on the inner side of the annular boss of the lower pressing plate 3 through the rectangular tooth grooves, and the six upright posts 3A of the lower pressing plate 3 correspondingly penetrate through the six unthreaded holes on the annular bottom plate of the inner hub 6 one by one, so that the relative sliding between the inner hub 6 and the lower pressing plate 3 along the axial direction is realized.
The friction plates 4 and the steel sheets 5 form a friction assembly of the clutch, and are coaxially arranged between the lower pressing plate 3 and the inner hub 6, wherein the friction plates 4 and the steel sheets 5 are sequentially stacked in a staggered manner, rectangular teeth are uniformly arranged on the outer side of the circumference of each friction plate 4 along the radial direction, the friction plates 4 are slidably arranged in rectangular tooth grooves formed in the side wall of the outer hub 1 through the rectangular teeth so as to realize that the friction plates 4 axially slide relative to the outer hub 1, the inner side of the circumference of each steel sheet 5 is uniformly provided with the rectangular teeth along the radial direction, and the steel sheets 5 are slidably arranged in the rectangular tooth grooves formed in the outer side of the cylindrical side wall of the inner hub 6 through the rectangular teeth so as to realize that the; the outermost friction plate 4 on one side of the outer hub 1 is in sliding-grinding contact with an annular boss on a bottom plate of the lower pressing plate 3, and the outermost friction plate 4 on one side of the inner hub 6 is in sliding-grinding contact with an annular outer edge plate of the inner hub 6; under the axial sliding of the lower pressure plate 3 and the inner hub 6, the friction plates 4 and the steel sheets 5 are separated or pressed against each other, so that the transmission or the interruption of the power between the inner hub 6 and the outer hub 1 is realized.
Second belleville spring 7 is the awl disk that one end bore is big, and other end bore is little, and it has six second belleville spring jack catch 7A to distribute along the circumferencial direction at second belleville spring 7's big bore end, second belleville spring jack catch 7A is along the direction of the 7 conical surfaces of second belleville spring to peripheral hardware extension form, second belleville spring 7 and the coaxial setting of interior hub 6, and its six second belleville spring jack catch 7A one-to-one joint are in six second belleville spring draw-in grooves 6A of the annular boss inboard of interior hub 6.
The second pressure plate 8 is a circular disc with a center through hole at the circle center position, the second pressure plate 8 and the second disc spring 7 are coaxially arranged, one end face of the second pressure plate 8 is axially pressed at one end of the small aperture of the second disc spring 7, an annular groove is arranged at the position, close to the center through hole, on the other end face of the second pressure plate 8, six through holes are uniformly arranged along the circumferential direction of the bottom face of the annular groove, a threaded hole is also arranged between every two through holes in the six through holes, namely, six threaded holes are formed in total, a circle of annular boss is arranged on the outer edge of the end face circumference at one side of the annular groove of the second pressure plate 8, and six first disc spring clamping grooves 8A are uniformly arranged on the radial inner side of the annular boss; six through holes in the annular groove of the second pressure plate 8 correspond to internal threaded holes in six upright columns 3A of the lower pressure plate 3 one by one, the second pressure plate 8 is fastened on the end faces of the upright columns 3A of the lower pressure plate 3 through first fastening bolts 13, and then the second belleville spring 7 is pressed on the inner hub 6 through the second pressure plate 8 along the axial direction, so that the second belleville spring 7 is pre-tightened between the second pressure plate 8 and the inner hub 6, and pressing force is provided for the friction assembly; in addition, on the terminal surface that second pressure disk 8 and second belleville spring 7 compress tightly one side, open along the circumference outside and have a ring shape to dodge the groove, when second pressure disk 8 compressed tightly second belleville spring 7 to the biggest deformation along the axial, second pressure disk 8 dodges the groove through this ring shape and realizes dodging interior 6 outer most ring boss of hub to avoid taking place the interference collision.
First dish-shaped spring 9 is the same with structure of second belleville spring 7, promptly first dish-shaped spring 9 also is the awl disk that one end bore is big, and the other end bore is little, and it has six first dish spring jack catch 9A to distribute along the circumferencial direction at the big bore end of first dish-shaped spring 9, first dish spring jack catch 9A is along the direction of the first dish-shaped spring 9 conical surface to the peripheral hardware extension form, first dish-shaped spring 9 and the coaxial setting of second pressure disk 8, and its six first dish spring jack catch 9A one-to-one joint are in six first dish spring jack catches 8A of the annular boss inboard of second pressure disk 8.
And the ratio of the height of the inner cone to the thickness of the disc spring is larger than that of the first disc spring 9 and the second disc spring 7 in the free state
Figure BDA0002374794610000071
The first pressure plate 10 and the first disc spring 9 are coaxially arranged, the end face of the first pressure plate 10 is axially pressed against one end with a small aperture of the first disc spring 9, six unthreaded holes are uniformly formed in the end face of the first pressure plate 10 along the circumferential direction, the six unthreaded holes in the first pressure plate 10 correspond to six threaded holes in the bottom surface of an annular groove of the second pressure plate 8 one by one, the first pressure plate 10 is connected with the second pressure plate 8 through a shoulder bolt 14, wherein the threaded end of the shoulder bolt 14 is fixedly connected with the threaded holes in the second pressure plate 8, the shoulder end face of the shoulder bolt 14 is tightly pressed on the bottom surface of the annular groove of the second pressure plate 8, the unthreaded rod end of the shoulder bolt 14 is connected with the unthreaded holes in the first pressure plate 10 in a sliding fit manner, so that the first pressure plate 10 axially slides along the end of the shoulder bolt 14, the length of the shoulder bolt 14 is selected through the unthreaded holes, and the axial distance between the first pressure plate 10 and the second pressure plate 8 is the largest, the first pressure plate 10 will apply a certain pressing force to the first disc spring 9 along the axial direction to deform the first disc spring 9, and the deformation force generated by the deformation of the first disc spring 9 can ensure that the position of the first disc spring 9 and the second pressure plate 8 are relatively fixed during the rotation motion.
The center position of first pressure disk 10 is equipped with the bearing frame coaxially, release bearing 11 installs in this bearing frame, release bearing 11 is angular contact bearing.
In the normally closed wet-type multi-plate clutch, the friction components are pressed or separated along with the linear movement of the first pressure plate 10 along the axial direction under the action of external force, so that the clutch is combined or separated, and the transmission or interruption of power is realized.
As shown in fig. 2 and 3, the present invention also discloses an actuator of a normally closed wet multi-plate clutch, comprising: the device comprises a photoelectric encoder 15, a direct current motor 16, a bottom plate 19, a needle bearing 20, a second thrust bearing 21, a second snap spring 22, a guide plate 23, a trapezoidal lead screw 24, a lead screw sliding sleeve 25 and a gearbox controller.
A direct current motor flange 16A is arranged on the outer side of a motor shell of the output end of the direct current motor 16, the direct current motor flange 16A, a bottom plate 19 and a guide plate 23 are sequentially arranged along the axial direction and are all fixed on a gearbox shell 18 through a second fastening bolt 17, wherein coaxial unthreaded holes are formed in corresponding positions of the gearbox shell 18, the direct current motor flange 16A and the bottom plate 19 at a position where the direct current motor flange 16A, the bottom plate 19 and the guide plate 17 are matched and connected, threaded holes are formed in corresponding positions of the guide plate 23, the second fastening bolt 17 sequentially penetrates through the gearbox shell 18, the direct current motor flange 16A and the bottom plate 19 and is finally fixedly connected with the guide plate 23 through threads, and the direct current motor flange 16A, the bottom plate 19 and the guide plate 23 are fixedly connected on the gearbox shell 18; coaxial through holes are formed in the center positions of the direct current motor flange 16A, the bottom plate 19 and the guide plate 23, and the trapezoidal screw rod 24 penetrates through the through holes.
For convenience of description, the end with the smaller diameter of the trapezoidal lead screw 24 is referred to as a small end, i.e., the power connection end of the trapezoidal lead screw 24, and the end with the larger diameter is referred to as a large end, i.e., the thread transmission end of the trapezoidal lead screw 24. A large end of the trapezoidal lead screw 24 is processed with trapezoidal lead screw threads, a small end of the trapezoidal lead screw 24 is processed with a section of optical axis, a clamp spring groove is processed on the optical axis, and a rectangular block is processed at the tail end of the small end of the trapezoidal lead screw 24; a rectangular groove matched with the rectangular block at the small end of the trapezoidal screw 24 is processed at the output shaft end of the direct current motor 16, the rectangular block at the small end of the trapezoidal screw 24 is matched and installed with the rectangular groove of the output shaft of the direct current motor 16, and the torque of the direct current motor 16 is transmitted to the trapezoidal screw 24 through the rectangular block and the rectangular groove; the small end optical axis segment of the trapezoidal lead screw 24 is supported and installed in the needle bearing 20, and the needle bearing 20 is pressed in the central through hole of the bottom plate 19; a shoulder is machined at one end of the bottom plate 19 close to the direct current motor 16, and the needle bearing 20 is pressed on the shoulder so as to realize the axial translation limit of the needle bearing 20 at the end; an annular groove is processed at the other end of the bottom plate 19, and a second thrust bearing 21 is tightly pressed in the annular groove under the action of the axial force of a trapezoidal screw 24, so that the axial translation limit of the needle bearing 20 at the end is realized; the second clamp spring 22 is arranged in a clamp spring groove of a small-end optical shaft section of the trapezoidal lead screw 24, and a shaft shoulder formed between the large end and the small end of the trapezoidal lead screw 24 is propped against the end face of an inner ring of the second thrust bearing 21, so that the axial translation freedom degree of the trapezoidal lead screw 24 is limited.
An axial rectangular spline guide groove is processed on the inner side wall of the central through hole of the guide plate 23, and matched with the guide groove, a rectangular guide spline is processed on the outer side wall of the lead screw sliding sleeve 25, the lead screw sliding sleeve 25 is connected in the central through hole of the guide plate 23 in a sliding manner along the axial direction, and the lead screw sliding sleeve 25 only moves in a translation manner along the axial direction without rotating under the guide of the rectangular spline guide groove of the guide plate 23; the central position of the screw sliding sleeve 25 is provided with a threaded hole matched with the trapezoidal screw thread of the trapezoidal screw 24 along the axial direction, the trapezoidal screw 24 is connected with the screw sliding sleeve 25 in a threaded fit manner, and the screw sliding sleeve 25 moves linearly along the axial direction of the guide plate 23 under the driving of the rotation of the trapezoidal screw 24.
Screw sliding sleeve 25 is connected one end top and leans on the outer lane terminal surface of second thrust bearing 21 with trapezoidal lead screw 24's screw thread section root cooperation, and screw sliding sleeve 25 and trapezoidal lead screw 24's screw thread section top cooperation link are installed through the cooperation of release bearing 11 and the first pressure disk 10 of above-mentioned normally closed wet-type multiplate clutch, wherein, screw sliding sleeve 25 and release bearing 11 matched with one end processing have uide bushing and spacing shaft shoulder, and release bearing 11's inner circle suit is on the uide bushing of screw sliding sleeve 25 tip, and release bearing 11's inner circle terminal surface top leans on the spacing shaft shoulder of screw sliding sleeve 25 tip, and under screw sliding sleeve 25's drive, release bearing 11 can follow axial linear motion.
The photoelectric encoder 15 is installed at the rear end of the dc motor 16 and is used for measuring the number of photoelectric pulses generated when the output shaft of the dc motor 16 rotates. The photoelectric encoder 15 is in signal connection with a transmission controller (not shown in the figure), and sends the measured photoelectric pulse number generated when the output shaft of the direct current motor 16 rotates to the transmission controller, and the transmission controller converts the photoelectric pulse number into the rotation angle of the output shaft of the direct current motor 16. According to a disc spring mechanical characteristic curve MAP and a gear shifting strategy stored in a gearbox controller, the rotating angle of an output shaft of the direct current motor 16 is converted into the axial displacement of the first pressure plate 10 (namely the deformation of the first disc spring 9), and the pressing force between the friction plate 4 and the steel sheet 5 is obtained through further table lookup calculation, so that the accurate control of the torque transmitted by the clutch is realized.
In the executing mechanism of the normally closed wet type multi-plate clutch, the output torque of the direct current motor 16 drives the trapezoidal lead screw 24 to rotate, the trapezoidal lead screw 24 drives the lead screw sliding sleeve 25 to axially and linearly slide along the guide plate 23, further drives the release bearing 11 to axially and linearly move, and finally drives the first pressure plate 10 to axially move through the release bearing 11, so that the executing control of the separation or combination of the clutch is realized.
According to the composition structure of the normally closed wet type multi-plate clutch and the actuating mechanism thereof, the invention also provides a control method of the normally closed wet type multi-plate clutch, which is specifically explained as follows:
the power transmission route of the normally closed wet type multi-plate clutch is as follows: power is input through the gearbox input shaft 26, firstly, the gearbox input shaft 26 transmits the power to the inner hub 6, then the inner hub 6 transmits the power to the outer hub 1 through a friction assembly, and finally the outer hub 1 outputs the power through the external flange plate.
Specifically, after power is input through the gearbox input shaft 26, the gearbox input shaft 26 transmits the power to the inner hub 6 through spline connection between the end part and the base of the inner hub 6, the steel sheet 5 is installed in a rectangular tooth groove on the outer side of the inner hub 6 through rectangular teeth on the inner side of the circumference, on one hand, the steel sheet 5 can synchronously rotate along with the inner hub 6, on the other hand, the steel sheet 5 can relatively linearly slide along the axial direction of the inner hub 6, and the friction plate 4 is installed in a rectangular tooth groove on the outer hub 1 through rectangular teeth on the outer side of the circumference, on the one hand, the friction plate 4 can synchronously rotate along with the outer hub 1, and on the other hand, the friction plate 4 can relatively;
when the executing mechanism does not have power output, namely the first disc spring 9 and the second disc spring 7 do not have external force action, under the fixed connection of the first fastening bolt 13, the second disc spring 7 is pre-tightened between the second pressure plate 8 and the inner hub 6, so that the forces of the second disc spring 7 acting on the second pressure plate 8 and the inner hub 6 are the same in magnitude and opposite in direction; the force of the second disc spring 7 acting on the second pressure plate 8 is transmitted through the bolt 13 and the lower pressure plate 3 in sequence and acts on the surface of the friction plate 4 in sliding and grinding contact with the bottom plate of the lower pressure plate 3, and because the inner hub 6 is fixed along the axial direction, under the extrusion of the acting force, the friction plate 4 and the steel sheet 5 which are stacked in a staggered mode are pressed tightly, the acting force is finally transmitted to one end face of the inner hub 6 through the friction plate 4 in sliding and grinding contact with the annular outer edge plate of the inner hub 6, and finally the acting force is offset with the force which is equal in size and opposite in direction and acts on the other end face of the inner hub 6 through the second disc spring 7, and at the moment, the normally closed wet type multi-plate clutch is in a combined state;
as described above, when the actuator does not have power output, that is, the clutch is in a combined state without external force, power is transmitted to the steel plates 5 through the inner hub 6, friction torque is generated between the steel plates 5 and the friction plates 4 and the power is transmitted to the friction plates 4, the friction plates 4 transmit the power to the outer hub 1, the outer hub 1 is connected with the external flange through bolts, and finally the power is output through the external flange.
When the clutch needs to be disengaged, the actuator starts to operate, and for convenience of description, in this embodiment, the rotation direction of the dc motor 16 when the screw sliding sleeve 25 moves toward the side close to the first pressure plate 10 is referred to as forward direction, and the rotation direction of the dc motor 16 when the screw sliding sleeve 25 moves toward the side away from the first pressure plate 10 is referred to as reverse direction.
When the clutch needs to be separated, in the executing mechanism, the direct current motor 16 rotates in the positive direction, the direct current motor 16 drives the trapezoidal lead screw 24 to rotate in the positive direction through the output shaft, the trapezoidal lead screw 24 drives the lead screw sliding sleeve 25 to move linearly towards one side close to the first pressure plate 10 along the axial direction of the guide plate 23, and the lead screw sliding sleeve 25 further pushes the first pressure plate 10 to move linearly towards one side of the second pressure plate 8 through the separating bearing 11; the first disc spring 9 is arranged between the first pressure plate 10 and the second pressure plate 8, the first disc spring 9 generates certain deformation under the pre-tightening of the shaft shoulder bolt 14, and under the action of deformation force corresponding to the deformation, the position of the first disc spring 9 relative to the second pressure plate 8 does not change in the rotating process;
along with the movement of the first pressure plate 10 to the side close to the second pressure plate 8, the deformation of the first disc spring 9 is gradually increased, the deformation force of the first disc spring 9 is also increased, the force of the first disc spring 9 acting on the second pressure plate 8 is gradually increased, the second pressure plate 8 transmits the acting force to the second disc spring 7, because the second disc spring 7 is in a pre-tightening state between the inner hub 6 and the second pressure plate 8, and the second pressure plate 8 is fixed on the inner hub 6 through the first fastening bolt 13, the acting force with the same size as the pre-tightening force of the second disc spring 7 exists on the acting surface of the first fastening bolt 13 in contact with the second pressure plate 8, when the deformation force of the first disc spring 9 is smaller than the pre-tightening force of the second disc spring 7, namely, the force of the first disc spring 9 acting on the second pressure plate 8 is smaller than the pre-tightening force of the second disc spring 7, so that under the pre-tightening force of the second disc spring 7, the acting surface of the first fastening bolt 13 contacted with the second pressure plate 8 still has acting force, and the acting force is equal to the difference between the deformation force of the first disc spring 9 and the pretightening force of the second disc spring 7, and the acting force is the pressing force between the friction plate 4 and the steel sheet 5, so when the pressing force exists between the friction plate 4 and the steel sheet 5, the pressing force is the difference between the deformation force of the first disc spring 9 and the pretightening force of the second disc spring 7, therefore, by controlling the deformation amount of the first disc spring 9, the slow change of the pressing force between the friction plate 4 and the steel sheet 5 can be realized, and the separation or combination of the clutch can be accurately and stably controlled by an actuating mechanism.
When the deformation force generated by the deformation of the first disc spring 9 is just equal to the pretightening force of the second disc spring 7, the acting force on the acting surface of the first fastening bolt 13 contacted with the second pressure plate 8 is equal to zero, namely no acting force exists on the acting surface of the first fastening bolt 13 contacted with the second pressure plate 8, no acting force exists between the friction plate 4 and the steel sheet 5, so that the friction torque is not transmitted between the friction plate 4 and the steel sheet 5 at the moment, the clutch is in a separated state, and the clutch is in unpowered transmission.
When the first disk spring 9 is deformed to a deformation force which is just equal to the pre-tightening force of the second disk spring 7, no force is just applied between the left plane of the bolt 13 for fixing the lower pressure plate 3 and the second pressure plate 8. From this point on, no friction torque is transmitted between the friction plate 4 and the steel plate 5.
In order to further illustrate the excellent performance of the normally closed wet-type multiplate clutch of the invention when a double-disc spring structure is adopted, the mechanical properties of the disc spring adopted by the invention are analyzed as follows:
as mentioned above, the ratio of the inner cone height of the disk spring in a free state to the thickness of the disk spring adopted by the clutch is larger than
Figure BDA0002374794610000111
As shown in fig. 5, at this time, the corresponding relationship between the spring force and the deformation amount of the disc spring is nonlinear; the pretightening force of the second disc spring 7 is equal to the spring force corresponding to the position of a point B in the figure, when the deformation of the first disc spring 9 is gradually increased to the deformation corresponding to the position of a point A in the figure, the deformation force of the first disc spring 9 is just the same as the pretightening force of the second disc spring 7, and as can be seen from the figure, the deformation of the first disc spring 9 is smaller than the deformation of the second disc spring 7; and the stiffness K of the disc spring at the point AA(amount of change in force per unit length of disc spring) is positive, and the stiffness K of the disc spring at point BBIs negative and the stiffness K of the disc spring at point AAGreater than the stiffness K at point BBAbsolute value of (d);
as shown in fig. 5, the stiffness of the first disc spring 9 corresponding to point a is a positive value, and the deformation force of the first disc spring 9 will continue to increase with the increase of the deformation, but in the pre-tightening state, the stiffness of the second disc spring 7 corresponding to point B is a negative value, and the deformation force of the second disc spring 7 will decrease with the increase of the deformation;
at this time, if the first pressure plate 10 just continues to move to the side of the second pressure plate 8, the double-disc spring structure composed of the first disc spring 9 and the second disc spring 7 is connected in series, and then the overall stiffness of the double-disc spring structure is:
Figure BDA0002374794610000112
therefore, at this time, the overall stiffness K of the double-disc spring structure is a negative value, and then, as the first pressure plate 10 continues to move to one side of the second pressure plate 8, the total deformation force of the double-disc spring structure will be reduced, and the deformation forces of the first disc spring 9 and the second disc spring 7 are equal and both will be reduced;
assuming that the total deformation force of the double disc spring configuration is reduced by 2 Δ F, the deformation force of the second disc spring 7 is reduced by Δ F, and accordingly the amount of deformation of the second disc spring 7 will be increased by Δ F2(ii) a A reduction of the deformation force of the second disc spring 7 by deltaf, i.e. a corresponding reduction of deltaf in the force acting against the first disc spring 9, results in a return of the deformation of the first disc spring 9, the amount of deformation of the first disc spring 9 being reduced by deltaf1The corresponding deformation force decreases by Δ F; that is, as shown in fig. 5, the operating point of the first disc spring 9 is changed from point a to point a ', and the operating point of the second disc spring 7 is changed from point B to point B';
when the corresponding relation between the disc spring force and the deformation is linear, the deformation of the first disc spring 9 is the same as that of the second disc spring 7; since the displacement of the first pressure plate 10 is equal to the sum of the deformation amounts of the first disc spring 9 and the second disc spring 7, when the first pressure plate 10 is displaced to the side of the second pressure plate 8 by Δ, the deformation amounts of the first disc spring 9 and the second disc spring 7 are respectively Δ/2; when the correspondence between the disc spring force and the amount of deformation is nonlinear as described above, when the first pressure plate 10 is displaced by Δ toward the second pressure plate 8 side, the amount of deformation of the first disc spring 9 is Δ1The amount of deformation of the second disc spring 7 is Δ2And Δ1+Δ2Δ; and because of the point stiffness K of the disc spring AAGreater than point B stiffness KBAbsolute value of, so-Delta1＜Δ2Then a is1＜0＜Δ＜Δ2Therefore, the amount of deformation Δ of the second disc spring 72Greater than the displacement Δ of the first platen 10; therefore, the rapid change in the amount of deformation of the second disc spring 7 means that the lower disc 3 can be quickly separated from the friction member without affecting the power transmission after the clutch is completely disengagedOpening, increasing the axial space between the friction plate 4 and the steel sheet 5, and reducing the liquid friction between the friction plate 4 and the steel sheet 5;
therefore, before the second disc spring 7 is pressed to the limit, the amount of deformation of the second disc spring 7 is always increased and the amount of deformation of the first disc spring 9 is always decreased as the first pressure plate 10 moves toward the second pressure plate 8 side.
In summary, when the normally closed wet type multiple disc clutch of the present invention adopts the structure of the double disc springs, the disc spring with the nonlinear mechanical property is more excellent than the disc spring with the linear mechanical property, and the power of the dc motor 16 in the actuator can be effectively reduced.
In the double disc spring structure, the maximum deformation amount of the first disc spring 9 is the deformation amount at the point M in fig. 5. At the M point, the rigidity of the disc spring is zero, the rigidity of the disc spring on the left side of the M point is a positive value, the rigidity of the disc spring on the right side is a negative value, and when the deformation amount of the first disc spring 9 is larger than that corresponding to the M point, the double-disc spring structure does not have the excellent mechanical property.
In the process of separating the wet-type multi-plate clutch, a photoelectric encoder 15 arranged at the tail end of a direct current motor 16 transmits collected photoelectric pulse number data generated when an output shaft of the direct current motor 16 rotates to a gearbox controller, the gearbox controller obtains the rotating angle of the output shaft of the direct current motor 16 through calculation, converts the rotating angle of the output shaft of the direct current motor 16 into the axial displacement of a first pressure plate 10 (namely the deformation of a first disc spring 9) according to disc spring mechanical characteristic curve MAP data stored in the gearbox controller and a gear shifting strategy, and further calculates the pressing force between a friction plate 4 and a steel plate 5 through table lookup so as to realize the accurate control of the torque transmitted by the clutch.
After the wet multiplate clutch is disengaged, the dc motor 16 stops outputting the torque, and the trapezoidal lead screw 24 has a self-locking function, so that the wet multiplate clutch can be always kept in the disengaged state.

Claims (10)

1. A normally closed wet type multi-plate clutch is characterized in that:
the device comprises an outer hub (1), a first thrust bearing (2), a lower pressing plate (3), a friction component, an inner hub (6), a second disc spring (7), a second pressing plate (8), a first disc spring (9), a first pressing plate (10) and a release bearing (11);
the outer hub (1), the lower pressure plate (3) and the inner hub (6) are sequentially arranged on an input shaft (26) of the gearbox, the first thrust bearing (2) is arranged between the outer hub (1) and the inner hub (6), the friction assembly is arranged between the lower pressure plate (3) and the inner hub (6), the circumferential inner side of the friction assembly and the outer hub (1) are relatively fixed in the circumferential direction, and the circumferential outer side of the friction assembly and the inner hub (6) are relatively fixed in the circumferential direction;
the inner hub (6) is fixed on the input shaft (26) of the gearbox, and the lower pressing plate (3) is connected with the inner hub (6) in a sliding mode along the axial direction;
a second disc spring clamping jaw of the second disc spring (7) is clamped on the circumferential outer edge of the inner hub (6), an upright post (3A) is arranged on the lower pressure plate (3), and the second pressure plate (8) is fixedly connected with the upright post (3A) penetrating through the inner hub (6) through a first fastening bolt (13), so that the second disc spring (7) is pre-tightened between the inner hub (6) and the second pressure plate (8);
a first disc spring clamping claw of the first disc spring (9) is clamped on the circumferential outer edge of the second pressure plate (8), the first pressure plate (10) is connected with the second pressure plate (8) through a shaft shoulder bolt (14), so that the first disc spring (9) is pressed between the first pressure plate (10) and the second pressure plate (8), and the first pressure plate (10) axially slides relative to the shaft shoulder bolt (14);
the release bearing (11) is arranged in a bearing seat arranged at the center of the first pressure plate (10), and the release bearing (11) pushes the first pressure plate (10) to slide along the axial direction under the action of external force.
2. The normally closed wet multiplate clutch of claim 1, wherein:
the friction assembly consists of friction plates (4) and steel sheets (5) which are sequentially staggered and stacked;
rectangular teeth are uniformly arranged on the outer side of the circumference of the friction plate (4) along the radial direction, and the friction plate (4) is axially and slidably arranged in a rectangular tooth groove formed in the side wall of the outer hub (1) through the rectangular teeth;
rectangular teeth are uniformly arranged on the inner side of the circumference of the steel sheet (5) along the radial direction, and the steel sheet (5) is axially and slidably arranged in a rectangular tooth socket formed in the outer side of the side wall of the inner hub (6) through the rectangular teeth;
the outermost friction plate (4) positioned on one side of the outer hub (1) is in sliding and grinding contact with an annular boss on a bottom plate of the lower pressure plate (3);
the outermost friction plate (4) positioned on one side of the inner hub (6) is in sliding and grinding contact with the annular outer edge plate of the inner hub (6);
under the axial sliding of the lower pressure plate (3) and the inner hub (6), the friction plate (4) and the steel sheet (5) are pressed or separated, so that the transmission or the interruption of the power between the inner hub (6) and the outer hub (1) is realized.
3. The normally closed wet multiplate clutch of claim 1, wherein:
the first disc-shaped spring (9) and the second disc-shaped spring (7) are in conical disc shapes with the same structure, and the ratio of the height of the inner cone of the first disc-shaped spring (9) to the thickness of the second disc-shaped spring (7) to the thickness of the inner cone is larger than that of the first disc-shaped spring (9) in a free state
Figure FDA0002374794600000021
4. The normally closed wet multiplate clutch of claim 1, wherein:
the end face of the outer hub (1) is provided with a positioning hole used for being matched and positioned with an external flange and a bolt hole used for being fixedly connected with the external flange, and the outer hub (1) is matched and connected with the external flange to transmit power transmitted by the friction assembly outwards.
5. The normally closed wet multiplate clutch of claim 1, wherein:
the center of the inner hub (6) is a base provided with a center hole, the inner side wall of the center hole of the base is provided with a spline groove, the base of the inner hub (6) is in spline fit connection with the outer spline of the shaft end of the transmission input shaft (26) to enable the inner hub (6) to synchronously rotate along with the transmission input shaft (26), one end of the base of the inner hub (6) penetrates through the center hole of the bottom plate of the lower pressure plate (3) and is directly pressed on the end face of the outer hub (1) through the first thrust bearing (2), and the other end of the base of the inner hub (6) is axially fixed in a clamp spring groove on the outer spline of the transmission input shaft (26) through the first clamp spring (27) to axially fix the inner hub (6);
the inner hub (6) extends from the axial middle position of the outer side wall of the base to the circumferential outer side to form an annular bottom plate, a plurality of unthreaded holes are uniformly formed in the annular bottom plate along the circumferential direction, and the upright columns (3A) of the lower pressing plate (3) penetrate through the unthreaded holes in the annular bottom plate of the inner hub (6) in a one-to-one correspondence manner;
the outer edge of the annular bottom plate of the inner hub (6) extends rightwards along the axial direction to form a cylindrical side wall, a plurality of rectangular tooth grooves arranged along the axial direction are formed in the surface of the outer side wall of the cylindrical side wall, and the outer side of the cylindrical side wall of the inner hub (6) is connected with the rectangular teeth on the inner side of the lower pressure plate (3) in a sliding mode through the rectangular tooth grooves;
the outer edge of the annular outer edge plate of the inner hub (6) is provided with a circle of annular boss, a plurality of second disc spring clamping grooves are uniformly formed in the radial inner side of the annular boss, and second disc spring clamping claws of the second disc springs (7) are correspondingly clamped in the second disc spring clamping grooves one by one.
6. The normally closed wet multiplate clutch of claim 1, wherein:
the second pressure plate (8) is a circular disc with a central hole, a plurality of through holes which are in one-to-one correspondence with the upright columns (3A) are uniformly formed in the circumferential direction of the central hole of the second pressure plate (8), and the first fastening bolts (13) penetrate through the through holes to be in threaded connection with the upright columns (3A);
a circle of annular boss is arranged on the circumferential outer edge of the end face of the second pressure plate (8) matched with the first disc-shaped spring (9), a plurality of first disc-shaped spring clamping grooves are uniformly formed in the radial inner side of the annular boss, and the first disc-shaped spring clamping claws of the first disc-shaped spring (9) are correspondingly clamped in the first disc-shaped spring clamping grooves one by one;
second pressure disk (8) and second belleville spring (7) cooperate a side end face outside to open and have the annular groove of dodging, compress tightly second belleville spring (7) to when maximum deformation along the axial in second pressure disk (8), second pressure disk (8) avoid taking place to interfere with interior hub (6) through dodging the groove.
7. The normally closed wet multiplate clutch of claim 1, wherein:
the release bearing (11) is an angular contact bearing.
8. The actuator of a normally closed wet multiplate clutch of claim 1, wherein:
the device comprises a direct current motor (16), a bottom plate (19), a needle bearing (20), a second thrust bearing (21), a second snap spring (22), a guide plate (23), a trapezoidal lead screw (24) and a lead screw sliding sleeve (25);
a direct current motor flange (16) A, a bottom plate (19) and a guide plate (23) at the output end of the direct current motor (16) are sequentially arranged and fixed on the gearbox shell (18);
one end of a trapezoidal lead screw (24) is coaxially connected with an output shaft of a direct current motor (16), an optical axis section of the trapezoidal lead screw (24) is installed in a bottom plate (19) through a needle bearing (20), the inner side of a lead screw sliding sleeve (25) is in threaded connection with a threaded shaft section of the trapezoidal lead screw (24), the outer side of the lead screw sliding sleeve (25) is installed on the inner side of a guide plate (23) in a sliding mode through a guide spline, and the lead screw sliding sleeve (25) slides linearly along the guide plate (23) under the driving of the rotation of the trapezoidal lead screw (24);
the second thrust bearing (21) is arranged at a shaft shoulder between a smooth shaft section and a threaded shaft section of the trapezoidal lead screw (24), the second thrust bearing (21) is pressed in an annular groove at the outer end of the bottom plate (19) under the action of the axial force of the trapezoidal lead screw (24), the second snap spring (22) is arranged in a snap spring groove of the trapezoidal lead screw (24) and contacts with the side surface of the bottom plate (19), and further the axial fixation of the trapezoidal lead screw (24) is realized;
the tip of lead screw sliding sleeve (25) with release bearing (11) cooperation is connected, wherein the tip processing of lead screw sliding sleeve (25) has uide bushing and spacing shaft shoulder, and the inner circle suit of release bearing (11) is on the uide bushing of lead screw sliding sleeve (25) tip, and the inner circle terminal surface top of release bearing (11) leans on the spacing shaft shoulder of lead screw sliding sleeve (25) tip, and axial linear motion is followed in release bearing (11) under the drive of lead screw sliding sleeve (25).
9. The actuator of a normally closed wet multiplate clutch of claim 8, wherein:
further comprising a photoelectric encoder (15);
the photoelectric encoder (15) is arranged at the rear end of the direct current motor (16) and is used for measuring the photoelectric pulse number generated when the output shaft of the direct current motor (16) rotates;
the photoelectric encoder (15) is in signal connection with the gearbox controller, the measured photoelectric pulse number generated when the output shaft of the direct current motor (16) rotates is sent to the gearbox controller, and the axial displacement of the release bearing (11) is determined and controlled through the gearbox controller.
10. The method of controlling a normally closed wet multiplate clutch of claim 1, wherein:
the combination control method of the clutch comprises the following steps:
when the first disc spring (9) and the second disc spring (7) have no external force, under the fixed connection of the first fastening bolt (13), the second disc spring (7) is pre-tightened between the second pressure plate (8) and the inner hub (6), the forces of the second disc spring (7) acting on the second pressure plate (8) and the inner hub (6) are respectively the same in magnitude and opposite in direction, wherein the forces of the second disc spring (7) acting on the second pressure plate (8) are sequentially transmitted through the bolt (13) and the lower pressure plate (3) and act on the friction component, under the extrusion of the acting force, the friction component is pressed, the acting force is finally transmitted to one end face of the inner hub (6) through the friction component, and finally the acting force is resisted with the force which is the same in magnitude and opposite in direction and acts on the other end face of the inner hub (6) through the second disc spring (7), at the moment, the normally closed wet type multi-plate clutch is in a combined state and transmits power, the power is transmitted to a friction assembly through an inner hub (6), the friction assembly transmits the power to an outer hub (1), and the power is finally output through an external flange plate connected with the outer hub (1);
the clutch release control method comprises the following steps:
under the action of an actuating mechanism, a release bearing (11) pushes a first pressure plate (10) to move linearly to one side of a second pressure plate (8), under the pre-tightening of a shaft shoulder bolt (14), a first disc-shaped spring (9) arranged between the first pressure plate (10) and the second pressure plate (8) generates certain deformation, along with the movement of the first pressure plate (10) to one side close to the second pressure plate (8), the deformation of the first disc-shaped spring (9) is gradually increased, the deformation force of the first disc-shaped spring (9) is also increased, the force of the first disc-shaped spring (9) acting on the second pressure plate (8) is gradually increased, the second pressure plate (8) transmits the acting force to a second disc-shaped spring (7), because the second disc-shaped spring (7) is in a pre-tightening state between an inner hub (6) and the second pressure plate (8), and the second pressure plate (8) is fixed on the inner hub (6) through a first fastening bolt (13), therefore, the acting surface of the first fastening bolt (13) contacted with the second pressure plate (8) has acting force with the same size as the pretightening force of the second disc spring (7), when the deformation force of the first disc spring (9) is smaller than the pretightening force of the second disc spring (7), under the pretightening force of the second disc spring (7), the acting force still exists on the acting surface of the first fastening bolt (13) contacted with the second pressure plate (8), the acting force is equal to the difference between the deformation force of the first disc spring (9) and the pretightening force of the second disc spring (7), and the acting force is the pressing force between the friction plate (4) and the steel plate (5), so when the pressing force exists between the friction components, the pressing force is the difference between the deformation force of the first disc spring (9) and the pretightening force of the second disc spring (7), and the deformation amount of the first disc spring (9) is controlled, the slow change of the pressing force between the friction components is realized, so that the separation or combination of the clutch can be accurately and smoothly controlled through an actuating mechanism;
when the deformation force generated by the deformation of the first disc spring (9) is just equal to the pretightening force of the second disc spring (7), the acting force on the acting surface of the first fastening bolt (13) contacted with the second pressure plate (8) is equal to zero, namely no acting force exists on the acting surface of the first fastening bolt (13) contacted with the second pressure plate (8), no acting force exists between the friction components, at the moment, the friction torque is not transmitted between the friction plate (4) and the steel plate (5), the clutch is in a separation state, and the clutch is in unpowered transmission.
CN202010062018.XA 2020-01-20 2020-01-20 Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof Pending CN111075855A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010062018.XA CN111075855A (en) 2020-01-20 2020-01-20 Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010062018.XA CN111075855A (en) 2020-01-20 2020-01-20 Normally-closed wet type multi-plate clutch and execution mechanism and control method thereof

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Application Number Title Priority Date Filing Date
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114776720A (en) * 2022-05-05 2022-07-22 重庆宗申集研机电科技有限公司 Double clutch

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114776720A (en) * 2022-05-05 2022-07-22 重庆宗申集研机电科技有限公司 Double clutch
CN114776720B (en) * 2022-05-05 2023-12-26 重庆宗申集研机电科技有限公司 Dual clutch

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