Patent Application
20190128344
The present disclosure relates to a centrifugal clutch for a drivetrain of a motor vehicle, having a centrifugal mass that is coupled to an angle plate in such a way that a radial movement of the centrifugal mass caused by a centrifugal force causes an axial movement of the angle plate. The centrifugal clutch has a pre-stressing element that is assigned to a coupling pin, which is prepared to at least partially transmit the axial movement of the angle plate to an inner basket designed to hold laminae, and which is inserted into an elongated hole in the angle plate in such a way that in an intermediate operating position a relative movement between the angle plate and the coupling pin is made possible when the inner basket rotates relative to the angle plate. The coupling pin may be at least partially surrounded by the pre-stressing element.
Various centrifugal clutches are known from the prior art. International patent application publication no. WO 2015/135540 A1 discloses a centrifugal clutch having an input part firmly attached to the motor, which is connected to laminae that come into contact with an output part by means of a centrifugal mass in such a way that a torque is transmissible from a motor output shaft to a transmission input shaft.
In centrifugal clutches according to this species, coupling is brought about depending on a speed of rotation. A first centrifugal mass is coupled here with a component attached to the motor, in such a way that a centrifugal force causes an axial movement of a first angle plate. Positioned between the first angle plate and a component attached to the transmission is a thrust bearing, which prevents rotational motion from being transmitted between the first angle plate and the component attached to the transmission. The axial movement of the first angle plate brought about by the first centrifugal mass, on the other hand, is transmitted to the component attached to the transmission. The component attached to the transmission is coupled rigidly to a second angle plate. The latter transmits the axial movement through a coupling pin to an inner basket, on which laminae are arranged, so that the inner basket laminae transmit torque frictionally with outer basket laminae that are connected non-rotatingly to the component attached to the motor. The torque of the inner basket is passed on via leaf springs to a hub, which provides the rotational speed of the transmission input shaft.
The coupling pin is surrounded by a pre-stressing element, so that an additional axial movement caused by a second centrifugal mass, which, analogously to the first centrifugal mass, brings about an axial movement of the second angle plate that intensifies the frictional lock between the laminae, is intercepted in such a case by the pre-stressing element if the force in the laminae should become too great. Because of its inertia, the second centrifugal mass causes a disengagement of the centrifugal clutch to be delayed, whereas an engagement is possible even with low torque and high rotational speeds.
The centrifugal clutches known from the prior art have the disadvantage that when the clutch is in a non-stationary state, for example in a moving-off process, unwanted frictional forces arise due to relative movements of individual components.
Furthermore, in the prior art the pre-stressing elements are coupled to an angle plate in such a way that the entire pre-stressing force of the pre-stressing element acts on the coupling zone between the pre-stressing element and angle plate when the inner basket is in a state of motion relative to the angle plate.
In the intermediate operating position, a loading section of the angle plate provided to transmit force to the pre-stressing element, a stop attached to the coupling pin and a stop attached to the pre-stressing element, are matched to each other so that the angle plate has a maximum contact area on one side of its loading section to transmit force. In this way, the pre-stressing element, which may be designed as a compression spring, acts on the angle plate on one side, which minimizes the occurrence of friction forces.
Example embodiments will be explained in greater detail below.
The contact area may be formed on the side of the angle plate facing the pre-stressing element. This provides space benefits, since the pre-stressing element is positioned at the shortest distance from the angle plate. In this way, the side of the angle plate facing away from the pre-stressing element experiences no pressure force from the side of the pre-stressing element, which further favors the intended minimization of friction.
When the pre-stressing element and the coupling pin are configured so that the movement of the coupling pin relative to the angle plate is achievable free of any pre-stressing of the pre-stressing element, a leaf spring positioned between the inner basket and a hub exerts a pressure force on the angle plate when a relative movement occurs between the inner basket and the angle plate.
The pre-stressing force exerted by the leaf spring is less than that exerted by the pre-stressing element. In this way, it is possible to reduce the friction that occurs in the relative rotation.
In an example embodiment, the stop attached to the coupling pin is formed by a support plate, which is attached rigidly to the coupling pin by a fastener such as a screw. In this way, a conventional coupling pin can be used. Attaching the additional support plate is sufficient to achieve the benefits according to the disclosure.
When the stop attached to the pre-stressing element is formed by an intermediate plate which can be placed on the pre-stressing element, a time-efficient and economical assembly of the coupling pin according to the disclosure with the pre-stressing element is possible. Furthermore, the geometry and material composition of the intermediate plate may be designed so that it can absorb the forces which act between the pre-stressing element, the coupling pin and the angle plate in a way that optimizes the flow of force.
It may be advantageous if an application of force brought about by the pre-stressing element acts on one side of the angle plate. A unilateral application of force brings the advantage that no opposing force is inducible. A corresponding relative rotation, which is enabled by a unilateral application of force, is accordingly lower in friction than a bilateral application of force. This prevents a clamping of the angle plate between two sections, each of which is pre-stressed by the pre-stressing element. Besides a lower energy input, caused by the relative rotation, the benefit of longer service life is realized. The reduced friction implies less abrasion of the angle plate, which on the one hand prolongs its life, and on the other hand causes fewer particles/shavings in the clutch. This also increases the quietness of operation of the centrifugal clutch according to the disclosure.
In an example embodiment, the angle plate and the coupling pin are connected to each other in such a way that the coupling pin allows a movement of the angle plate in a direction away from the coupling pin. The axial movement of the angle plate in the direction away from the coupling pin is limited accordingly by other components of the centrifugal clutch.
Additionally, it may be advantageous if the stop attached to the coupling pin is formed by a fastener that is connected rigidly to the coupling pin. The rigid connection keeps the relative friction low even at high vibrations, which has a positive affect on the life of the centrifugal clutch.
In addition, it may be advantageous if the coupling pin is designed as a stepped rivet. On the one hand, stepped rivets can be produced as standard components and at a reasonable price; on the other hand, they have shoulders which excel as a reliable stop in the centrifugal clutch.
According to the present disclosure, a drivetrain of a motor vehicle is disclosed. The drivetrain has a motor, a clutch and a transmission, the clutch being produced according to the design of a centrifugal clutch presented above.
In other words, an angle plate, which is positioned on the transmission side of a first centrifugal mass in the axial direction, is moved axially in the direction of the transmission by a first and/or second centrifugal mass. The centrifugal masses are designed here so that they bring about a coupling between the motor output shaft and the transmission input shaft even at a low speed of rotation. Thus, even at low rotational speeds they produce a motor torque that suffices to propel a motor vehicle. Since a coupling occurs even at low rotational speeds, it follows that at high rotational speeds the axial force induced by the centrifugal masses may be greater than necessary. To compensate for the excessive application of force, a pre-stressing element is employed to limit the pressing force and/or the disengaging force. The pre-stressing element may be designed as a compression spring, which is pre-stressed to the maximum pressing force. If a force is induced by the centrifugal masses that is greater than the pre-stressing of the compression spring, the compression spring is compressed. The centrifugal masses may be limited by a stop. Furthermore, the inner basket of the centrifugal clutch is linked to a hub by means of leaf springs, which brings about an additional intensification of the pressing force. The greater the axial movement of a leaf spring, the greater the rotation of the inner basket.
According to the disclosure, the operating area between the angle plate, the pre-stressing element and the coupling pin is designed so that they transmit force at a friction point. Thus, at the friction contact between the angle plate and the component attached to the pre-stressing element, e.g., a washer, the only force present is the stiffness of the leaf spring.
The centrifugal clutch according to the disclosure may be designed as a multi-plate clutch. It lends itself primarily for use in motorcycles, automobiles, dual clutches and/or hybrid clutches. While a wet-running clutch is also possible, dry clutch operation is preferred here.
According to the disclosure, the fuel consumption of a vehicle may be reduced. The division of the centrifugal masses according to the disclosure into a motor side and a transmission side also enables earlier synchronization of the clutch, which makes it possible to drive/drive off at lower motor speeds. The effect of this is that carbon dioxide emissions are significantly reduced for applications with centrifugal clutches according to the disclosure.
The division of the centrifugal masses according to the disclosure, namely into a motor and a transmission side, also makes a driving experience possible whose performance is very similar to that of conventional drivetrains. In particular, a motor under full load may be operated at lower speeds without causing slippage in the clutch. In combination with the self-intensification as a centrifugal disk, the solution according to the disclosure may thus be utilized for all conventional applications, i.e., also for shift transmissions without a centrifugal clutch, without necessitating an adaptation of the vehicle architecture. This expands the range of application of the device according to the disclosure.
In summary, the rotation of the inner basket or load transfer cup in the disengaging behavior is improved by inserting washers on the pin on the inner basket or load transfer cup side, which are positioned between the coil springs and the plate piece or ramp plate in the axial direction.
Example embodiments will be explained in greater detail below by means of figures. The figures show the following:
The figures are merely schematic in nature, and serve to aid in understanding the disclosure. The same elements are provided with the same reference labels. The features of the individual exemplary embodiments may be exchanged with one another.
Force is introduced into the friction clutch 1 by means of a ring gear 11. The latter is connected non-rotatingly to the input part 12. Between the input part 12 and a first shaft 13, a thrust bearing is positioned so that the input part 12 and the first shaft 13 are rotatable relative to each other. A first centrifugal mass 14a is coupled with the input part 13 so that it is fixed in the circumferential direction and variable in the radial direction. A second centrifugal mass 14b is positioned to the transmission side of the first centrifugal mass 14a. Due to a bevel 15 on a first angle plate 16, the radial movement of the first centrifugal mass caused by the centrifugal force is converted to an axial movement of the first angle plate 16. A thrust bearing 17 prevents rotation from being transmitted from the first angle plate 16 to a centrifugal mass carrier part 18.
A connecting piece 19 ensures that the axial movement of the first angle plate is transmitted to a second angle plate 20. According to the disclosure, the coupling pin 5 is coupled with the second angle plate 20 in such a way that, in a state in which the maximum pressing force pre-stressed by the pre-stressing element is not reached, the axial movement of the second angle plate results in an axial movement of the inner basket 7. The inner basket is made up of a driver 21 and a load transfer cup 22. A contact segment 23 of the inner basket 7 causes laminae 24 to be pressed against one another in such a way that a torque is transmissible from the motor side to the transmission.
The frictional lock referenced by the arrow 25a in
When the inner basket 7 rotates, a rotation is transmitted via the leaf spring 26 to the hub 27. The hub 27 drives the transmission input shaft. The hub 27 is connected rigidly to a housing part 29 by means of a bolt 28.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2016 211 217.1 | Jun 2016 | DE | national |
This application is the United States National Phase of PCT Appln. No. PCT/DE2017/100398 filed May 10, 2017, which claims priority to German Application No. DE102016211217.1 filed Jun. 23, 2016, the entire disclosures of which are incorporated by reference herein.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/DE2017/100398 | 5/10/2017 | WO | 00 |
