KR20150006025A - Lever actuator of a friction clutch and method for designing said lever actuator - Google Patents

Abstract

The present invention relates to a lever-like actuator and a method of designing the lever-like actuator, characterized in that the lever-like actuator comprises a plurality of lever-like actuators, each of which has a clutch characteristic curve of a clutch torque, Wherein the lever-like actuator includes an engaging lever, the engaging lever being axially displaced by a spindle drive along a rolling path, the lever-type actuator being axially displaced by a spindle drive, And the swinging curve of the engagement engaging lever is driven by the spindle drive along the rolling path, and the tolerance for the rolling device rolling between the base plate and the swinging curve of the lever- For all clutch characteristic curves occurring within the range, Lt; RTI ID = 0.0 > clutch torque < / RTI > A design is achieved that extends the possible rolling paths or requires less spindle force of the spindle drive by creating a rocking curve based on the key characteristic curve reproduced by the variation of the clutch characteristic curves of the actually required engagement engagement forces along the meshing engagement path.

Description

TECHNICAL FIELD [0001] The present invention relates to a lever-type actuator of a friction clutch and a design method of the lever-type actuator.

The present invention relates to a lever-like actuator in friction clutches pressed against each other and a method for designing a lever-like actuator for friction clutches having different engagement and coupling force characteristic curves along the engagement-engagement path.

The friction clutches pressed against each other are used in a drive train having a dual clutch transmission including two sub-drive trains, and each sub-drive train can be connected to the internal combustion engine via a friction clutch. In order to suppress the interruption of the drive train in the event of an emergency, one or more friction clutches are formed to be squeezed together and opened automatically. This is because the friction clutch is automatically switched to the open state in which there is no torque transmission in the absence of power supply to the clutch actuator (here lever type actuator) that operates the friction clutch, so that an excessively large torque, Clutch transmission < / RTI > The frictional clutches pressed against each other are opened in the non-operating state and are closed by lever-like actuators without transmitting torque, because the lever members, e.g., lever springs or pressure vessels, are displaced axially along the engaging- . In this case, the pressure plate, which is again displaced in the axial direction by the lever member or toward the back pressure plate so as to act about the fulcrum point, is operatively connected to the friction lining of the clutch disc, The torque is transmitted through the friction clutch according to the engagement engagement path. To adjust such torque, the corresponding engaging force must be applied along the engaging coupling path of the lever-like actuator, but the engaging force is not constant according to a series of variations in the clutch characteristic curves of the transmissible torque of the friction clutch on the engaging coupling path . Rather, the lever-like actuator should be designed to adjust the maximum clutch torque required over the range of deviation of the clutch characteristic curves along the meshing engagement path to be provided.

A typical lever-type actuator and its method of operation are known, for example, from DE 10 2004 009 832 A1, DE 2008 026 994 A1, DE 2009 010 136 A1, DE 10 2009 019 581 A1 and DE 10 2009 048 725 A1 have. A typical lever type actuator includes, for example, an engaging lever for pressing a lever member of a friction clutch, and a base plate to which a spindle drive driven by the motor is fixed and the lever end of the engaging lever is received in a pre-pressured state. The spindle drive drives a displaceable rolling device in a radial direction relative to the rotational axis of the friction clutch, the rolling device rolling between the base plate and the engaging lever. At this time, by the rolling profile in the form of a rocking curve, which is preferably provided on the engaging lever, the spindle force of the spindle drive and the preload of the engagement lever, An effective engagement force is determined along the meshing engagement path adjusted by the rolling device based on the path. In this case, the lever-like actuator is designed in accordance with the clutch characteristic curve in which the maximum available spindle force is adjusted in order to deliver the maximum transmittable clutch torque in the shortest meshing engagement paths. In this case, a smaller spindle force is generated for the remaining friction clutches having so-called longer characteristic curves in the rolling path, i. E. Having an engaging force for adjusting the maximum transmittable clutch torque in the larger meshing engagement paths. In this case, the rolling path is designed to match the longest clutch characteristic curve. In this case, of course, if the deviation of the clutch characteristic curves is severe, the leverage ratio provided by the swing curve in the shortest characteristic curve is very large, so that the friction clutch may be overloaded in the large rolling paths. On the other hand, if the characteristic curves are long, the required rolling path may be insufficient to adjust the maximum transferable torque.

It is therefore an object of the present invention to design a lever-like actuator which can be used for a maximum number of friction clutches pressed against one another, with a series of deviations of the clutch characteristic curve of the friction clutch. It is also an object of the present invention to improve the design method of the lever-type actuator. Another aspect of the above-described task is to reduce the spindle force of the spindle drive, for example, so that a smaller motor can be used.

One aspect of the above-described problem is to provide an engaging coupling force along a meshing engagement path with a lever member of the friction clutches pressed against each other, having clutch characteristic curves of clutch torque that can be transmitted along the meshing engagement path and influenced by the tolerance, A lever-shaped actuator including an engaging lever which is axially displaced along a rolling path by a spindle drive and which presses a lever member and receives a preload at a lever end opposite the lever member, wherein the engaging lever A swinging curve is defined as a clutch torque that is maximally transferible for all clutch characteristic curves occurring within a tolerance range, for a rolling device driven by a spindle drive along the rolling path and rolling between a base plate and a swinging curve of a lever- To the engagement force required to transmit The second is the design, the design of the swing curve is performed using a key characteristic curve reproduced by the variation of the clutch characteristic curve of the actually required engagement coupling force along the engagement coupling path. The design of the lever type actuator using this type of key characteristic curve no longer follows the actual clutch characteristic curve. Rather, the key characteristic curve of this type is synthetically adjusted to the required operating area of the lever-type actuator when the clutch characteristic curves are different. In this case, preferably, the key characteristic curve is a sub characteristic curve formed from an arbitrary engagement engagement force to an engagement engagement force when the clutch torque that can be transmitted along the clutch characteristic curve with the shortest engagement coupling path is maximum, And a sub characteristic curve along the tolerance width of the engagement engagement paths assigned to the clutch characteristic curves at a predetermined engagement engagement force over the behavior of the engagement engagement force required for transmission of the maximum clutch torque. In detail, the lever-like actuator according to the present invention is preferably controlled in such a manner that the mechanical load can be kept small so as not to deviate from the key characteristic map. In such a control method, the actually necessary operation path is identified and used as a limit in the control device. The identification can be performed either through adaptation in the driving mode, or during manufacturing, and the results can be stored.

Another aspect of the above-mentioned problem is achieved by an operating lever that receives an applied pressure to the base plate at one end of the lever and axially presses the lever member of the friction clutch at the other end of the lever; And a roller unit which has a roller which forms a fulcrum point of the operating lever and which rolls over the rocking curve of the base plate and the operating lever, and which is displaced in the radial direction along the rolling path by the spindle drive At this time, the tangential angle between the roller and the swing curve on the rolling path suddenly increases at a predetermined path point. At this path point, the slope of the swing curve, preferably from the mean path to the predetermined path point, is smaller than the slope from the path point to the maximum path.

Further, the operation method of such a lever-type actuator is advantageous for operating the friction clutch. In this case, the maximum required operating path is determined for full operation of the friction clutch, and the operation of the larger operating paths is blocked by the control device. In this way, overload of the lever type actuator can be prevented in a predetermined series of deviations, especially when the characteristic curve of the friction clutch is short. The maximum operating path may be determined, for example, during adaptation and / or commissioning, at which time, for example, operating forces on the operating path are determined and the maximum operating path is assigned and stored at any predetermined operating force.

The present invention will be described in detail with reference to the embodiments shown in Figs. 1 to 6. Fig.

1 is a graph showing a key characteristic curve fitted to the operating region of a lever-type actuator.
2 is a characteristic diagram of a lever-type actuator superimposed on the key characteristic curve and the clutch characteristic curves.
Fig. 3 is a schematic view of an engaging lever of a lever-type actuator having a swing curve designed based on the key characteristic curve of Figs. 1 and 2. Fig.
4 is a graph showing the swing curve in a rectangular coordinate system.
5 is a graph showing the tangential angle between the roller of the rolling device and the swing curve along the longitudinal axis.
6 is a graph showing the tangential angle when the spindle force is reduced.

)로 표시되어 있다. 최단 맞물림 결합 경로에서 전달가능한 최대 결합 토크를 조정하기 위해, 베이스 플레이트에 대해 설정된 예압 및 사전 설정된 최대 스핀들 힘에서 도 3에 상세히 도시된 레버형 작동기의 요동 곡선을 특성 곡선(2a)에 맞추어 설계할 때와 달리, 요동 곡선은 종합적으로 결정되는 키 특성 곡선(3)에 기초하여 설계된다. 상기 키 특성 곡선은 제1 서브 특성 곡선(4)에서는 최대로 전달 가능한 또는 제공된 클러치 토크[M(2a)]까지 이른바 최단 클러치 특성 곡선(2a)을 따르며, 제2의 서브 특성 곡선(5)에서는 나머지 특성 곡선들(2b, ..., 2n)의 최대로 전달 가능한 토크들을 따른다. 이로써 레버형 작동기의 유효 작동 범위가 정해진다.The graph 1 shows the engaging force against the engaging coupling path of the lever-like actuator and the crowd 2 of the clutch characteristic curves 2a, 2b, ..., 2n relating to the friction clutch pressed against each other, These clutch characteristic curves form a corresponding clutch torque when the meshing engagement paths are different due to a series of deviations, for example, geometric dimensions, variation in frictional coefficient of the friction lining, etc.,

). In order to adjust the maximum engageable torque in the shortest engaging engagement path, the swing curve of the lever-type actuator shown in detail in Fig. 3 at a pre-set pressure and a predetermined maximum spindle force set for the base plate is designed to match the characteristic curve 2a Unlike the case, the oscillation curve is designed based on the key characteristic curve (3) which is comprehensively determined. The key characteristic curve follows the so-called shortest clutch characteristic curve 2a up to the maximum clutch torque M [2a] that can be delivered or maximized in the first sub characteristic curve 4, and in the second sub characteristic curve 5 And follows the maximum transferable torques of the remaining characteristic curves 2b, ..., 2n. This defines the effective operating range of the lever-type actuator.

Fig. 2 shows a graph 1a in which a cluster 6 of lever characteristic curves 6a, 6b, ..., 6n is added to graph 1. Here, the lever characteristic curves 6a indicate the engaging force provided through the meshing engagement path in accordance with the spindle force applied when the rolling paths of the rolling device ascend from bottom to top. In this case, a clear meshing engagement path is required for a predetermined clutch torque and to provide a varying meshing force due to the given clutch characteristic curve 2a, 2b, ..., 2n, Lt; / RTI > Corresponding spindle force of the spindle drive is required to adjust the clutch torque in accordance with the leverage ratio of the engagement lever at this position of the engagement engagement path. As a result, for example, the illustrated lever characteristic curves 6a, 6b, ..., 6n cross the clutch characteristic curves 2a, 2b, ... 2n when the clutch torque is adjusted accordingly. By designing the lever characteristic curves 6a, 6b, ..., 6n based on the key characteristic curve 3, the lever characteristic curves 6n ', 6n-6n based on the broken line designed based on the shortest clutch characteristic curve 2a, 1 ', 6n-2'), a wider range of meshing engagement paths is used when the meshing engagement paths are large. Using the rocking curve of the lever-like actuator designed on the basis of the key characteristic curve, a larger deviation of the clutch characteristic curves 2a, 2b, ... 2n can be covered. Alternatively, since a smaller spindle force can be provided by designing the swing curve in accordance with the key characteristic curve 3 within the range of the lever characteristic curve 6n ', the motor necessary for providing such a spindle force is also more Can be designed to be small, and thus can be mounted in a narrower installation space.

Fig. 3 schematically shows the engaging lever 7 seen from the side. The engagement engaging lever 7 presses the pressure vessel or its lever spring on the rotational axis d of the friction clutch at one lever end 8. The engaging lever 7 is housed so as to be pre-pressurized toward the base plate 11 by the energy storage device 10, which is only indicated at the other lever end 9. The rolling device 15 which rolls on the swinging curve 14 at a tangential angle alpha by means of the rollers 12 which are only indicated on the base plate 11 and on the other hand by the rollers 13, Is displaced radially with respect to the rotational axis d by a spindle drive not shown in the drawing along the cloud path s (r) to form a fulcrum fulcrum for the engaging lever 7. Shaped engagement path s (e) of the lever-shaped actuator is formed according to the shape of the swinging curve 14 as it passes the rolling path s (r). At this time, the swing curve 14 is designed on the basis of the key characteristic curve 3 shown in Figs. 1 and 2, and compared with the initial swing curve 14 'shown by the broken line designed based on the shortest clutch characteristic curve, (g)] to a larger cloud path [s (r)]. As a result, a longer engagement engagement path [s (e)] is achieved within the rolling path range.

Fig. 4 shows projection of the swing curves 14 and 14 'of Fig. 3 in an orthogonal coordinate system 16 having coordinates (x) corresponding to the length path and coordinates (y) corresponding to the stroke. From this figure, it can be clearly seen that the slope of the swing curve 14 is changed in accordance with the actual scale, in comparison with the swing curve 14 'in the cloud paths exceeding the path point [s (g)].

5 shows the tangent angle (between the roller 13 and the swing curves 14 and 14 ') projected on the graph 17 to the linear coordinate x along the rolling path s (r) alpha) is shown. From this graph, the tangential angle alpha of the swinging curve 14 is larger than the tangential angle alpha of the swinging curve 14, while the tangential angle alpha of the swinging curve 14 is substantially constant between the sub-characteristic curves 4 and 5 (G (g)) corresponding to the bent point of the key characteristic curve (3) of FIG.

Fig. 6 shows a special case of the graph 17 of Fig. 5, in which the swing curve 14 is designed only to a larger engagement engagement path [s (e)] (Fig. 3). Since the swing curve 14a in the graph 18 of FIG. 6 is optimized for the smaller actuator force compared to the swing curve 14 ', the tangential angle a at the corresponding roll path positions as a whole is smaller than the swing curve 14 ').

1 graph
1a Graph
2 Composition of characteristic curves
2a clutch characteristic curve
2b Clutch characteristic curve
2n clutch characteristic curve
3 Key characteristic curve
4 Sub characteristic curve
5 Sub characteristic curve
6 A bunch of characteristic curves
6a Lever characteristic curve
6b Lever characteristic curve
6n lever characteristic curve
6n 'lever characteristic curve
6n-1 lever characteristic curve
6n-2 lever characteristic curve
7 Engaging lever
8 lever end
9 Lever End
10 Energy storage devices
11 base plate
12 Rollers
13 Rollers
14 Swing curve
14 'swing curve
14a swing curve
15 cloud device
16 Coordinate system
17 graph
18 graph
d rotary shaft
M (2a) Clutch torque
s (e) meshing coupling path
s (g) path point
s (r) cloud path
x coordinate
y coordinate
α tangent angle

Claims (6)

A method of designing a lever-like actuator,
The lever-like actuator comprises a lever (2) of friction clutches (2b, 2b, 2n) pressed against each other with clutch characteristic curves (2a, 2b, 2n) of clutch torque that can be transmitted along the engagement engagement path (E), and the lever-like actuator comprises an engagement engaging lever 7 which engages the spindle 4 along the rolling path s (r) The swinging curves 14 and 14a of the engaging lever 7 are displaced in the axial direction by the drive to press the lever member and receive a preload at the lever end 9 opposite the lever member, ) For the rolling device 15 driven by the spindle drive and rolling between the base plate 11 of the lever-like actuator and the swing curves 14 and 14a, 2, 2a, 2n) In the, method of designing a lever-type actuator that is designed on the basis of the engagement coupling force required to deliver the torque reochi,
The design of the rocking curves 14 and 14a is such that the key characteristic curve 3 reproduced by the variation of the clutch characteristic curves 2, 2a, 2n of actually engaging engagement forces along the engagement engagement path s (e) Wherein the step of performing the method comprises the steps of: 2. The shift control device according to claim 1, wherein the key characteristic curve (3) is obtained when the clutch torque [M (2a)] which can be transmitted from the engagement engagement force along the clutch characteristic curve (2a) having the shortest engagement road (2b, 2n) at a predetermined engagement force over the behavior of the engagement engagement force required for the transmission of the maximum clutch torque following the engagement engagement path, and a sub characteristic curve Characterized by a sub-characteristic curve (5) along the tolerance width of the engaging engagement paths. An engaging lever 7 which receives a preload with respect to the base plate 11 at one lever end 9 and axially urges the lever member of the friction clutch at the other lever end 8, ) And a rolling device (15) which forms a fulcrum fulcrum of the rolling device and which is displaced along the rolling path (s (r)) in a radial direction by a spindle drive, And rollers (12, 13) having swing curves (14, 14a) of an engaging lever (7) designed on the basis of the base plate (11) and the swinging curves (14, 14a). 4. The method according to claim 3, wherein the tangential angle alpha between the roller (13) and the swinging curve (14, 14a) along the rolling path (s (r) Wherein the lever-like actuator is a lever-like actuator. 5. The method according to claim 4, wherein the slope of the swing curve (14, 14a) from the mean cloud path [s (r)] 0 to the path point [s Is smaller than the slope of the lever-like actuator. A method of driving a lever-like actuator for operating a friction clutch according to any one of claims 1 to 5, wherein a maximum required operating path [s (g)] is determined for full operation of the friction clutch, Characterized in that the operation of the lever-type actuator is inhibited by the control device.

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