WO2018149437A1

WO2018149437A1 - Pedal force simulation device having a planar spring element and actuating system

Info

Publication number: WO2018149437A1
Application number: PCT/DE2018/100025
Authority: WO
Inventors: Andreas Schiebenes; Sebastian Honselmann; Manuel BAßLER
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2017-02-16
Filing date: 2018-01-16
Publication date: 2018-08-23
Also published as: DE112018000850A5; DE102017103211A1

Abstract

The invention relates to a pedal force simulation device (1) for a motor vehicle, comprising a housing (2) and a guide piston (4), which is received in the housing (2) and is movable along a longitudinal axis (3) of the housing (2), wherein the guide piston (4) has a conical segment (5) extending along the longitudinal axis (3) and wherein a contact element (6a, 6b) positioned in each case by means of a spring element (8a, 8b) can be pressed on said conical segment (5) from two sides facing away from one another in a radial direction of the longitudinal axis (3), wherein the spring elements (8a, 8b) are designed such that the spring elements extend in a planar manner in the unloaded state. The invention further relates to an actuating system for a motor vehicle clutch having said pedal force simulation device (1).

Description

Pedal force simulation device with flat spring element

The invention relates to a pedal force simulation device (ie, a pedal force simulation / pedal force simulator) for a motor vehicle, such as a car, truck, bus, or other utility vehicle, having a housing and a housing received along the housing and along a longitudinal axis the guide piston slidable guide piston, wherein the guide piston has a along the longitudinal axis (conical / conical) extending (ie widening and / or tapering in a radial direction of the longitudinal axis) cone segment and wherein on this cone segment (/ a conical surface of the cone segment) of two each other in a radial direction of the longitudinal axis facing away from each side a biased by a spring element contact element is pressed or pressed. In addition, the invention relates to an actuation system for a motor vehicle clutch with this Pedalkraftsimulationsvomchtung.

There are already known various types of actuation systems, including actuation systems in which a sensor is present in a device coupled to the pedal force simulation device, which detects the actuation of the pedal and accordingly controls the actuation / disengagement or engagement of the clutch.

From the not yet published DE 10 2015 216 146.3, with filing date

24.08.2015, discloses a device for force simulation on an actuating element of a vehicle, in particular a pedal force simulator disclosed. This device has a housing and an axially displaceable piston in the housing, wherein the piston is connected via a piston rod with the actuating element. In addition, a spring element is present, which is at least partially, in particular completely, disposed within the housing. The piston has a varying cross-section and when actuated by the actuating element, it engages in the spring element, wherein on the spring element rolling bodies are arranged, which are in operative connection with the piston and wherein the spring element consists of at least a first and a second spring part, which are interconnected. As a disadvantage, however, it has been found in the known prior art that the individual components are relatively expensive to produce. This applies in particular to the spring elements that have hitherto been made complex and thus relatively expensive in the production.

It is therefore the object of the present invention to overcome the disadvantages known from the prior art and in particular to provide a pedal force simulation device whose production costs are further reduced. Also, their mountability should be further improved.

This is inventively achieved in that the spring elements are formed so that they have a flat extension in an unloaded state, i. extend in an unloaded state along an imaginary extension plane straight / straight.

As a result, the spring elements are significantly easier formed and produced in a cost effective manner as a mass component. In particular, numerous process steps for forming the shape of the spring elements are saved over the prior art.

Further advantageous embodiments are claimed with the subclaims and explained in more detail below. If the spring elements are each supported on three bearing points, the spring elements are permanently pressed against the cone segment. By means of this three-point bearing, a corresponding force characteristic of the pedal force simulation device is converted particularly reliably over the service life. In this regard, it is particularly advantageous if the spring elements each at a first housing-fixed bearing point (ie at a first fixed to the housing supported bearing point) and a second housing-fixed bearing point (ie at a second fixedly supported on the housing bearing point) are supported / pivotally mounted. In addition, the spring elements are preferably each supported on a third bearing point, said third bearing point is in turn formed by a conical surface of the cone segment.

Thus, the first bearing point, the second bearing point, and the third bearing point are sequentially spaced in an axial direction (i.e., along the longitudinal axis). The first bearing point is thus arranged at a side facing away from the third bearing point of the second bearing point.

It is also advantageous if the bearing points of each spring element in the axial direction with respect to the longitudinal axis spaced from each other, wherein a first axial distance between the first bearing point and the second bearing point on each spring element is less than the axial distance between the second bearing point and the third bearing point (on the same spring element). This results in a particularly skilled lever arm for pressing the contact elements on the cone segment.

If the guide piston has several, for example two slide bearing sections, which are each arranged to a different axial side of the cone segment and abut against an inner circumferential side of the housing, the guide piston is securely guided.

In this context, it is also expedient if the spring elements in an operating state of the pedal force simulation device permanently press the associated contact element to a conical surface of the cone segment, ie that the contact element rests in any displaced in operation displacement position of the guide piston on the respective conical surface. The respective contact element is preferably designed as a role, namely as a needle roller / needle-like role. The roll forms a kind of needle roller bearing.

Is the cone segment in an axial direction and a first radial direction, seen in an extension plane of the cone segment fixed in / on the guide piston and in a second radial direction, seen transversely to the extension plane, limited (preferably by providing stops) displaced is ensures a secure guidance of the guide piston. The spring elements are in turn suitably received pivotably in an insertion sleeve inserted in the interior of the housing. As a result, the spring elements form a spring unit, which is constructed in several parts and can be easily mounted in the housing. Furthermore, the invention relates to an actuating system for a motor vehicle clutch with the pedal force simulation device according to the invention according to at least one of the embodiments described above.

In other words, it is thus proposed according to the invention in a pedal force simulation device / a pedal force simulator with a multi-part spring unit to form the spring elements flat. The spring elements are connected via three support points (bearing points) via a holder (insertion sleeve) with the housing of the pedal force simulator. The two outer contact points shorten the lever arm of the respective spring elements and thus lead to an increase in spring stiffness. In addition, a two-part piston guide with a distance between the bearing surfaces (plain bearing sections) on the housing to an improved leadership by restricting the tilting movement of the piston (guide piston) in an off-center force application. In addition, the scenery can be arranged within the two-piece piston.

The invention will now be explained in more detail with reference to figures.

Show it: 2 is a perspective view of the longitudinally cut pedal force simulation device according to FIG. 1, so that in particular the arrangement of two spring elements and their interaction with a cone segment can be recognized. The figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals.

In Fig. 1, a preferred embodiment of a pedal power simulation device 1 according to the invention is illustrated. In principle, the pedal force simulation device 1 serves to counteract an appropriate reaction force (pedal force) to an operator as a function of the displacement / pivoting path of an operating pedal (not shown here for clarity), namely a clutch pedal. In this exemplary embodiment, the pedal force simulation device 1 is used in an actuating system of a clutch of a drive train of a motor vehicle, not shown for the sake of clarity. The pedal force simulation device 1 thus serves as a device which simulates a corresponding counterforce to the operator as a function of the position of the operating pedal. The actual signal for actuating / engaging or disengaging the corresponding clutch of the motor vehicle is electronically transmitted to the respective input or release of the clutch. The actuation system is therefore designed as a clutch-by-wire system.

The pedal force simulation device 1 basically has a housing 2, within which a guide piston 4 is displaceably guided. The housing 2 has a sleeve-like outer wall 16, which extends cylindrically along an imaginary longitudinal axis 3 of the housing 2. By this outer wall 16, the housing 2 thus forms an interior, within which the guide piston 4 is slidably received along the longitudinal axis 3. In particular, the guide piston 4 at two, as explained in more detail below, slide bearing sections 13 and 14 on an inner peripheral side 12 of the housing 2 / the outer wall 16 slidably guided.

With the guide piston 4 a backdrop-like acting cone segment 5 / wedge segment is firmly connected. The cone segment 5 is, as can be seen well in Fig. 2, formed as a plate-shaped segment and has two mutually facing each other in a radial direction of the longitudinal axis 3 conical surfaces 7a and 7b. The cone segment 5 extends in particular along an axial direction of the longitudinal axis 3 and in an imaginary radial plane along a first radial direction. Consequently, the cone segment 5 is aligned with an imaginary plane of extension in which it extends transversely, namely perpendicular to a second radial plane extending in a second radial direction.

Viewed in the axial direction, the cone segment 5 tapers in a first section and thickened thereafter in a second section. The conical surfaces 7a and 7b extend, as seen in the axial direction, complementary to one another, so that the two conical surfaces 7a and 7b are mirror-inverted with respect to the plane of extent of the conical segment 5. The cone segment 5 is firmly received in the guide piston 4. The cone segment 5 is inserted / received in recesses within the guide piston 4. The cone segment 5 is secured to the guide piston 4 in such a manner that the cone segment 5 is fixed / secured in position in the axial direction as well as in the first radial direction (in the first radial plane corresponding to the plane of extent). In the second radial direction (in the second radial plane) extending transversely to the plane of extent of the cone segment 5, however, the cone segment 5 is received in a displaceably displaceable manner in the region of the recesses between two stops of the guide piston 4.

At each conical surfaces 7a and 7b, a contact element 6a or 6b assigned to it is pressed. A first contact element 6a is connected to a first conical surface 7a, and a second contact element 6b is to a second, facing away from the first conical surface 7a Cone surface 7b pressed. The contact elements 6a, 6b are each designed as a roller, namely as a needle roller. The contact elements 6a and 6b are in turn rotatably mounted / received on a respective spring element 8a and 8b. The contact elements 6a and 6b are each part of one of the spring elements 8a or 8b, so that the spring element 8a, 8b is designed in several parts.

The spring elements 8a and 8b are components of a spring unit 17 mounted in the housing 2. According to the invention, the spring elements 8a and 8b are shaped in such a way that, in their unloaded state, they are in a plane, i. just reach.

The spring unit 17 is designed in several parts. In addition to two individual spring elements 8a and 8b, the spring unit 17 also has an insertion sleeve 15. The insertion sleeve 15 serves as a holder / receptacle for the spring elements 8a and 8b in the housing 2. The insertion sleeve 15 is preferably pressed or screwed on the inner peripheral side 12 of the housing 2. In principle, other types of attachment for the insertion sleeve 15 in the housing 2 can be implemented in this context. The insertion sleeve 15 is always fixed, namely firmly integrated in the housing 2 in the axial and in the radial direction. The spring elements 8a and 8b are each attached to a first bearing point 9, which is arranged on an end region of the spring elements 8a, 8b facing away from the respective contact element 6a and 6b, attached to the insertion sleeve 15 and thus indirectly fixed to the housing / supported. The first bearing point 9 thus forms a pivot point, on which the spring elements 8a, 8b are firmly clamped.

From the first bearing point 9, the spring elements 8a and 8b extend substantially in the axial direction towards the cone segment 5 / to the contact elements 6a and 6b, but are slightly angled in their extension to the longitudinal axis 3. In addition to the first bearing point 9, the spring elements 8a and 8b are also fixed to the housing at a second bearing point 10 / supported on the insertion sleeve 15. In the region of the second bearing point 10, the spring elements 8a and 8b respectively lie, with the formation of a fulcrum, on support elements 18 in the form of Support pins on. A third bearing point 1 1, which is formed on a first bearing point 9 facing away from the axial side of the second bearing point 10, the respective spring element 8a and 8b via the contact element 6a and 6b on the cone segment 5 / the cone surfaces 7a, 7b stored / supported / pressed. This results in a three-point support / three-point support of the respective spring element 8a and 8b. The individual bearing points 9, 10 and 1 1 are spaced apart in the axial direction, in particular the distance (first distance) between the first bearing point 9 and the second bearing point 10 is smaller than the further distance (second distance) between the second bearing point 10 and the third storage point 1 1 is.

Coming back to the sliding bearing sections 13, 14, it can be clearly seen in connection with FIG. 1 that these are each arranged to one axial side of the cone segment 5. A first sliding portion / slide bearing portion 13 is arranged in the axial direction to a first side of the cone segment 5, while a second sliding portion / slide bearing portion 14 is disposed to a first slide bearing portion 13 remote from the second side of the cone segment 5 in the axial direction. Both slide bearing portions 13 and 14 are designed substantially as annular portions and are slidably on the inner peripheral side 12.

The second sliding bearing section 14 also merges into a journal region 19. This pin portion 19 receives a piston rod 20 against displacement. The piston rod 20 is connected in the usual way with the operating pedal of the motor vehicle. Furthermore, a compression spring 21 in the form of a screw compression spring, which is arranged outside the housing 2, is typically present. The compression spring 21 is supported at a first end to a housing-fixed area and coupled to a second end non-displaceable with the piston rod 20. Thus, the compression spring 21 is used for biasing the piston rod 20 (and indirectly the guide piston 4) in an extended position relative to the housing 2. The compression spring 21 is completely surrounded in the radial direction from radially outside by a schematically illustrated mudguard 22. Since the contact elements 6a and 6b are permanently pressed by the spring elements 8a and 8b with a certain biasing force on the cone surfaces 7a and 7b, the contour of the conical surfaces / conical segment, the biasing force of the spring elements 8a and 8b and the biasing force of the compression spring 21 the corresponding force curve for simulating the corresponding pedal force.

In other words, the embodiment according to the invention of a prior art pedal force simulation device 1 is distinguished, in particular, by the fact that the component geometry is simplified with regard to manufacturability by means of a flat spring element 8a, 8b. The storage concept was adapted accordingly and now represents a three-point bearing 9, 10, 1 1. Two of the bearing points 9,10 are in the fastener (insertion sleeve 15), the third bearing point 1 1 is the point of contact between the scenery (cone segment 5) and the needle rollers 6a, 6b located on the multi-part spring element 8a, 8b. In order to ensure the seat of the spring elements 8a, 8b they are to be clamped permanently. The slide 5 is axially and radially fixed in the two-part piston (guide piston 4) on their contact points on the piston 4, wherein a certain radial movement is possible, but limited by stops. The leadership of the piston 4 in the housing 2 via two spaced-apart contact surfaces (plain bearing sections 13, 14) located on the right and left of the gate 5) to reduce the susceptibility to tipping by an off-center force on the piston 4. The force characteristic is determined upon actuation of the pedal force simulator 1 by the interaction of the compression spring 21, the shape of the link 5 and the spring stiffness. By a displacement of the support points 1 1 on the spring elements 8a, 8b, the effective lever arm of the spring element 8a, 8b is directly influenced, which thus brings about an increase or reduction of the spring rigidity. A change in the gate shape increases or decreases, upon actuation of the pedal force simulator 1, the deflection of the spring elements 8a, 8b and thus changes the force curve of the overall system. Reference character list Pedal force simulation device

casing

longitudinal axis

guide piston

cone segment

a first contact element

b second contact element

a first cone surface

b second cone surface

a first spring element

b second spring element

first bearing point

0 second bearing point

1 third bearing point

2 inner circumference side

3 first slide bearing section

4 second plain bearing section

5 insertion sleeve

6 outer wall

7 spring unit

8 support element

9 pin area

0 piston rod

1 compression spring

2 dirt protection

Claims

claims

1 . Pedal force simulation device (1) for a motor vehicle, comprising a housing (2) and a guide piston (4) accommodated in the housing (2) and displaceable along a longitudinal axis (3) of the housing (2), the guide piston (4) extending along a conical segment (5) which extends along the longitudinal axis (3) and in which a contact element (6a, 6b) positioned on each side of the conical segment (5) faces away from each other in a radial direction of the longitudinal axis (3) can be pressed, characterized in that the spring elements (8a, 8b) are formed so that they have a flat Erstre- ckung in an unloaded state.

2. pedal force simulation device (1) according to claim 1, characterized in that the spring elements (8a, 8b) in each case at three bearing points (9, 10, 1 1) are supported.

3. pedal force simulation device (1) according to claim 2, characterized in that the spring elements (8a, 8b) are each supported on a first housing-fixed bearing point (9) and a second housing-fixed bearing point (10).

4. pedal force simulation device (1) according to claim 2 or 3, characterized in that the spring elements (8a, 8b) each at a third bearing point (1 1) on a conical surface (7a, 7b) of the cone segment (5) are supported.

5. pedal force simulation device (1) according to claim 3 and 4, characterized in that the bearing points (9, 10, 1 1) of each spring element (8 a, 8 b) in an axial direction with respect to the longitudinal axis (3) are arranged spaced from each other, wherein a first axial distance between the first bearing point (9) and the second bearing point (10) on each spring element (8a, 8b) is less than a second axial distance between the second bearing point (10) and the third bearing point (1 1).

6. pedal force simulation device (l) according to any one of claims 1 to 5,

characterized in that the guide piston (4) has a plurality of sliding bearing portions (13, 14) which are respectively arranged to another axial side of the cone segment (5) and abut against an inner peripheral side (12) of the housing (2).

7. Pedalkraftsimulationsvomchtung (1) according to one of claims 1 to 6,

characterized in that the spring elements (8a, 8b) in an operating state of the Pedalkraftsimulationsvomchtung (1) each their respective contact element (6a, 6b) to a conical surface (7a, 7b) of the cone segment (5) press.

8. Pedalkraftsimulationsvomchtung (1) according to any one of claims 1 to 7,

characterized in that the cone segment (5) in an axial direction and a first radial direction, in an extension plane of the cone segment (5) in the guide piston (4) is fixed and in a second radial direction, transversely to the plane of extension, limited displaceable is.

9. Pedalkraftsimulationsvomchtung (1) according to one of claims 1 to 8,

characterized in that the spring elements (8a, 8b) are pivotally received in an insertion sleeve (15) inserted in the interior of the housing (2).

10. actuation system for a motor vehicle clutch with a Pedalkraftsimulationsvomchtung (1) according to one of claims 1 to 9.