JP3269239B2 - Brake pedal device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a brake pedal device, and more particularly to a brake device for a vehicle, in which a characteristic of a lever ratio to a pedal stroke of a brake pedal is appropriately set to realize an excellent operation feeling. It relates to a suitable brake pedal device.

[0002]

2. Description of the Related Art The characteristics of a vehicle brake device are greatly affected by the characteristics of a brake pedal device as an input mechanism. That is, if the lever ratio of the brake pedal device is set to be large, the pedaling force applied to the brake pedal can be greatly boosted and transmitted to the push rod, which is the operating force transmitting member that presses the master cylinder. On the other hand, if the lever ratio is set small, the boosting ability of the pedaling force is reduced, but a large stroke change can be given to the push rod.

Accordingly, in a vehicle brake device in which the lever ratio of the brake pedal device is set to a large value, a large braking force can be obtained with a small depressing force, but a relatively large pedal stroke is required for the brake operation.
This is a characteristic suitable for controlling the stroke of the braking force.

In a vehicle brake device in which the lever ratio of the brake pedal device is set to be small, a relatively large pedaling force is required, but the braking force can be largely changed by a small pedal stroke, and the braking force is reduced. This is a characteristic suitable for controlling the pedaling force.

[0005] Incidentally, it is not appropriate for a vehicle brake device to have uniform characteristics in all situations, and by changing the characteristics in accordance with the pedal stroke of a brake pedal, an operation fee for a brake operation is obtained. It is possible to improve the ring.

As a brake pedal device focusing on the above characteristics, for example, a device described in Japanese Utility Model Laid-Open Publication No. 57-109058 is known. In this brake pedal device, the lever ratio is small in the region where the pedal stroke is small, that is, the stroke change of the push rod with respect to the pedal stroke is large, while the lever ratio is large in the region where the pedal stroke is large, that is, the pedal ratio is small. The structure is such that the change in stroke of the push rod is small.

According to this configuration, the pedal stroke can be reduced in the initial stage of the brake operation, and the pedaling force can be effectively reduced as the reaction force applied to the push rod due to the large depression of the brake pedal increases.

[0008]

When the operability of the vehicle brake is considered, the braking force can be adjusted by the stroke control in a region where the braking force is small, and the braking force can be adjusted by the pedaling force control in a region where the braking force is large. Is desirably adjustable.

However, the characteristics of the above-mentioned conventional brake pedal device show characteristics completely opposite to the required characteristics. For this reason, the conventional pedal device is effective for improving the response of the vehicle brake device and realizing labor saving, but can realize an appropriate operation feeling in consideration of the operability for the driver. It was not something.

The present invention has been made in view of the above points, and comprises a brake lever that operates integrally with a brake pedal, and a rotary link that provides an effective stroke to an input shaft of a brake mechanism. By providing a brake pedal device that solves the above-described problem, the lever ratio can be set more freely with respect to the pedal stroke by connecting with a connection link that swings in response to change the substantial lever ratio. The purpose is to:

[0011]

SUMMARY OF THE INVENTION The above objects are attained in the first round.
The lever portion rotatably supported by a pivot shaft;
A brake pedal having a pedal provided at a position separated from the first rotation support shaft by a predetermined distance; and a brake pedal having a second rotation support shaft.
Together are more rotatably supported, said second rotation support shafts
A pivot link that is connected to the operating force transmitting member at a predetermined distance spaced apart position from the front with the rotation of the brake pedal
Comprising a connecting link for connecting the Burekipeda Le before <br/> Kikaido link to rotate the Kikaido link, wherein the connecting link, the lever ratio with respect to the pedal stroke of the brake pedal pedal so as to have a characteristic change in the upwardly convex in the region of small strokes, the center line or the extension line thereof in the longitudinal direction of the connecting link connecting the second Kaido支 shaft and the first Kaido支 shaft A brake pedal device having a configuration intersecting with a line segment, and receiving a compressive load from a connection portion with the brake pedal to a connection portion with the rotation link in a process of increasing a pedal stroke of the brake pedal. Achieved. The purpose of the above is
At one end of the lever part that is rotatably supported in the
Brake pedal with
It is movably supported and has one end connected to the operation force transmission member.
The pivot link to be connected, the other end of the brake pedal and the front
A connecting link connecting the other end of the rotating link.
The link is connected to the pedals of the brake pedal.
Lever ratio to troke with small pedal stroke
So that the region has an upwardly convex characteristic change.
The longitudinal center line of the link or its extension is
A pivot shaft of the key pedal and a pivot shaft of the pivot link are connected.
The brake pedal
In the process of increasing the pedal stroke of the brake pedal,
Compression from the other end of the dull toward the other end of the pivot link
Also achieved by the brake pedal device under load
You.

[0012]

In the brake pedal device according to the first aspect of the present invention,
When the pedaling force is applied to the brake pedal,
Rotates the brake pedal and transmits to the rotation link
Is done. The rotating link rotates its own while
The transmitted force is transmitted to the operating force transmitting member according to the lever ratio.
Reach. Also, in the brake device according to claim 2 of the present invention , when a pedaling force is applied to the brake pedal, the pedaling force is transmitted to the other end of the brake pedal according to a lever ratio of the lever portion while rotating the brake pedal. Is done.

[0013] The force transmitted to the other end of the brake pedal as described above is transmitted to the rotating link via the connecting link. The rotating link transmits the transmitted force to the push-rod connected to one end thereof according to its own lever ratio while rotating itself.

At this time, the direction of the force transmitted to the bush rod varies depending on the rotation angle of the rotation link, and the operation force transmission member swings with the rotation of the rotation link. For this reason, the moment length formed between the rotation support shaft of the rotation link and the operation force transmitting member varies with the rotation of the rotation link, that is, with the pedal stroke of the brake pedal. .

By the way, the connecting link connecting the brake pedal and the turning link changes the state of transmission of the force between the brake pedal and the turning link according to the posture of the link. Let it. That is, depending on the posture of the connecting link, the displacement generated on the brake pedal is reduced or increased and transmitted to the rotating link.

Further, the posture of the connecting link is restricted by the brake pedal and the rotating link, and changes according to a change in pedal stroke. Such a change in the displacement characteristic of the rotary link with respect to the displacement of the brake pedal is substantially the same as a change in the characteristic of the output stroke that occurs with respect to the input stroke, and the lever ratio of the entire brake pedal device changes. It is equivalent to

Therefore, if the posture change of the connecting link with respect to the pedal stroke is appropriately adjusted, the relationship between the lever ratio and the pedal stroke of the brake pedal device, that is, the rate of change of the lever ratio with respect to the pedal stroke change can be appropriately adjusted. Will be done.

[0018]

FIG. 1 shows an overall configuration diagram of a brake pedal device according to an embodiment of the present invention. In FIG. 1, the brake pedal 10 includes a pedal 14 at one end of a lever portion 12 and is rotatably supported by a rotation support shaft 16 at an intermediate portion.

The other end of the brake pedal 10 is connected to a connecting link 20 via a rotatable connecting portion 18. The connection link 20 is connected to a rotation link 24 via a connection portion 22 that is also rotatable.

The rotation link 24 is rotatably supported at an intermediate portion by a rotation support shaft 26, and the other end of the rotation link 24 is connected to the above-described operating force transmitting member via a connecting portion 28 which is rotatable. It is connected to a corresponding push rod 30.

The push rod 30 constitutes an input shaft of a brake booster 32 for transmitting a boosted driver's treading force to a master cylinder (not shown) for generating a brake hydraulic pressure in a vehicle brake device. The brake booster 30 is swingably provided within a predetermined range.

Therefore, in the brake device including the brake pedal device of the present embodiment, the stroke equivalent to the horizontal displacement of the push rod 30 and the thrust corresponding to the horizontal component of the external force transmitted to the push rod 30 are generated. To the main piston of the master cylinder.

Incidentally, the brake pedal device shown in FIG. 1 avoids interference between the brake pedal 10 and the connecting link 20 and the rotating link 24, and also reduces the size of the whole body by compacting the brake pedal 10 and the rotating link. Although a predetermined bending is given to the 24, when the brake pedal 10 is captured as a link mechanism, the brake pedal 10 is a member having lengths L ₁ and R ₁ indicated by solid lines in FIG. 1 (hereinafter simply referred to as L ₁ and R _1). ), A connecting link 20 is connected to a member having a length Rm (hereinafter referred to as Rm).
), The rotating link 24 is replaced with a member having a length of R ₂ and L ₂ (hereinafter referred to as R ₂ and L ₂ ), and the push rod 30 is
Is replaced by a member having a length L _B (hereinafter referred to as L _B ).

Further, when analyzing how the pedaling force applied to the pedal 14 is transmitted to the brake booster 32, L ₁ , corresponding to the brake pedal 10,
As long as R ₁ and R ₂ and L ₂ corresponding to the rotary link are always maintained at a constant angle, any angle is equivalent.

For this reason, the brake pedal device shown in FIG. 1 can be modeled and represented as shown in FIG.
The analysis model shown in FIG. 2 shows the mutual relationship between R ₁ corresponding to a part of the brake pedal 10, Rm corresponding to the connecting link 20, R ₂ corresponding to a part of the turning link 24, and turning L ₂ corresponding to a part of the link 24, the L _B each correlation corresponding to the push rod 30 is directly reproduced relationship brake pedal apparatus of FIG. 1.

Further, L ₁ ,
_{R 1, Rm, R 2,} L 2, L B is the pedal stroke S
_P is “0”, that is, a non-braking state, and L ₁ , R ₁ , Rm, R ₂ , L ₂ , L ₂ indicated by a chain line in FIG.
_B indicates a state in which the pedal 14 has appropriately stroked.

When operating the brake pedal 10, the brake pedal device of this embodiment adjusts the braking force by stroke control in a region where the pedal stroke _SP is relatively small and a region in which the pedal stroke _SP is relatively large. Is characterized in that it is configured to realize braking force adjustment by pedal force control.

That is, in the brake pedal device of the present embodiment, in a region where the pedal stroke _SP is relatively small as described later, the ratio of the input side moment length to the output side moment length, which is the effective moment length for the brake booster 32, is used. lever ratio R _P is large, the pedal stroke S _P is the lever ratio R _P is changed smaller with the increase.

[0029] In this case, the horizontal stroke of the brake operation initial been reduced pedal stroke S _P is greater push rod 30 (hereinafter, referred to as effective stroke) to be converted into S _B, excellent properties stroke controllability There is implemented, whereas in the region where the pedal 14 is depressed fully, the pedal stroke S _P is converted to the effective stroke S _B without being reduced so much, because a slight pedal stroke S _P changes causing a large braking force change Thus, characteristics excellent in controlling the pedaling force are realized.

By the way, as a mechanism to increase the lever ratio R _P with the increase of the pedal stroke S _P, the brake pedal apparatus of FIG. 3 are known in the prior art, the brake pedal apparatus of this embodiment, FIG. Compared with the conventional device shown in FIG. 3, the present invention has a feature that ideal characteristics can be realized as a vehicle brake device.

Before describing the effects peculiar to the brake pedal device of the present embodiment, the structure and operation of the brake pedal device shown in FIG. 3 will be described for comparison.

In the brake pedal device shown in FIG. 3, the brake pedal 40 comprises a lever portion 42 and a pedal 44 connected to one end of the lever portion 42. The other end of the lever portion 42 is rotatably supported by a rotation support shaft 46 fixed to the vehicle body. In addition, a push rod 50 is connected to an intermediate portion of the lever portion 42 via a rotatable connecting portion 48.

The push rod 50 constitutes an input shaft of a brake booster (not shown), and transmits a thrust corresponding to the pedaling force applied to the pedal 44 to the brake booster. Here, the push rod 50 is provided so as to be able to swing vertically with respect to the brake booster. Accordingly, the brake pedal 40 is rotated, the connecting portion 48 is displaced with it, the other end of the push rod 50 strokes in the horizontal direction with the effective stroke S _B.

[0034] In this case, for the brake pedal apparatus of FIG. 3, replace the brake pedal 40 to the member of the lengths L _1, L _2, and by replacing the push rod 50 and the member of length L _B, FIG. 3 An analysis model indicated by a solid line and an alternate long and short dash line therein can be assumed.

In FIG. 3, the angle between the member L _{2 and the} horizontal direction is θ ₀ , and the angle between the member L _{B and the} horizontal direction is θ.
_B, and represents the vertical distance between the brake booster end of the rotating shaft and the member L _B and Lh, also operating angle member L _1, i.e. the operating angle of the brake pedal 10 as theta _1.

[0036] When defining the parameters as shown in FIG. 3, the input side the moment the length of the brake pedal device, the pedal 44 and the pivot shaft 46 a distance, that is, L _1.
On the other hand, the output side moment length of the brake pedal device, that is, the point where a horizontal force acts upon the rotation of the brake pedal 40 (the member L when the perpendicular is lowered from the rotation support shaft 46 as shown by the broken line in FIG. 2) (Intersection with _B ) and pivot 4
Distance and 6, the initial setting value theta _0, L _2, as a function of the operating angle theta _1, and member L _B in the horizontal direction and the angle theta _B, L ₂
sin (θ ₀ + θ ₁ + θ _B ) / cos θ _B

Therefore, in the brake lever device shown in FIG. 3, the lever ratio R _P, which is the ratio of the input side moment length to the output side moment length, can be expressed as follows.

[0038]

(Equation 1)

By the way, θ _B in the above equation (1) can be expressed as follows using the initial set values Lh, θ ₀ and the operating angle θ ₁ .

Θ _B = sin ⁻¹ {(Lh−L ₂ sin (θ ₀ + θ ₁ )) / L _B } (2) The operating angle θ ₁ is the pedal stroke _SP and the initial set value. it can be expressed as follows as a function of L _1.

[0041] _{θ 1 = S P / L 1} ··· (3) Accordingly, the lever ratio R _P shown in equation (1) as a function of only the pedal stroke S _P as a parameter, it is expressed as follows it can.

[0042]

(Equation 2)

[0043] At this time, the effective stroke is the displacement amount of the tip of the push rod 50 S _B, the connecting portion 48 and the amount of change in the horizontal direction component of the member L _B associated with that theta _B changes
Of can be determined as the sum of the horizontal displacement can be expressed as a function of the following as the pedal stroke S _P.

[0044] ^{_{S B = √ {L B 2}} - (Lh-L 2 sin (θ 0 + S P / L 1)) 2} -√ {L B 2 - (Lh-L 2 sinθ 0) 2} + L 2 cosθ _{0 -cos (θ 0 + S P} / L 1) ··· (5) Thus, in the brake pedal apparatus of FIG. 3, the lever ratio R _P, and the effective stroke S _B, both the pedal stroke S _P As a function of In order to increase the rate of change of the lever ratio R _P with respect to the pedal stroke S _P is 3, and from equation (4), it is effective to increase the swing angle of the push rod 50 it is obvious.

However, the swing angle of the push rod 50 must be kept within the range of the twist that can be tolerated with respect to the brake booster. To avoid this, the brake booster is largely separated from the brake pedal device. Need arises. FIG. 4 shows an example of designing the brake pedal device shown in FIG. 3 in consideration of such points.

The trend in this case, the relationship between the lever ratio R _P and the pedal stroke S _P output as a brake pedal apparatus, the lever ratio R _P with the increase of the pedal stroke S _P, as shown by the broken line is lowered in FIG. 5 next, as a brake device excellent stroke controllability in the region pedal stroke S _P is small, the region pedal stroke S _P is large can be obtained excellent properties pedal force control.

However, the conventional brake pedal device shown in FIGS. 3 and 4 has a pedal stroke S
_{Since the} rate of change of the lever ratio R _P with respect to _P cannot be adjusted, and the rate of change of the swing angle of the push rod 50 must be larger in a region where the pedal stroke _SP is smaller, FIG. as the lever ratio in idle region R _P rate of change indicates the characteristic over the rate of change of the lever ratio R _P in practical range.

According to such characteristics, if the stroke control and the pedaling force control are to be appropriately realized in the practical range, the lever ratio _RP must be changed abruptly in an idle region, which is a so-called play region. As a result, the idle stroke is increased by a slight error, and it is difficult to obtain a good operation feeling.

The brake pedal device of this embodiment is invented in order to solve the above-mentioned problems and to realize an excellent operation feeling. As the pedal stroke S _P increases, the lever ratio R _P increases. And pedal stroke S
_{In an} idle region where _P is extremely small, the rate of change of the lever ratio R _P is smaller than in a practical range.

Hereinafter, the operation of the brake pedal device of the present embodiment will be described with reference to the analysis model shown in FIG.

In FIG. 2, a point corresponding to the pivot 26 is represented as point A, and a point corresponding to the pivot 16 is represented as point B. Further, a straight line connecting point A and point B (hereinafter simply referred to as A
B and referred) a member R ₁ is an angle at the time of non-braking theta relative _m1 (sign and negative), the angle formed by members R ₂ theta
_m2 (sign and negative), also member L ₂ represents a horizontal direction and angle as theta _0.

Further, it changes with the stroke of the pedal 14.
The moving parameters include the member L ₁Ie brake
The operating angle of the pedal 10 is θ₁, The associated member L_TwoRotation of
Angle, that is, the rotation angle of the rotation link 24 is θ_Two, Member Rm
Is the angle between_FIt is expressed as

[0053] In the brake pedal device configured as shown in FIG. 2, if the rotating small angle d [theta] ₁ is generated in member L _1, the rotation displaces is transmitted by members R ₁ a member Rm in the axial direction . At this time, the moment lengths for members Rm, the distance between Rm and the rotation support shafts 16, i.e. the distance and equidistant shown in FIG. 2 M _1, minute displacement amount d [alpha] of the member Rm is d [alpha] = M ₁ · dθ ₁ .

On the other hand, when the small displacement dα occurs member Rm, member L distance of displacement the member Rm and the pivot shaft 26, i.e. the distance indicated in Figure 2 in M ₂ as a moment length
₂ to generate a minute rotation angle dθ ₂ in the member L ₂ and the member R ₂ .

Here, the member R_TwoThe connecting portion 22 of the member R
m, the amount of displacement is dα as described above.
Equal, thus M₁・ Dθ₁= M_Two・ Dθ_TwoIe
dθ _Two= (M₁/ M_Two) Dθ₁Is to hold
You. That is, in the present embodiment, the brake pedal 10
Operating angle dθ input to₁Is M₁/ M_TwoRotated phosphorus
Transmitted to the client 24.

This means that, as shown in FIG.
In a device whose operating angle is equal to that of the output side, L₁Input
Pedal stroke S against moment length_PAnd give
Rotation angle S on output side_P/ L₁In this embodiment,
At the rotation angle (M₁/ M _Two) ・ S_P/ L₁Occurs
Means that.

[0057] Such phenomenon is constructive and although those caused by the action of the member Rm, which is the original L input torque length L ₁ that is set to the length of _{1 L 1 · (M 2 / M} 1) Then, the brake pedal device of the present embodiment can be treated as a device in which the input side operation angle and the output side rotation angle are equal.

On the other hand, a member L corresponding to the rotation link 24_Two
And the member L corresponding to the push rod _BIs determined by the positional relationship with
The output side moment length to be set is the same as the conventional device shown in FIG.
2, a perpendicular line passing through the pivot 26 shown by a broken line in FIG.
Is the member L_BBetween the point of intersection with the pivot 26
It is enough if you grasp, the member L_BIs the angle between_BWhen
Then, L_Twosin (θ₀+ Θ₁+ Θ_B) / Cos θ_BExpress
be able to.

Here, θ_BAbout the above equation (2)
Similarly, θ_B= Sin^-1｛(Lh-L _Twosin (θ₀+
θ_Two)) / L_BSince it can be expressed as｝, the book
Lever ratio R of the brake pedal device of the embodiment_PIs, after all,
It can be expressed as an equation.

[0060]

(Equation 3)

Accordingly, in FIG. 6, θ ₂ and M ₂ / M
If it is possible to represent a ₁ as a function of the pedal stroke S _P, it is possible to grasp the lever ratio R _P as a function of the pedal stroke S _P for the brake pedal device of the present embodiment.

By the way, in FIG. 2, if the distances from the points A and B to the intersection of the extension line of the member Rm and AB are defined as m ₂ and m ₁ , respectively, m ₂ / m ₁ = M ₂ / M ₁
It is clear that holds.

At this time, m ₁ is an initial set value of R ₁ ,
It can be expressed as follows using θ _m1 and parameters θ ₁ and θ _F.

M₁= R₁cos (θ_m1+ Θ₁) -R₁sin (θ_m1+ Θ₁) Tanθ_F .. (7) Further, in the above equation (7), θ_FAbout initial, in FIG.
Setting values AB and θ _m2, And the parameter θ_TwoTo
It can be expressed as follows.

[0065]

(Equation 4)

[0066] In this case, theta ₁ is because it can be grasped as a function of the pedal stroke _{S P (θ 1 = S P} / L 1), if it is possible to grasp the theta ₂ as a function of the pedal stroke S _P, m ₁ can be calculated as a function of the pedal stroke S _P. Further, if it is possible to calculate the m _1, it is possible to obtain the m ₂ by m ₂ = AB-m ₁ comprising an arithmetic expression by using the result, therefore m
₂ / m _1, i.e. it is possible to grasp in equation (6), a M ₂ / M ₁ as a function of the pedal stroke S _P.

[0067] Incidentally, in the brake pedal apparatus of the present embodiment, the distance between the connecting portion 22 of the connecting portion 18 and the member R ₂ members R ₁ is constantly maintained at Rm, which brake pedal 10 and the pivot It is a constraint condition with the link 24. That, theta ₁ varies with changes in the pedal stroke S _P, and theta ₂ is constantly changing while satisfying the relationship shown below.

Rm ² = {R ₂ sin (θ _m2 + θ ₂ ) −R ₁ sin (θ _m1 + θ ₁ )} ² + ΔAB−R ₂ cos (θ _m2 + θ ₂ ) −R ₁ cos (θ _m1 + θ ₁ )｝ ² ··· (9) By rearranging this equation for (θ _m2 + θ ₂ ), a quadratic equation such as the following equation is obtained.

A · cos (θ _m2 + θ ₂ ) ² + b · cos (θ _m2 + θ ₂ )｝ + c = 0 (10) where a, b, and c are the following coefficients.

[0070]

(Equation 5)

[0071] Solving this, it is possible to capture the as follows theta ₂ as a function of theta _1, therefore, it is possible to capture the theta ₂ as a function of the pedal stroke S _P,
When the lever ratio R _P shown in the above equation (6) is changed to the pedal stroke S
It can be expressed as a function of _P.

Cos (θ _m2 + θ ₂ ) = {− b ± {(b ² −4ac)} / (2a) (11) Therefore, when (θ _m1 + θ ₁ ) ≦ 0, θ _m2 + θ ₂ = cos ^-1 ｛(-b + √ (b ² -4ac) /
(2a) When｝ (θ _m1 + θ ₁ )> 0, θ _m2 + θ ₂ = cos ^-1 ｛(-b-√ (b ² -4ac) /
(2a)} curve shown with a solid line in FIG. 5, on the basis of the above relationship, the result of calculating the relationship between the lever ratio R _P and the pedal stroke S _P of the brake pedal device of the present embodiment. As apparent from the figure, the lever ratio R _P of the brake pedal apparatus of this embodiment, FIG 3, gently at idle region as compared with the conventional brake pedal apparatus of FIG. 4, rapidly in its practical range By changing the value, the characteristic is ideal as a brake pedal device.

Table 1 below shows that the pedal stroke _SP is 0
The dimensions of each part of the apparatus of this embodiment realizing a variable rate of 0.366% / mm at １００100 mm are illustrated. Table 2 shows the apparatus of this embodiment and the conventional apparatus shown in FIG.
Shows the results of performance comparison when assuming an idle region and 20 to 80 as a practical region.

[0074]

[Table 1]

[0075]

[Table 2]

As described above, the reason why the brake pedal device of the present embodiment exhibits excellent characteristics as compared with the conventional device is that the above-mentioned M ₂ / M ₁ , that is, m ₂ / m ₁ is the idle region end position. This is because it is configured to be maximum in the vicinity.

That is, in the brake pedal device of the present embodiment, the lever ratio _RP increases as far as the operation of the connecting member 22 is concerned in the process in which the brake pedal 10 strokes from the non-braking state toward the idle region end region. When the brake pedal 10 passes through idle area end position, thereafter the connecting link 20 serves to facilitate the lowering of the lever ratio R _P.

[0078] By the action of this result, the pivot link 24 and the push rod 30, in conjunction with the lever ratio R _P with the increase of the pedal stroke S _P is lowered as a whole the brake pedal device, the pedal stroke S It reduces the lever ratio R _P with increasing _P, and the characteristics of the rate of change is minimum in the idle region end position near, that is, the brake pedal device-specific characteristics of the present embodiment is realized.

[0079] Incidentally, in the brake pedal apparatus of the present embodiment, in order to suppress the rocking of the push rod 30, and the vicinity of 90 ° in angle practical range of the member L ₂ and the push rod 30 as shown in FIG. 1 For example, the angle is set to about 70 ° when no braking is performed.

For this reason, as shown in Table 1 above, the swing angle of the push rod 30 can be reduced as compared with the conventional device, which can contribute to the improvement of the reliability of the device. Further, for reasons such as the advantage of suppressing the swing angle of the push rod 30, as shown in Table 1,
It can be remarkably reduced as compared from the tip of the push rod 30 a distance L _X to pivoting axles 16 of the brake pedal 10 to a conventional device. For this reason, according to the brake pedal device of the present embodiment, it is possible to realize superior mountability as compared with the conventional device.

FIG. 6 shows the brake pedal device shown in FIG. 3 described above, similar to the device of this embodiment.
0 the distance L _X from the tip to the rotation shaft of the brake pedal is analysis model when set to 65 mm, Table 3 below, formed by appropriately setting each parameter other than L _X ~
The following shows the result of calculating the characteristics for the specifications.

[0082]

[Table 3]

In this case, in order to secure the leg space of the vehicle, there is actually no possibility other than the specifications in Table 2 above. As for the specifications, a variable rate of only about 0.18% / mm can be secured in a practical range. In practice, since the variable rate of the lever ratio R _P is about 0.3% / mm is necessary, in substantially the configuration shown in FIG. 3 L _X =
In this sense, the brake pedal device of the present embodiment is particularly effective when strict restrictions are imposed on its mounting space.

Incidentally, the brake pedal device shown in the above embodiment is a brake pedal device which is assumed to be operated during traveling. However, the brake pedal device according to the present invention is not limited to such a device, but is used for a parking brake. It can also be applied to the brake pedal device.

A brake pedal device for a parking brake is required to be able to generate a sufficient braking force with a short operation stroke and a light pedaling force, without regard to controllability. Therefore, as a characteristic of the lever ratio with respect to the pedal stroke, it is preferable that the lever ratio is small in a small stroke region where the reaction force is small and high in a large stroke region where the reaction force is large.

On the other hand, in the brake pedal device according to the present invention, the characteristics of the lever ratio can be set relatively freely by appropriately setting the swinging state of the connecting link, and the brake lever satisfying the above requirements can be set. Since the device can be realized, a brake pedal device for a parking brake having excellent characteristics can be realized.

FIG. 7 shows an overall configuration diagram of a brake pedal device designed to satisfy the above characteristics as another embodiment of the present invention. Brake pedal apparatus shown in FIG. Operate the brake pedal 60 to the distance R ₁ is configured to 50mm from the pedal 62 a distance L ₁ to the rotating shaft 64 is 240 mm, until the coupling portion 66 from the rotation support shafts 64 By doing so, it is a mechanism for giving a desired stroke to the cable 68 corresponding to the above-mentioned operation force transmitting member.

Here, in this embodiment, the connecting portion 66 of the brake pedal 60 has an effective length Rm of 20 mm.
Are connected. The other end of the connecting link 70 is connected via a connecting portion 72 to a rotating link 76 having a distance R ₂ of 60 mm to a pivot 74. A cable 68 is also connected to the connecting portion 72. Thus, L ₁ is the distance from the pivot shaft 74 to the distal end of the cable 72, the same 60mm and R _2.

In the brake pedal device shown in FIG. 7, the length L _B of the cable 68 at the time of specific braking is 120 mm, and the vertical distance Lh from the pivot 74 to the cable 68 is 57 mm.
mm, the distance AB between the rotation support shafts 64 and 74 is set to 100 mm, and the initial set angles of θ _m1 and θ ₀ are set to −50, respectively.
° and 80 °.

According to the above design, the pedal stroke 1
A cable stroke of 23.57 mm can be ensured with respect to 20 mm, and as shown by a solid line in FIG. 8, characteristics such that the lever ratio increases as the pedal stroke increases can be obtained. The specific numerical values are shown in Table 4 below.

[0091]

[Table 4]

In FIG. 8, the characteristic shown by the broken line shows the characteristic when the lever ratio is fixed at 5.09 to obtain a cable stroke of 23.57 mm for a pedal stroke of 120 mm. However, when the two characteristics are compared, it is apparent that the brake pedal device of this embodiment achieves a higher lever ratio in a large pedal stroke region, that is, in a region where the reaction force is large.

Therefore, according to the brake pedal device for a parking brake shown in FIG. 7, it is possible to secure a sufficient braking force with a short pedal stroke and a light pedaling force as compared with a device generally used in the past. It is.

[0094]

As described above, according to the present invention, the setting of the lever ratio characteristic with respect to the pedal stroke can be performed with a relatively high degree of freedom. For this reason, for example, in a brake pedal device operated during driving, stroke control is performed in a region where braking force is relatively small.
In a region where the braking force is relatively large, the braking force can be operated by the pedaling force control.

Further, when it is necessary to sufficiently generate a braking force with a short pedal stroke and a light pedaling force as in a brake pedal device for a parking brake, an appropriate lever ratio characteristic suitable for such a characteristic is realized. be able to.

As described above, the brake pedal device according to the present invention has a higher degree of freedom in setting characteristics as compared with the conventional brake pedal device, and realizes an excellent operation feeling by accurately reproducing required characteristics. It has the feature of being able to.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram of a brake pedal device according to an embodiment of the present invention.

FIG. 2 is a diagram for explaining the operation of the brake pedal device of the present embodiment.

FIG. 3 is an overall configuration diagram of a conventional brake pedal device.

FIG. 4 is a diagram showing a physique necessary for satisfying required characteristics in a conventional brake pedal device.

FIG. 5 is a diagram illustrating a relationship between a pedal stroke and a lever ratio of the present embodiment and a conventional brake pedal device.

FIG. 6 is a diagram illustrating a configuration example for obtaining the same mountability with the conventional brake pedal device as the brake pedal device of the present embodiment.

FIG. 7 is an overall configuration diagram of a brake pedal device according to another embodiment of the present invention.

FIG. 8 is a diagram illustrating a relationship between a pedal stroke and a lever ratio of the brake pedal device of the present embodiment.

[Explanation of symbols]

10, 60 Brake pedal 12 Lever part 14, 62 Pedal 16, 26, 64, 74 Rotation support shaft 18, 22, 28, 66, 72 Connection part 20, 70 Connection link 24, 76 Rotation link 30 Push rod 32 Brake booster _{L 1, R 1, Rm,} R 2, L 2, L B member 68 cable

Continuation of the front page (56) References JP-A-59-180713 (JP, A) JP-A-5-185912 (JP, A) JP-A-57-84248 (JP, A) JP-A-57-109058 (JP, A) , U) Japanese Utility Model Application No. 4-40319 (JP, U) Japanese Utility Model Application Model No. 1-87069 (JP, U) Japanese Utility Model Application No. 51-40582 (JP, Y2) (58) Fields surveyed (Int. Cl. ⁷ , DB Name) B60T 7/06 G05G 1/14

Claims (2)

(57) [Claims] A first rotation support shaft rotatably supported by the first rotation support shaft;
A predetermined distance from the first pivot shaft
A brake pedal comprising comprising a pedal provided at a position, while being rotatably supported by a second rotation support shafts, before
The rotation link connected to the operation force transmitting member at a position separated from the second rotation support shaft by a predetermined distance, and the rotation link rotates with the rotation of the brake pedal.
And a connecting link for connecting the pivot link and the Burekipeda Le order to moving, the connecting link is convex characteristic change on the lever ratio in a region of small pedal stroke with respect to the pedal stroke of the brake pedal The center line in the longitudinal direction of the connecting link or an extension thereof is the first rotation.
It has a configuration which intersects the line segment connecting the supporting shaft and said second Kaido支 axis and said pivot link connection portion between the brake pedal during the pedal stroke of the brake pedal is increased A brake pedal device, which receives a compressive load toward a connecting portion of the brake pedal. 2. A lens rotatably supported at an intermediate portion.
A brake pedal having a pedal at one end of a bar portion, and a rotatably supported intermediate end portion having one end operated.
A rotating link connected to the working force transmitting member, and the other end of the brake pedal and the other end of the rotating link.
And a connecting link for connecting the brake pedal to the brake pedal.
Area where the lever ratio to the brake stroke is small
In the above, the connecting phosphorus
The longitudinal centerline of the brake or its extension is
Line connecting the pivot of the dull and the pivot of the pivot link
Has a configuration that intersects with the minute, and
As the pedal stroke increases, the brake pedal
From the other end of the rotating link toward the other end of the rotating link.
A brake pedal device characterized by receiving a brake pedal.