METHOD FOR DETECTING CHANGES IN THE RIGIDITY OF A HYDRAULIC BRAKE SYSTEM

Abstract

In a method for detecting air in the brake circuit of a motor vehicle having a hydraulic brake system that has a vacuum brake booster, the pressure prevailing in the vacuum chamber of the vacuum brake booster in the operated and the non-operated states of the brake is measured, and a parameter characteristic of the brake performance is determined as a function of the measured pressure, and the characteristic parameter is compared to a reference value.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a method for detecting changes in rigidity of a hydraulic passenger car brake system, as well as a control unit having an algorithm for carrying out the method.

2. Description of Related Art

In known hydraulic passenger car brake systems, changes in the brake characteristics are able to come about especially by air inclusions in the brake fluid. Changes in the brake performance characteristics are normally able to be detected by the driver when operating the brake pedal, since a longer pedal path has to be covered to achieve the same vehicle deceleration. This is only true, however, for the usual hydraulic brake systems, in which a mechanical feedthrough exists between the brake pedal and the brake caliper. By contrast, brake systems in which the brake pedal is mechanically decoupled from the remainder of the brake system give no feedback via the brake pedal.

BRIEF SUMMARY OF THE INVENTION

An object of the present invention is to provide a method by the use of which rigidity changes in brake systems (hydraulic ones and also ones that are decoupled) are able to be detected automatically.

One aspect of the present invention is to measure the pressure prevailing in the vacuum chamber of the vacuum brake booster in the operated and the non-operated state of the brake, and from the measured pressures to calculate a characteristic parameter that is characteristic for the break performance, such as the path covered by the booster diaphragm or the main brake cylinder, the volume displaced by the main brake cylinder or just simply the pressure difference in the two states, and to compare this characteristic variable to a reference value. This makes it possible to detect a change in the rigidity of the brake system based on the measured vacuum chamber pressure alone.

The reference value is preferably calculated as a function of the hydraulic brake pressure (e.g. of the admission pressure) or is determined with the aid of a characteristics curve.

According to one example embodiment of the present invention, the pressure difference between the vacuum chamber pressure in the operated and the non-operated state is calculated and compared to the reference value. The reference value Δp may, for instance, be calculated using the following relationship

$\begin{array}{cc}\Delta p=p_{\mathrm{FC}}^{\mathrm{Rel}.}-p_{\mathrm{FC}}^{\mathrm{Appl}.}=\frac{\left(S_B+\frac{V_{\mathrm{RC}}^{\mathrm{Rel}.}}{A_B}\right)·\left(\begin{array}{c}{p}_{\mathrm{MC}}^{\mathrm{Appl}.}·\left(A_{\mathrm{MC}}+\alpha \right)+\\ D·S_B+F_0\end{array}\right)}{V_B}& \left(1\right)\end{array}$

as a function of the hydraulic brake pressure p_MC^Appl., or ascertained from an appropriate characteristics curve. (For the explanation of the formula, see special figure description).

In the method according to the first example embodiment, the vacuum chamber pressure is preferably first measured in the operated state of the brake, and after that in the non-operated state.

According to a second example embodiment of the present invention, the path covered by the diaphragm of the vacuum brake booster, or a quantity proportional to it, is determined as a function of the measured vacuum chamber pressures in the operated and the non-operated state. The path s covered by the diaphragm may be ascertained, for instance, according to the following relationship:

$\begin{array}{cc}{S}_B^{\mathrm{Appl}.}=\frac{V_{\mathrm{FC}}^{\mathrm{Rel}.}-V_{\mathrm{FC}}^{\mathrm{Appl}.}}{A_B}=\frac{V_{\mathrm{FC}}^{\mathrm{Rel}.}}{A_B}·\left[1-{\left(\frac{r_{\mathrm{FC}}^{\mathrm{Rel}.}}{p_{\mathrm{FC}}^{\mathrm{Appl}.}}\right)}^{1/\kappa }\right]& \left(2\right)\end{array}$

(For the explanation of the formula, see special figure description).

From the path s thus calculated, a volume displaced by the main brake cylinder is preferably calculated. This volume V_MC may be calculated as follows, for instance:

V _MC =A _MC·(S_B^Appl.−S₀)   (3)

Volume V_MC determined from the vacuum pressures is preferably compared to a volume ascertained from a p/V characteristics line. If the deviation is greater than a specified threshold value, a change in the rigidity of the brake system is detected. This may be displayed to the driver, for example, using a control lamp or another device.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

FIG. 1 shows a schematic view of a vacuum brake booster.

FIG. 2 shows a flow chart of the steps of a method for detecting changes in the rigidity of a break system, according to a first example embodiment.

FIG. 3 shows a flow chart the steps of a method for detecting changes in the rigidity of a break system, according to a second example embodiment.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 shows a schematic representation of a usual vacuum brake booster (UBKV). The UBKV essentially includes a working chamber 2, a vacuum chamber 1 having a vacuum connection 3 and a diaphragm 7, which is situated between the two chambers 1, 2. A vacuum source (not shown) is connected to vacuum connection 3, which is driven, for instance, by the internal combustion engine, and generates a specified vacuum in vacuum chamber 1. In the central region of UBKV 8 there is a double valve 4 which fulfills two functions, namely a) to separate working chamber 2 from vacuum chamber 1, or to connect the two chambers 1, 2 to each other, and b) to ventilate working chamber 2 or to separate it from the environmental air.

In the non-braked state, the connection between vacuum chamber 1 and working chamber 2 is open. In both chambers 1, 2 there consequently prevails the same vacuum. When the brake pedal is operated, the two chambers 1, 2 are separated from each other and working chamber 2 is ventilated.

As a function of the path set via piston rod 6, a pressure difference sets in between the pressure in vacuum chamber 1 and the environmental pressure. The force resulting from the pressure difference on working diaphragm 7 boosts the brake force via piston rod 6, in this instance. After the release of force F, the ventilation using environmental air is interrupted and the chamber valve is opened again. Because of this, both chambers 1, 2 have a vacuum applied to them by the vacuum source.

In contrast to known UBKV's, the UBKV 8 shown includes a sensor system 9, 10, 11, by which changes in the force-path characteristics of the vacuum brake booster are able to be detected. The sensor system, in this case, includes a pressure sensor 9 situated in vacuum chamber 1, whose output signal is evaluated by a control unit 11, and a pressure sensor 10 for measuring a hydraulic brake pressure (admission pressure), which is also connected to control unit 11.

Variant 1: Determination of the Rigidity when the Brake Pedal is Released

According to a first example embodiment of the present invention, the pressure prevailing in vacuum chamber 1 is first measured in the operated state and then in the released state of the brake, and a pressure difference is formed from this. This pressure difference is finally compared to a reference value.

FIG. 2 shows the method steps of this method.

In step 15 it is first monitored whether the foot brake pedal has been operated and held constant over a predefined short time period, for instance, at least 500 ms. In addition, it is checked whether the vacuum prevailing in vacuum chamber 1 is constant. If both conditions are satisfied, in step 16 a measurement takes place of the vacuum p_FC^appl in vacuum chamber 1 (the subscript appl=applied or operated, FC=front chamber or vacuum chamber), as well as of the hydraulic brake pressure p_MC^appl (subscript MC=master cylinder or main brake cylinder).

In the following step 17 it is monitored whether the direction of motion of the pedal is changing and the brake is released. When the foot brake pedal is released for a predefined short time, and the pressure prevailing in vacuum chamber 1 is constant over a predefined time period, in step 18 a pressure measured value p_FC^Rel. (superscript Rel=released), is taken up, on which the following calculation is based.

In step 19 the pressure difference Δp=p_FC^Rel.−p_FC^Appl. is then formed from the two measured values.

The following equation is applied for the reference value:

$\begin{array}{cc}{p}_{\mathrm{FC}}^{\mathrm{Rel}.}-p_{\mathrm{FC}}^{\mathrm{Appl}.}=\frac{\left(S_B+\frac{V_{\mathrm{RC}}^{\mathrm{Rel}.}}{A_B}\right)·\left(\begin{array}{c}{p}_{\mathrm{MC}}^{\mathrm{Appl}.}·\left(A_{\mathrm{MC}}+\alpha \right)+\\ D·S_B+F_0\end{array}\right)}{V_B}& \left(1\right)\end{array}$

In the equation, α denotes the pressure-dependent friction of the seals in the brake cylinder, D the force of the springs and the pressure-dependent friction, and F₀ the initial force which has to be present via a pressure difference at diaphragm 7 before the diaphragm moves from its position of rest. Furthermore, A_MC is the effective area of the main brake cylinder and s_B is the path covered by the diaphragm or the main brake cylinder.

Formula (1) may be derived from the following considerations. For the entire air volume V_B in vacuum brake booster 8, the following applies:

V _B=const.=V_FC^Rel.+V_RC^Rel.=V_FC^Appl.+V_RC^Appl.   (4)

p _FC ^Rel. ·V _B =p _FC ^Appl. V _FC ^Appl. +p _RC ^Appl. V _RC ^Appl.   (4)

In equation (4) it was assumed that the connection of vacuum chamber 1 to the vacuum supply was interrupted during the discharge. If this is not the case, the pressure of vacuum supply p_vac is first determined by measuring the pressure in vacuum chamber 1, while the vacuum brake booster is not being operated. During the discharge, the pressure in vacuum chamber 1 is constantly measured. From the difference of chamber pressure p_RC and the vacuum pressure, the air mass flowing out during the discharge is able to be determined:

Δm=A_c∫Ψ(p_RC,p_vac)dt

using the function:

$\psi =\mathrm{const}.=p_0\sqrt{\frac{2}{\mathrm{RT}}}\sqrt{\frac{\kappa }{\kappa +1}}{\left(\frac{2}{\kappa +1}\right)}^{\frac{1}{\kappa -1}}\mathrm{for}p_{\mathrm{vac}}<{p_{\mathrm{RC}}\left(\frac{2}{\kappa }\right)}^{\frac{\kappa }{\kappa +1}}$ $\psi =p_0\sqrt{\frac{2}{\mathrm{RT}}}\sqrt{\frac{\kappa }{\kappa -1}}\sqrt{{\left(\frac{p_{\mathrm{vac}}}{p_{\mathrm{RC}}}\right)}^{\frac{2}{\kappa }}-{\left(\frac{p_{\mathrm{vac}}}{p_{\mathrm{RC}}}\right)}^{\frac{\kappa +1}{\kappa }}}\mathrm{for}p_{\mathrm{vac}}\ge {p_{\mathrm{RC}}\left(\frac{2}{\kappa }\right)}^{\frac{\kappa }{\kappa +1}}$

In order to be able to calculate the displacement s_B of diaphragm 7 from equation (5), the pressure p_RC^Appl. prevailing in working chamber (subscript RC=rear chamber) has to be determined in the operated state. For this, we observe the force equilibrium between the main brake cylinder and diaphragm 7 in the operated state:

p _MC ^Appl. ·A _MC +p _MC ^Appl. ·α+D·S _B +F ₀ =A _B(p_RC^Appl.−p_FC^Appl.)   (6)

In the equation, α denotes the pressure-dependent friction of the seals in the brake cylinder, D the force of the springs (diaphragm and main brake cylinder) and the path-dependent friction, and F₀, the initial force, which has to be present via a pressure difference at diaphragm 7 before the diaphragm moves from its position of rest.

Equation (6) applies only for systems not having mechanical coupling. In the case of the usual vacuum brake boosters, the equation should be modified to the extent that input force F_in is taken into consideration:

p _MC ^Appl. ·A _MC +p _MC ^Appl. ·α+D·S _B +F ₀ =A _B(p_RC^Appl.−p_FC^Appl.)+F_in

Provided the saturation point of the vacuum brake booster has not been reached (which may be detected on p_MC) the boosting may be approximated linearly:

A _B(p_RC^Appl.−p_FC^Appl.)=βF_in

using boost factor β. Now, if the quantity A_B is replaced by

$A_B\left(1+\frac{1}{\beta }\right),$

equation (6) keeps its validity even in the case of the usual vacuum brake boosters.

From equations (5) and (6) one may now calculate path s_B of diaphragm 7 during the release of the pedal:

$\begin{array}{cc}{S}_B=-\left(\frac{A_B}{2·D}·X+\frac{V_{\mathrm{RC}}^{\mathrm{Rel}.}}{2·A_B}\right)+\sqrt{\begin{array}{c}\left(\frac{A_B}{2·D}·X+\frac{V_{\mathrm{RC}}^{\mathrm{Rel}.}}{2·A_B}\right)+\\ \frac{\left(p_{\mathrm{FC}}^{\mathrm{Rel}.}-p_{\mathrm{FC}}^{\mathrm{Appl}.}\right)·V_B-V_{\mathrm{RC}}^{\mathrm{Rel}.}·X}{D}\end{array}}& \left(7\right)\\ X:=\frac{p_{\mathrm{MC}}^{\mathrm{Appl}.}·\left(A_{\mathrm{MC}}+\alpha \right)+F_0}{A_B}& \left(8\right)\end{array}$

Path s_B, calculated from equations (7) and (8) could be directly compared (or rather, after recalculating of path s_B into a volume V) to the pV characteristics curve for the brake system. From the difference of the two values one could consequently determine whether air inclusions are present or not.

Since, however, formula (7) in its present form can only be calculated with great effort in a control unit, and since, for the application, it is only of interest when the volume take-up in the brake system is exceeding a certain limit, we propose the following procedure.

First, equations (7) and (8) are solved according to pressure difference p_FC^Rel.−p_FC^Appl. operated and released state, so that the following equation is obtained:

$\begin{array}{cc}{p}_{\mathrm{FC}}^{\mathrm{Rel}.}-p_{\mathrm{FC}}^{\mathrm{Appl}.}=\frac{\left(S_B+\frac{V_{\mathrm{RC}}^{\mathrm{Rel}.}}{A_B}\right)·\left(p_{\mathrm{MC}}^{\mathrm{Appl}.}·\left(A_{\mathrm{MC}}+\alpha \right)+D·S_B+F_0\right)}{V_B}& \left(9\right)\end{array}$

In this equation, only path s_B, covered by the main cylinder, is unknown. This quantity may be determined via the following equation, as a function of the hydraulic admission pressure p_MC and from the pV characteristics curve of the evacuated brake system V_MC=V_MC^NoAir(p_MC).

Consequently, formula (9) is only still a function of hydraulic pressure p_MC, and for each measured hydraulic pressure p_MCr^Appl. it gives a pertaining value for the pressure difference Δp that is to be expected. Consequently, measured pressure difference Δp must be compared only to the pressure difference ascertained from characteristics line (9). When these two values differ from each other more than a predefined threshold value, a critical state is detected and a corresponding warning signal is emitted.

Variant 2: Determination of the Rigidity when the Brake Pedal is Operated

According to a second example embodiment, volume V_MC displaced in response to the operation of the foot brake pedal by the main brake cylinder is ascertained, and is compared to the pV characteristics curve of the system. For the volume of vacuum chamber 1 (subscript FC) in the operated state (superscript Appl.), the following applies:

$\begin{array}{cc}{V}_{\mathrm{FC}}^{\mathrm{Appl}.}=V_{\mathrm{FC}}^{\mathrm{Rel}.}·{\left(\frac{p_{\mathrm{FC}}^{\mathrm{Rel}.}}{p_{\mathrm{FC}}^{\mathrm{Appl}.}}\right)}^{\frac{1}{\kappa }}& \left(10\right)\end{array}$

where the assumption was made again that the vacuum supply was interrupted. The differential mass may be calculated and taken into account analogously to the preceding case.

In this context, p_FC^Rel. and p_FC^Appl. are the pressures in vacuum chamber 1 in the non-operated and the operated state respectively, and k=1 for an isothermal change in state. Then the following applies for the path S_B^Appl. covered by diaphragm 7:

$\begin{array}{cc}{S}_B^{\mathrm{Appl}.}=\frac{V_{\mathrm{FC}}^{\mathrm{Rel}.}-V_{\mathrm{FC}}^{\mathrm{Appl}.}}{A_B}=\frac{V_{\mathrm{FC}}^{\mathrm{Rel}.}}{A_B}·\left[1-{\left(\frac{p_{\mathrm{FC}}^{\mathrm{Rel}.}}{p_{\mathrm{FC}}^{\mathrm{Appl}.}}\right)}^{\frac{1}{\kappa }}\right]& \left(11\right)\end{array}$

where A_B is the effective area of diaphragm 7. The volume V_MC displaced by the main cylinder may now be calculated from cross sectional area A_MC of the main brake cylinder and path s_B^Appl., since the path covered in main brake cylinder 8 is thus identical to the path of diaphragm 7, minus some free play s₀, until a pressure build-up takes place in the main brake cylinder (MC). The following applies:

V _MC =A _MC·(S_B^Appl.−S₀)   (12)

From a comparison of V_MC to the pV characteristics curve of the evacuated brake system V_MC=V_MC^NoAir(P_MC), one is able to establish whether there is air inclusion in the brake system.

Claims

1-12. (canceled)

13. A method for detecting changes in the rigidity of a hydraulic brake system having a vacuum brake booster, comprising: measuring, in each of operated state and non-operated state of the brake, a pressure prevailing in the vacuum chamber of the vacuum brake booster, wherein the vacuum chamber includes a diaphragm;ascertaining, as a function of the measured vacuum chamber pressures in each of operated state and non-operated state of the brake, a characteristic parameter characterizing the brake performance; andcomparing the characteristic parameter to a reference value.

14. The method as recited in claim 13, wherein a pressure difference between the measured vacuum chamber pressures in the operated state and the non-operated state of the brake is calculated as the characteristic parameter and is compared to the reference value.

15. The method as recited in claim 14, wherein the reference value is ascertained as a function of a hydraulic brake pressure.

16. The method as recited in claim 15, wherein the reference value is ascertained from the following relationship:

17. The method as recited in claim 16, wherein the path covered by the diaphragm is determined with the aid of a stored characteristic curve.

18. The method as recited in claim 13, wherein the vacuum chamber pressure is first measured in the operated state of the brake and subsequently measured in the non-operated state of the brake.

19. The method as recited in claim 13, wherein one of the path covered by the diaphragm or a quantity proportional to the path covered by the diaphragm is determined as a function of the measured vacuum chamber pressures.

20. The method as recited in claim 19, wherein the path covered by the diaphragm is calculated from the following relationship:

21. The method as recited in claim 20, wherein a volume displaced from the main brake cylinder is determined based on the path covered by the diaphragm.

22. The method as recited in claim 21, wherein the volume displaced from the main brake cylinder is calculated from the following relationship: VMC=AMC·(SBAppl.−S0)wherein VMC is the volume displaced from the main brake cylinder, AMC is the cross-sectional area of the main brake cylinder, and S0 is a predetermined tolerance value.

23. The method as recited in claim 22, wherein the calculated volume displaced from the main brake cylinder is compared to a corresponding volume displaced from the main brake cylinder as ascertained from a pressure-volume characteristics curve.

24. A control unit for detecting changes in the rigidity of a hydraulic brake system having a vacuum brake booster, comprising: a measuring arrangement configured to measure, in each of operated state and non-operated state of the brake, a pressure prevailing in the vacuum chamber of the vacuum brake booster, wherein the vacuum chamber includes a diaphragm;an ascertaining arrangement configured to ascertain, as a function of the measured vacuum chamber pressures in each of operated state and non-operated state of the brake, a characteristic parameter characterizing the brake performance; andcomparing unit configured to compare the characteristic parameter to a reference value.