ELECTROHYDRAULIC BRAKE ACTUATOR

Abstract

An electrohydraulic brake actuator for a motor vehicle. The brake actuator has a piston-cylinder unit, whose piston is displaceable by an electric motor via a screw drive. Two pistons are provided, of which initially only a piston having a greater pressure-generating piston surface is displaced in order to build up pressure quickly and subsequently a second piston having a smaller pressure-generating piston surface is displaced in order to increase pressure.

Claims

1-8. (canceled)

9. An electrohydraulic brake actuator for generating a brake pressure for operating one or multiple hydraulic wheel brakes of a motor vehicle, comprising: a piston-cylinder unit configured to generate the brake pressure; a rotation-translation conversion drive configured to displace a piston in a cylinder of the piston-cylinder unit; and an electric motor configured to drive the rotation-translation conversion drive, the rotation-translation conversion drive configured to convert a rotational drive movement of the electric motor into a displacement which displaces the piston in the cylinder of the piston-cylinder unit; wherein a pressure-generating piston surface of the piston of the piston-cylinder unit is reduced during a displacement of the piston in the cylinder when generating pressure.

10. The electrohydraulic brake actuator as recited in claim 9, wherein the piston-cylinder unit has two pistons having pressure-generating piston surfaces of different sizes, and wherein the piston having a greater pressure-generating surface is displaced in the cylinder to build up pressure and the piston having a smaller pressure-generating surface is displaced in the cylinder to increase pressure.

11. The electrohydraulic brake actuator as recited in claim 9, wherein the piston-cylinder unit has a hollow piston, which is displaceable in the cylinder by way of the rotation-translation conversion drive, and in which a second piston is situated, against which the hollow piston strikes during displacement of the hollow cylinder so that the hollow cylinder displaces the second piston along with the hollow cylinder.

12. The electrohydraulic brake actuator as recited in claim 9, wherein the piston-cylinder unit has two pistons which are displaced jointly to build up pressure, and of which only one is displaced further in the cylinder to increase pressure.

13. The electrohydraulic brake actuator as recited in claim 12, wherein the piston-cylinder unit has a driver device for the two pistons.

14. The electrohydraulic brake actuator as recited in claim 12, wherein the rotation-translation conversion drive displaces a first of the two pistons in the cylinder, and a second of the two pistons is displaced along with the first piston in the cylinder until a brake pressure in the cylinder is so great that it overcomes a friction between the two pistons or until the second piston strikes against a piston stop.

15. The electrohydraulic brake actuator as recited in claim 9, wherein the piston-cylinder unit has a floating piston configured to generate pressure in a second brake circuit, which on one side has the brake pressure applied to it, which is generated by the piston, which is displaced by the rotation-translation conversion gear, and which on another side generates a brake pressure in the second brake circuit.

16. The electrohydraulic brake actuator as recited in claim 9, wherein the piston-cylinder unit has a brake fluid reservoir for compensating for brake pad wear.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0010] FIGS. 1 and 2 show circuit diagrams of example electrohydraulic brake actuators in accordance with the present invention.

DETAILED DESCRIPTION OF EXAMPLE EMBODIMENTS

[0011] The present invention is explained in greater detail below on the basis of specific embodiments illustrated in the figures.

[0012] The two figures show circuit diagrams of electrohydraulic brake actuators according to the present invention.

[0013] The example electrohydraulic brake actuator 1 according to the present invention shown in FIG. 1 has an electric motor 2, a spindle drive 3 and a piston-cylinder unit 4. In the two illustrated and described specific embodiments of the present invention, a mechanical reduction gear 5 is interposed between electric motor 2 and spindle drive 3, which is not essential for the present invention, however. Reduction gear 5 is in particular a pinion drive and for example a planetary gear. Electric motor 2 is able to drive spindle drive 3 in rotating fashion via reduction gear 5, if present.

[0014] In the two illustrated and described specific embodiments of the present invention, spindle drive 3 is a ball screw; other spindle drives 3 are possible. Generally, spindle drive 3 may be understood as a rotation-translation conversion gear 6, which converts a rotational movement of electric motor 2 or of reduction gear 5 into a displacement, which displaces a piston 7 in a cylinder 8 of piston-cylinder unit 4. Instead of spindle drive 3, a cam drive, a crankshaft drive, a cam gear or a rack-and-pinion drive are also possible for example (not shown). The list is provided by way of example and is not exhaustive.

[0015] In FIG. 1, piston-cylinder unit 4 has two pistons 7, 9, of which a first piston 7 is a hollow piston 10, which is displaceable in cylinder 8 via spindle drive 3. A second piston 9 is likewise a hollow piston, which is displaceable in first piston 7. First piston 7 and second piston 9 enclose a volume, whose size is variable by a displacement of the two pistons 7, 9 relative to each other. By a displacement of first piston 7 in the direction of second piston 9, the volume in first piston 7 designed as hollow piston 10 is reduced and brake fluid is displaced from first piston 7 through a center hole 11 in a piston bottom of second piston 9 into second piston 9 that is likewise designed as a hollow piston.

[0016] Second piston 9 is displaceable on a fixed piston 12 fixedly situated in cylinder 8 of piston-cylinder unit 4, whereby a volume is variable in the second piston 9 designed as a hollow piston. By a displacement of second piston 9 on fixed piston 12, the volume in second piston 9 is reduced and brake fluid is displaced from second piston 9 through a center hole 13 in fixed piston 12 into a hydraulic wheel brake 14, which is connected to cylinder 8 of piston-cylinder unit 4 via a brake hose 15. It is also possible for multiple wheel brakes 14 to be connected to piston-cylinder unit 4 (not shown).

[0017] A piston spring 16 supports second piston 9 in cylinder 8.

[0018] In order to operate wheel brake 14, electric motor 2 displaces first piston 7 via reduction gear 5 and spindle drive 3, which forms the rotation-translation conversion gear 6, in cylinder 8 of piston-cylinder unit 4 and on second piston 9, piston spring 16 initially retaining second piston 9 against being displaced along with first piston 7. The displacement of first piston 7 on second piston 9 reduces the volume in first piston 7 designed as hollow piston 10 so that brake fluid is displaced from first piston 7 through center hole 11 in the piston bottom of second piston 9 into second piston 9, which is likewise designed as a hollow piston. A brake pressure is thereby generated in cylinder 8 and, respectively, in the two pistons 7, 9 of piston-cylinder unit 4 and in the wheel brake 14 connected to piston-cylinder unit 4, and wheel brake 14 is operated.

[0019] As soon as the brake pressure overcomes a spring force of piston spring 16, which supports second piston 9 against being displaced along, or first piston 7 strikes against second piston 9, second piston 9 is displaced together with first piston 7 on fixed piston 12 so that the volume in second piston 9, likewise designed as a hollow piston, is reduced and brake fluid is displaced into wheel brake 14. When first piston 7 strikes against second piston 9, the two pistons 7, 9 are displaced jointly and no longer against each other so that the volume no longer changes in first piston 7 and no more brake fluid is displaced from first piston 7. The brake pressure is now only increased by the displacement of second piston 9 on fixed piston 12, whose pressure-generating piston surface 17 is smaller than a pressure-generating piston surface 18 of first piston 7. Pressure-generating piston surfaces 17, 18 of the two pistons 7, 9, designed as hollow pistons, of piston-cylinder unit 4 of the electrohydraulic brake actuator 1 according to the present invention are radial inner surfaces of the piston bottoms of the two pistons 7, 9. Due to the smaller pressure-generating piston surface 18 of second piston 9, a displacement force, which is required for displacing the two pistons 7, 9 in cylinder 8, is smaller when first piston 7 abuts on second piston 9 and when both pistons 7, 9 are displaced together and without displacement against each other and thus without a change in the volume in first piston 7. This reduces a displacement force for displacing the two pistons 7, 9 in order to increase pressure, after initially a brake pressure was generated by displacing the first piston 7 on second piston 9. This reduces a pressure-generating piston surface 17, 18 of the two pistons 7, 9 or of piston-cylinder unit 4 in the displacement of pistons 7, 9 in cylinder 8 of piston-cylinder unit 4 during a pressure buildup. Initially, first piston 7 displaces a large brake fluid volume, whereby wheel brake 14 is applied quickly and a brake pressure is generated quickly. Subsequently, the displacement of second piston 9 on fixed piston 12 increases the brake pressure using a smaller displacement force.

[0020] The piston bottom of first piston 7, which strikes against second piston 9 and displaces second piston 9 along with first piston 7, may also be understood generally as a driver device 19. Other driver devices are also possible, for example inwardly extending ribs, lugs, an annular step or pegs projecting from the piston bottom, by which the volume in first piston 7 is not reduced to zero when it strikes against second piston 9 (not shown).

[0021] Via an axially parallel bore in fixed piston 12, in which a non-return valve 20 is situated, a brake fluid reservoir 21 communicates with the volume in second piston 9. From brake fluid reservoir 21, brake fluid is able to flow through non-return valve 20 into piston 9, which results in a brake pad wear of wheel brake 14.

[0022] In the explanation of FIG. 2 below, elements agreeing with FIG. 1 are designated by the same reference numerals as in FIG. 1. The example electrohydraulic brake actuator 1 according to the present invention shown in FIG. 2 has an annular piston 22 as second piston 9, which encloses a first piston 7 designed as a solid piston. As in FIG. 1, first piston 7 is displaceable by an electric motor 2 via a mechanical reduction gear 5, which is not essential for the invention, and a spindle drive 3 as rotation-translation conversion drive 6 in a cylinder 8 of a piston-cylinder unit 4. Due to friction between the two pistons 7, 9, the second piston 9 designed as an annular piston is displaced along with first piston 7 so that a brake pressure is generated in cylinder 8 initially jointly by both pistons 7, 9. The pressure-generating piston surfaces 17, 18 of the two pistons 7, 9 displace a large quantity of brake fluid and effect a quick generation of a brake pressure in a hydraulic wheel brake 14 connected to cylinder 8 of piston-cylinder unit 4. Wheel brake 14 is thereby applied and operated quickly.

[0023] In FIG. 2, cylinder 8 has an annular step 23, at which its diameter is reduced from an outer diameter of second piston 9 to a diameter of first piston 7. When second piston 9 strikes against annular step 23, which may also be generally understood as piston stop 24, it is not displaced further, but rather only first piston 7 is displaced in a section of a smaller diameter of diameter-stepped cylinder 8. As a result, a pressure-generating piston surface for increasing the brake pressure in cylinder 8 is smaller, namely, only the pressure-generating piston surface 17 of first piston 7. A displacement force for displacing first piston 7 for increasing the brake pressure in cylinder 8 of piston-cylinder unit 4 of the electrohydraulic brake actuator 1 according to the present invention and in the connected wheel brake 14 is thereby smaller than it would be if both pistons 7, 9 were displaced together. In the specific embodiment of the present invention shown in FIG. 2, a pressure-generating piston surface 17, 18 is also reduced when pistons 7, 9 are displaced in cylinder 8 during a pressure buildup.

[0024] A driver device 19 for displacing second piston 9 along with first piston 7 is formed by a frictionally engaged connection between the two pistons 7, 9.

[0025] For compensating for brake pad wear, cylinder 8 communicates with a brake fluid reservoir 21 via a non-return valve 20 through which brake fluid is able to flow in the direction of cylinder 8.

[0026] In the section having the smaller diameter of cylinder 8 of piston-cylinder unit 4 of the brake actuator 1 according to the present invention from FIG. 2, a floating piston 25 is situated, which has brake pressure applied to it on a side facing the first and the second piston 7, 9, which is generated by the first and the second piston 7, 9. A side of floating piston 25 facing away from the first and the second piston 7, 9 generates a brake pressure in cylinder 8 on a side of floating piston 25 facing away from the first and the second piston 7, 9, where another hydraulic wheel brake 14 is connected. Piston-cylinder unit 4 of electrohydraulic brake actuator 1 from FIG. 2 thereby operates two hydraulic wheel brakes 14 in a manner hydraulically separated from each other, as is in conventional master brake cylinders operated by muscle power or auxiliary power. It is possible for more than one hydraulic wheel brake 14 to be connected on cylinder 8 respectively on both sides of floating piston 25 (not shown). Cylinder 8, on the side of floating piston 25 facing away from the first and the second piston 7, 9, and the wheel brake 14 connected there may also be understood as a second brake circuit II.

[0027] The brake fluid reservoir 21 shown in the figures is not essential for the present invention, it also being possible to design brake actuators 1 as closed systems without brake fluid reservoir 21.