Patent Application
20230286486
This application claims priority benefit to German Patent Application serial no. DE 10 2022 105 427.6 filed on Mar. 8, 2022, the disclosure of which is incorporated by reference herein.
The patent application refers to a device for direct force measurement.
State of the art systems are frequently based on an indirect measurement to determine the brake force. In other known systems, the measurement is based on mathematical calculations.
State of the art systems are commonly based on the measurement of the energy used to generate the required braking force. Wherein the required braking force may be generated by means of electrical energy or pneumatically or using hydraulic pressure.
Many state of the art systems often prove to be inaccurate or time-consuming.
Therefore, it is the objective of the invention to provide a device for measuring the force acting on the brake caliper.
The problem is solved by a converting means, which is arranged to convert a basic force into a first force, which is then measured.
According to the invention the brake system comprises one or more of the following components: At least one brake caliper, at least one brake pad and/or a brake shoe. At least one brake piston is also included in the brake system. The brake system also comprises at least one brake disc.
The components of the brake system are referred to in more detail below.
A brake system is referred to as a mechanical device that prevents movement by absorbing energy from a moving system.
The brake system is used to slow or stop a moving vehicle. Also, a wheel or an axle of the vehicle may be slowed or stopped.
The brake system preferably reduces or stops the movement by generating friction.
In the following the brake system is described in relation to a land-based vehicle. Also, the brake system is referred to as brake.
The invention understands the brake caliper to be an assembly that houses at least one of the brake pads and the brake pistons.
Generally, the caliper may be designed as a floating caliper. Alternatively, the caliper may be designed as fixed caliper. Opposite to the floating caliper, the fixed caliper does not move relative to the brake disc. Therefore, the fixed caliper is less tolerant of disc unevenness.
The floating caliper moves with respect to the brake disc. The floating caliper may move along a line parallel to an axis of rotation of the brake disc.
State of the art systems are frequently designed as indirect measurement systems. The indirect measurement systems usually measure the energy source that is used to create the required brake force.
By way of example, the required braking force may be generated by means of electrical energy or pneumatically or using hydraulic pressure.
The invention is described in more detail below with reference to a hydraulic brake system.
In the case of a hydraulic brake system, the energy that would be required to generate a certain braking force could be determined, for example, by determining the force that would be required to generate the required hydraulic pressure.
A direct measurement of the energy required to provide a specific braking force may be taken when one explicitly measures the characteristic of the object in question.
By way of example, the energy used to provide a certain braking force with the brake system, preferably using a brake disc, can be measured directly at the brake shoe and/or at the brake pad.
As an example, but in no way exclusively, a brake force (PB) in Watts (unit: W) can be determined at the brake shoe by multiplying the tangential braking force (FB) at the brake shoe of the brake system in Newton (unit: N) with the speed (v) between the brake shoes in metres per second (unit: meter/second).
The corresponding formula would be:
(PB)=(FB)*V
It goes without saying that the required braking energy may also be determined in another technical way.
The invention proves to be very advantageous because the load pins according to the invention provide useful information about the degree of effectiveness of the braking force provided to perform the braking operation.
The degree of effectiveness refers to the braking force provided between the vehicle and the road surface.
Contrary to the invention, state of the art solutions only measure the force between the caliper and the brake disc.
A force, preferably a brake force can be measured in a direct manner by determining the reactive force.
The reactive force is always present to obtain the equilibrium of forces.
The invention understands the reactive force to be a force that acts in the opposite direction to an active force.
In the example of a hydraulic disk brake system, the braking force is applied to the brake shoes of the hydraulic brake system to exert the required braking torque on the brake disc. Thus, in the hydraulic brake system, the reactive force is the force needed to generate the required hydraulic pressure for the required braking force.
For every force there is an oppositely directed reactive force of the same magnitude.
Depending on the mechanical setup of the individual system, the reactive force may be one of the following types:
The reactive force may be a torque. The reactive force may also be a shear force. Of course, there may also be an axial reactive force or any other force.
The invention understands the term torque to be a rotational equivalent of linear force. The torque may also be referred to as moment. The torque may further be referred to as moment of force or as a rotational force. Alternatively, the torque may be understood as a turning effect. According to the invention the torque represents the capability of a force to produce change in the rotational motion of a body.
As an example, the torque may be caused by a lever arm. Thus, a linear reactive force is converted to a torque moment. The torque moment is measured by means of the magnetoelastic force sensor referred to below.
The magnetoelastic force sensor may be a torque sensor.
According to the invention, shear forces represent unaligned forces pushing one part of a body in one specific direction. Whereas another part of the body is pushed in the opposite direction.
According to the invention a braking force may be transferred via pins. The braking force may be measured with a magnetoelastic force sensor, wherein the magnetoelastic force sensor may be designed as a shear force sensor.
Alternatively, the reactive force may be an axial force.
An axial force refers to a reverse tensile force or to a reverse tensile pressure on a certain cross section of a structure. The axial force is caused by a certain action.
When the reverse tensile force is located at the centre of gravity of the cross section, it is called axial force, wherein the magnetoelastic force sensor may be designed as an axial force sensor.
Any reactive force referred to above may by measured by means of a magnetoelastic force sensor that is discussed in more detail below.
The magnetoelastic force sensor is designed to measure at least one force. The force, measured by the magnetoelastic force sensor may be torque. However, it goes without saying that the magnetoelastic force sensor may also be designed to measure a force, other than torque.
According to the invention, the magnetoelastic force sensor comprises a ferromagnetic ring that is attached to a shaft, with the shaft being measured by the sensor.
Alternatively, the shaft may comprise a ferromagnetic material. Wherein a section of the shaft may be permanently magnetized. The magnetized section of the shaft may produce a circumferential magnetic field, eliminating the need for an external ring.
Thus, a magnetoelastic force sensor is based on the magnetoelastic effect. According to the invention, the magnetoelastic force sensor uses non-contact sensing to provide accurate torque measurements for rotating or stationary shafts.
According to the invention the magnetized section may also be arranged on geometrical object other than the shaft referred to above.
According to the invention, the ferromagnetic ring can also be arranged on another geometrical body, except on a ring.
Further examples and advantageous embodiments of the invention are described in more detail below with reference to the figures.
When the fluid pressure is further increased in the brake cylinder 2 the compressed hydraulic fluid pushes the brake piston 1 along a longitudinal axis 3 towards the brake disc 4.
A brake pad 5 is arranged at the front end 6 of the brake piston 1.
With an additional increase of the fluid pressure in the brake cylinder 2, the brake pad 5 is pressed against the brake disc 4 and thus the braking process is initiated (not shown).
The force 24 that pushes the brake piston 1 along the longitudinal axis 3 towards the brake disc 4 is generated within the brake cylinder 2.
A force 27 applying the brake pad 5 to the brake disc 4 extends along the longitudinal axis 3.
The force 24 that pushes the brake piston 1 along a longitudinal axis 3 towards the brake disc 4 coincides with the force 27 that presses the brake pad 5 against the brake disc 4. The reactive force, which represents a balance of forces with respect to the force 24 pushing the brake piston 1 along the longitudinal axis 3 and/or with respect to the force 27 pressing the brake pad 5 against the brake disc 4, is represented by the reference numeral 23.
The lever arm 7 rotates around an axis of rotation, generating a torque moment 25.
In the illustration of
The
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In the illustration in
The caliper 16 is positioned above the brake disc 4.
In the illustration of
| Number | Date | Country | Kind |
|---|---|---|---|
| 102022105427.6 | Mar 2022 | DE | national |
