Disc brake system

Abstract

The utility model relates to the technical field of hydraulic brake systems, and discloses a disc brake system which comprises a brake head, an energy accumulator, a one-way throttle valve, a pressure transmitter, a one-way valve, a motor, a gear pump, an oil suction filter, a first overflow valve, a pressure gauge, an electromagnetic directional valve, a second overflow valve, a first electromagnet and a second electromagnet. The one-way throttle valve is additionally arranged, the pressure release speed of the energy accumulator is controlled, and the braking speed of the brake head of the brake is adjustable. When all the one-way throttle valves are closed, oil in the brake head of the brake can rapidly flow back for unloading, and the brake head of the brake rapidly brakes; when slow braking is needed, the one-way throttle valve can be opened, oil in the energy accumulator supplements oil in the brake head of the brake and slows down backflow of the oil in the brake head, and therefore the requirement for slow braking is met, and the adjusting function of different braking time can be achieved by adjusting the opening size of the one-way throttle valve. Therefore, the actual operation requirements can be quickly and accurately met.

Description

Technical Field

[0001] This utility model belongs to the technical field of hydraulic braking systems, specifically, it relates to a disc braking system. Background Technology

[0002] In modern industrial production, hydraulic braking systems are widely used in various mechanical equipment, such as lifting equipment and mining machinery. Their performance directly affects the safety and reliability of equipment operation.

[0003] Traditional hydraulic braking systems lack flexibility in braking state control. In many working conditions, it is necessary to switch flexibly between full braking and partial braking states. However, traditional systems often only have a single braking mode, or the switching process is complex and slow to respond, failing to meet actual operational needs quickly and accurately.

[0004] In view of this, this utility model is proposed. Utility Model Content

[0005] To address the shortcomings of traditional hydraulic braking systems in terms of braking state control, which suffer from poor flexibility, this invention addresses the technical problem of traditional systems lacking flexibility in braking state control. Many operating conditions require flexible switching between full braking and partial braking states; however, traditional systems often only offer a single braking mode, or the switching process is complex and slow to respond, failing to quickly and accurately meet the demands of actual operations. The basic concept of this invention is as follows:

[0006] A disc brake system includes a brake head, an accumulator, a one-way throttle valve, a pressure transmitter, a one-way valve, a motor, a gear pump, an oil suction filter, a first relief valve, a pressure gauge, a solenoid directional valve, a second relief valve, a first electromagnet, and a second electromagnet. The output shaft of the motor is drivenly connected to the input shaft of the gear pump. The oil inlet of the gear pump is connected to the oil suction filter through a pipeline. The oil suction filter is placed in an oil tank.

[0007] In a preferred embodiment of this utility model, the oil outlet of the gear pump is connected to a one-way valve via a pipeline, and then to a pressure transmitter, a brake head, a one-way throttle valve and an accumulator. The P port of the solenoid directional valve and the T port of the solenoid directional valve are connected to the oil tank via pipelines. The first relief valve and the second relief valve are respectively connected in parallel to the pipeline before the solenoid directional valve via pipelines. The pressure gauge is connected to the branch where the first relief valve is located. The first electromagnet and the second electromagnet are respectively connected to the corresponding control terminals of the solenoid directional valve.

[0008] In a preferred embodiment of this utility model, when neither the first electromagnet nor the second electromagnet is energized, the oil flows back to the oil tank through the P port to the T port of the electromagnetic reversing valve.

[0009] In a preferred embodiment of this utility model, when the first electromagnet is energized, the oil flows into port B through port P of the electromagnetic reversing valve. Since port B is blocked, the oil enters the accumulator for pressurization through the one-way throttle valve. When the system pressure rises, the brake head begins to open. When the pressure rises to the set rated pressure, the brake head opens to the maximum, and the first overflow valve limits the system pressure from rising further.

[0010] In a preferred embodiment of this utility model, the motor stops working, the first electromagnet remains energized, and the system is maintained under pressure by an accumulator, so that the brake head is in the open state.

[0011] In a preferred embodiment of this utility model, the motor is always running, and when the second electromagnet is energized, the oil flows from port P of the electromagnetic reversing valve into port A. At this time, the highest pressure of the system is determined by the second overflow valve, and the brake head is in a semi-braking state.

[0012] In a preferred embodiment of this utility model, when neither the first electromagnet nor the second electromagnet is energized, the oil in the accumulator is throttled by the one-way throttle valve to regulate the unloading speed, thereby regulating the closing speed of the brake head.

[0013] In a preferred embodiment of this utility model, the one-way throttle valve adjusts the braking time of the brake head by controlling the size of the opening.

[0014] Compared with the prior art, the present invention has the following advantages:

[0015] This invention achieves adjustable braking speed of the brake head by adding a one-way throttle valve to the accumulator oil circuit to control the release rate of the accumulator pressure. Specifically, when the one-way throttle valve is fully closed, the oil in the brake head quickly flows back to unload the load, resulting in rapid braking. When slower braking is required, the one-way throttle valve can be opened slightly, allowing the oil in the accumulator to replenish the oil in the brake head and slowing down the backflow of oil, thus achieving slower braking. Adjusting the opening size of the one-way throttle valve allows for different braking times, thereby quickly and accurately meeting actual operational needs.

[0016] The specific embodiments of this utility model will be described in further detail below with reference to the accompanying drawings. Attached Figure Description

[0017] In the attached diagram:

[0018] Figure 1 This is a schematic diagram of the overall structure of this utility model.

[0019] In the diagram: 1. Brake head; 2. Accumulator; 3. One-way throttle valve; 4. Pressure transmitter; 5. One-way valve; 6. Electric motor; 7. Gear pump; 8. Suction filter; 9. First relief valve; 10. Pressure gauge; 11. Solenoid directional valve; 12. Second relief valve; 13. First electromagnet; 14. Second electromagnet. Detailed Implementation

[0020] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions in the embodiments will be clearly and completely described below with reference to the accompanying drawings. The following embodiments are used to illustrate this utility model.

[0021] like Figure 1 As shown, a disc brake system includes a brake head 1, an accumulator 2, a one-way throttle valve 3, a pressure transmitter 4, a one-way valve 5, a motor 6, a gear pump 7, an oil suction filter 8, a first relief valve 9, a pressure gauge 10, a solenoid directional valve 11, a second relief valve 12, a first electromagnet 13, and a second electromagnet 14. The output shaft of the motor 6 is connected to the input shaft of the gear pump 7. The oil inlet of the gear pump 7 is connected to the oil suction filter 8 through a pipeline. The oil suction filter 8 is placed in an oil tank.

[0022] Furthermore, when neither the first electromagnet 13 nor the second electromagnet 14 is energized, the oil flows back to the oil tank through the P port to the T port of the electromagnetic reversing valve 11.

[0023] Furthermore, when the first electromagnet 13 is energized, the oil flows into port B through port AP of the electromagnetic reversing valve 11. Since port B is blocked, the oil enters the accumulator 2 for pressurization through the one-way throttle valve 3. When the system pressure rises, the brake head 1 begins to open. When the pressure rises to the set rated pressure, the brake head 1 opens to the maximum, and the first relief valve 9 limits the system pressure from rising further.

[0024] Furthermore, when neither the first electromagnet 13 nor the second electromagnet 14 is energized, the oil in the accumulator 2 adjusts the unloading speed through the throttling action of the one-way throttle valve 3, thereby adjusting the closing speed of the brake head 1.

[0025] The oil outlet of gear pump 7 is connected to check valve 5 via pipeline, and then to pressure transmitter 4, brake head 1, one-way throttle valve 3 and accumulator 2. The P port of solenoid directional valve 11 and the T port of solenoid directional valve 11 are connected to oil tank via pipeline. The first relief valve 9 and the second relief valve 12 are connected in parallel to the pipeline before solenoid directional valve 11 via pipeline. Pressure gauge 10 is connected to the branch where the first relief valve 9 is located. The first electromagnet 13 and the second electromagnet 14 are connected to the corresponding control terminals of solenoid directional valve 11.

[0026] Furthermore, the motor 6 stops working, the first electromagnet 13 remains energized, and the system is maintained under pressure by the accumulator 2, keeping the brake head 1 in the open state.

[0027] Furthermore, the motor 6 is always running, and when the second electromagnet 14 is energized, the oil flows from port P of the solenoid directional valve 11 into port A. At this time, the highest system pressure is determined by the second relief valve 12, and the brake head 1 is in a semi-braking state. The one-way throttle valve 3 adjusts the braking time of the brake head 1 by controlling the size of the opening.

[0028] The implementation principle of a disc brake system in this embodiment is as follows: When the hydraulic system starts, the motor 6 drives the gear pump 7 to draw oil from the oil tank through the suction filter 8. When neither the first electromagnet 13 nor the second electromagnet 14 is energized, the oil flows back to the oil tank through port P to port T. When the first electromagnet 13 is energized, the oil flows into port B through port AP. Since port B is blocked, the oil enters the accumulator 2 through the one-way throttle valve 3 to pressurize. When the system pressure rises, the brake head 1 begins to open. When the pressure rises to the set rated pressure, the brake head 1 opens to its maximum. Under the action of the first relief valve 9, the system pressure no longer rises. When the motor 6 stops working, the first electromagnet 13 remains energized, and the entire system is pressure-maintained by the accumulator 2, keeping the brake head 1 in the open state. When the motor 6 continues to work, and the second electromagnet 14 is simultaneously energized, oil flows from port P into port A. The set pressure of the second relief valve 12 is lower than the set pressure of the first relief valve 9, so the maximum system pressure is determined by the second relief valve 12. This pressure prevents the brake head 1 from fully opening, so the current state is a semi-braking state. When neither the first electromagnet 13 nor the second electromagnet 14 is energized, the oil in the accumulator 2 can be discharged at an adjustable rate through the throttling action of the one-way throttle valve 3. This allows for adjustable pressure drop rates in the system, making the closing speed of the brake head 1 adjustable, thus achieving adjustable braking speed and enabling rapid and precise fulfillment of actual operational needs.

Claims

1. A disc braking system, characterized in that, The system includes a brake head (1), an accumulator (2), a one-way throttle valve (3), a pressure transmitter (4), a one-way valve (5), a motor (6), a gear pump (7), an oil suction filter (8), a first relief valve (9), a pressure gauge (10), a solenoid directional valve (11), a second relief valve (12), a first electromagnet (13), and a second electromagnet (14). The output shaft of the motor (6) is connected to the input shaft of the gear pump (7). The oil inlet of the gear pump (7) is connected to the oil suction filter (8) through a pipeline. The oil suction filter (8) is placed in the oil tank.

2. The disc brake system according to claim 1, characterized in that, The oil outlet of the gear pump (7) is connected to the check valve (5) via a pipeline and then to the pressure transmitter (4), brake head (1), check valve (3) and accumulator (2), the P port of the solenoid directional valve (11) and the T port of the solenoid directional valve (11) are connected to the oil tank via a pipeline. The first overflow valve (9) and the second overflow valve (12) are respectively connected in parallel to the pipeline before the solenoid directional valve (11) via pipelines. The pressure gauge (10) is connected to the branch where the first overflow valve (9) is located. The first electromagnet (13) and the second electromagnet (14) are respectively connected to the corresponding control terminals of the solenoid directional valve (11).

3. A disc brake system according to claim 2, characterized in that, When neither the first electromagnet (13) nor the second electromagnet (14) is energized, the oil flows back to the oil tank through the P port to the T port of the electromagnetic reversing valve (11).

4. A disc brake system according to claim 2, characterized in that, When the first electromagnet (13) is energized, the oil flows into port B through port AP of the electromagnetic reversing valve (11). Since port B is blocked, the oil enters the accumulator (2) through the one-way throttle valve (3) to pressurize. When the system pressure rises, the brake head (1) begins to open. When the pressure rises to the set rated pressure, the brake head (1) opens to the maximum. The first overflow valve (9) restricts the system pressure from rising further.

5. A disc brake system according to claim 1, characterized in that, When the motor (6) stops working, the first electromagnet (13) remains energized, and the system is kept under pressure by the accumulator (2), so that the brake head (1) is in the open state.

6. A disc brake system according to claim 1, characterized in that, The motor (6) is always running, and when the second electromagnet (14) is energized, the oil flows from port P of the electromagnetic reversing valve (11) into port A. At this time, the highest pressure of the system is determined by the second overflow valve (12), and the brake head (1) is in a semi-braking state.

7. A disc brake system according to claim 2, characterized in that, When neither the first electromagnet (13) nor the second electromagnet (14) is energized, the oil in the accumulator (2) adjusts the unloading speed through the throttling effect of the one-way throttle valve (3), thereby adjusting the closing speed of the brake head (1).

8. A disc brake system according to claim 1, characterized in that, The one-way throttle valve (3) adjusts the braking time of the brake head (1) by controlling the size of the opening.

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