CN101451548B - Hydraulic transmission system implementing rapid starting/stopping and stable steering for large inertia load - Google Patents

Abstract

The present invention discloses a smooth and steady inverting hydraulic gear system that can realize big mass load quick startup and brake and dispel pitch play, which includes a oil tank, a variable capacity pump, a filter, a sequence valve, a one way valve, a three-position four-way electrohydraulic reversal valve, electrohydraulic proportionality over-flow valve, a hydraulic slave motor, a decelerator and pairs of wheel gear big and small. A hydraulic system in the invention is composed by two pars of a accelerate loop and a decelerate loop, wherein the accelerate loop and the decelerate loop supply oil in inverse direction on accelerate startup and decelerate brake stages, and adjust pressure value on each loop through four electrohydraulic proportionality over-flow valves to get enough pressure to drive the motor on the accelerate loop, and pressure on decelerate brake loop only need to be adjusted to make small gear wheel driven by motor on its loop stay close to the big gear wheel. From that gear influence from pitch play to transmission when gears engage can be dispelled and smooth and steady inverting can be done through the invention.

Description

A hydraulic transmission system that realizes fast start-stop and smooth reversing of large inertial loads

Technical field:

The invention belongs to the technical field of hydraulic pressure, and relates to a clamp rotating hydraulic system of a heavy-duty forging manipulator.

Background technique:

The problem of fast start-stop and smooth reversing during the acceleration and deceleration process of large inertial loads has a long history, especially in the field of metallurgical machinery. Due to some harsh work requirements of metallurgical machinery, it is required that the system with large inertial loads can quickly complete acceleration start-up and deceleration brake. Sometimes a working cycle itself is very short, such as the heavy-duty forging manipulator of the supporting equipment of a large press, due to the requirements of the forging process during the forging process, the manipulator requires dozens of times of acceleration, start-up, deceleration and braking every minute, and every A working cycle needs to turn through a specified angle. For this kind of large inertia load, it is required to complete dozens of times per minute. This kind of work puts forward high requirements for the rotary drive hydraulic system. The system must be able to complete quick start and smooth reversing. function. The torque output from the hydraulic motor is transmitted to the pinion through the reducer, and then drives the large gear (large inertial load) to rotate. In the gear transmission system, due to gear machining errors, installation errors and wear of the tooth profile during gear meshing, there is a gear backlash. shock. Secondly, for systems that require frequent positive and negative rotation and fast start and stop, the fast response of the system requires that the response time of the components that play the role of reversing in the system must be short. In order to overcome the impact of backlash between the gears on the transmission stability of the system, smooth the start-up impact of the hydraulic system itself, and achieve the purpose of fast start-stop, a hydraulic transmission system that realizes fast start-stop and smooth reversing of large inertial loads is designed.

Invention content:

In order to overcome the requirements of fast start, deceleration braking and smooth reversing of loads with large inertia, the present invention provides a hydraulic transmission system composed of two parts: acceleration circuit and deceleration braking. Adjust to complete the purpose of commutation.

The technical solution adopted by the present invention to solve the technical problem includes: oil tank, large gear, two variable displacement pumps, two filters, two overflow valves, two electro-hydraulic reversing valves, two motors, and two reducers , two pinions, four electro-hydraulic proportional relief valves, six one-way valves. Since the functions of the acceleration circuit and the deceleration brake circuit in the system can be interchanged, it will be described with reference to Figure 1 that the hydraulic motor in the system drives the large gear to rotate clockwise. The oil inlet A1 of the filter 2 in the acceleration circuit is connected to the fuel tank, the oil outlet B1 of the filter 2 is connected to the oil inlet A2 of the variable pump 3, and the oil outlet B2 of the variable pump 3 is connected to the oil inlet of the relief valve 4 respectively. Port P1 and the oil inlet A3 of the one-way valve 5 are connected, the oil outlet T1 of the overflow valve 4 is connected to the fuel tank, the oil outlet B3 of the one-way valve 5 is connected to the oil inlet P2 of the hydraulic reversing valve 6, and the electro-hydraulic The oil outlet A4 of the directional valve 6 communicates with the oil outlet B5 of the one-way valve 7, the oil inlet P3 of the electro-hydraulic proportional relief valve 9, and the oil inlet A7 of the hydraulic motor 11 respectively, and the oil inlet of the one-way valve 7 Port A5 communicates with the oil tank, the oil outlet T3 of the electro-hydraulic proportional relief valve 9 is connected to the oil tank, and the oil outlet B7 of the hydraulic motor 11 is connected with the oil inlet P4 of the electro-hydraulic proportional relief valve 10 and the outlet of the check valve 8 respectively. The oil port B6 and the oil outlet B4 of the electro-hydraulic reversing valve 6 are connected, the oil outlet T4 of the electro-hydraulic proportional overflow valve 10 is connected to the oil tank, the oil inlet A6 of the check valve 8 is connected to the oil tank, and the electro-hydraulic reversing valve 6 The oil return port T2 of the deceleration brake circuit is connected to the oil tank; the oil inlet A8 of the filter 15 in the deceleration brake circuit is connected to the oil tank, the oil outlet B8 of the filter 15 is connected to the oil inlet A9 of the variable pump 16, and the oil outlet of the variable pump 16 B9 communicates with the oil inlet P5 of the overflow valve 17 and the oil inlet A10 of the one-way valve 18 respectively, the oil outlet T5 of the overflow valve 17 leads to the fuel tank, and the oil outlet B10 of the one-way valve 20 is connected to the electric hydraulic reversing valve The oil inlet P6 of 19, the oil outlet A11 of the electro-hydraulic reversing valve 19 are respectively connected with the oil outlet B12 of the check valve 20, the oil inlet P7 of the electro-hydraulic proportional relief valve 22, and the oil inlet of the hydraulic motor 24. A14 communicates, the oil inlet A12 of the check valve 20 communicates with the oil tank, the oil outlet T7 of the electro-hydraulic proportional overflow valve 22 communicates with the oil tank, and the oil outlet B14 of the hydraulic motor 24 is connected with the inlet of the electro-hydraulic proportional overflow valve 23 respectively. The oil port P8, the oil outlet B13 of the check valve 21, and the oil outlet B11 of the electro-hydraulic reversing valve 19 are connected, the oil outlet T8 of the electro-hydraulic proportional overflow valve 23 is connected to the oil tank, and the oil inlet of the check valve 21 A13 leads to the fuel tank, and the oil return port T6 of the electro-hydraulic reversing valve 19 leads to the fuel tank.

Compared with technical background, the present invention has beneficial effects as follows:

1) The pressure feedback on the oil side of the inlet and outlet of the hydraulic motor and the pressure control technology of the electro-hydraulic proportional relief valve are adopted to realize the real-time adjustment of various loads and pressures, and the system has a wide working range

2) The combination of acceleration start and deceleration brake circuits is adopted. During the acceleration and deceleration stages, each circuit is supplied with oil at the same time, so that the motors on the acceleration and deceleration circuits drive their respective pinion gears to mesh with the large gear in reverse, eliminating The impact of the system during deceleration and braking due to the gap between the gears is eliminated, and the purpose of smooth commutation is achieved.

3) Since the reversing of the system is by adjusting the electro-hydraulic proportional overflow valve on the acceleration start and deceleration brake circuit, the pressure value of the electro-hydraulic proportional overflow valve can be adjusted in real time, so as to achieve the function of precise positioning. The reversing of this system is accomplished by adjusting the pressure value of the electro-hydraulic proportional relief valve on the acceleration start and deceleration brake circuits. Under the same system pressure, the response time of the electro-hydraulic proportional relief valve is faster The response time of the directional valve should be fast, so as to achieve the effect of fast braking.

4) When the system is about to brake, increase the electro-hydraulic proportional overflow valve on the acceleration start and deceleration brake circuits at the same time, so that the system can form a high residual pressure after the motor brakes, and the high residual pressure On the one hand, it shortens the time required for high pressure formation in the start circuit when the system starts, and achieves the purpose of fast start; on the other hand, the high residual pressure on the acceleration start and deceleration brake circuits reduces the pressure of the acceleration start and deceleration brake circuits. Poor, smoothes out the hydraulic shock at start-up.

This system is not only suitable for systems driven by two hydraulic motors, but also for systems driven by multiple hydraulic motors.

Description of drawings

The present invention will be further described below in conjunction with the accompanying drawings and specific implementation methods.

Accompanying drawing 1 is the structural schematic diagram of the present invention. Fig. 2a is the pressure setting curve of the electro-hydraulic proportional overflow valve 9 when the system rotates clockwise. Fig. 2b is a pressure setting curve of the electro-hydraulic proportional relief valve 23 when the system rotates clockwise. Fig. 2c is a pressure setting curve of the electro-hydraulic proportional overflow valve 10, 22 when the system rotates clockwise. Fig. 3a is the pressure setting curve of the electro-hydraulic proportional overflow valve 9 when the system rotates counterclockwise. Fig. 3b is a pressure setting curve of the electro-hydraulic proportional overflow valve 23 when the system rotates counterclockwise. Fig. 3c is a pressure setting curve of the electro-hydraulic proportional overflow valve 10, 22 when the system rotates counterclockwise. In Fig. 2a, Fig. 2b, Fig. 2c, Fig. 3a, Fig. 3b, Fig. 3c, the ordinate represents pressure, and the abscissa represents time.

Detailed ways:

As shown in the figure, the present invention includes an oil tank 1, a large gear 14, two variable displacement pumps 3, 16, filters 2, 15, overflow valves 4, 17, electro-hydraulic reversing valves 6, 19, motor 11, 24. Reducers 12, 25, pinions 13, 26, four electro-hydraulic proportional overflow valves 9, 10, 22, 23, and six one-way valves 5, 7, 8, 18, 20, 21. Since the functions of the acceleration circuit and the deceleration brake circuit in the system can be interchanged, it will be described with reference to Figure 1 that the hydraulic motor in the system drives the large gear to rotate clockwise. The oil inlet port of the filter 2 in the acceleration circuit is connected to the oil tank, the oil outlet B1 of the first filter 2 is connected to the oil inlet A2 of the variable pump 3, and the oil outlet B2 of the first variable pump 3 is respectively connected to the oil port A2 of the first variable pump 3. The oil inlet P1 of a relief valve 4 and the oil inlet A3 of the first one-way valve 5 are connected, the oil outlet T1 of the first relief valve 4 is connected to the fuel tank, and the outlet of the first one-way valve 5 The oil port B3 is connected to the oil inlet P2 of the first electro-hydraulic reversing valve 6, and the oil outlet A4 of the first electro-hydraulic reversing valve 6 is respectively connected to the oil outlet B5 of the second one-way valve 7, the first The oil inlet P3 of the first electro-hydraulic proportional overflow valve 9 is connected with the oil inlet A7 of the first hydraulic motor 11, the oil inlet A5 of the second check valve 7 is connected with the oil tank, and the first electro-hydraulic proportional overflow The oil outlet T3 of the flow valve 9 is connected to the oil tank, and the oil outlet B7 of the first hydraulic motor 11 is connected with the oil inlet P4 of the second electro-hydraulic proportional relief valve 10 and the oil outlet of the third check valve 8 respectively. Port B6 and the oil outlet B4 of the first electro-hydraulic reversing valve 6 are connected, the oil outlet T4 of the second electro-hydraulic proportional overflow valve 10 is connected to the fuel tank, and the oil inlet A6 of the third check valve 8 is connected to Oil tank, the oil return port T2 of the first electro-hydraulic reversing valve 6 leads to the oil tank; the oil inlet A8 of the second filter 15 leads to the oil tank, and the oil outlet B8 of the second filter 15 leads to the second variable pump The oil inlet A9 of 16, the oil outlet B9 of the second variable pump 16 communicate with the oil inlet P5 of the second relief valve 17 and the oil inlet A10 of the fourth one-way valve 18 respectively, the second The oil outlet T5 of the overflow valve 17 is connected to the fuel tank, the oil outlet B10 of the fourth check valve 18 is connected to the oil inlet P6 of the second electro-hydraulic reversing valve 19, and the oil outlet B10 of the second electro-hydraulic reversing valve 19 is connected to the fuel tank. The oil outlet A11 communicates with the oil outlet B12 of the fifth one-way valve 20, the oil inlet P7 of the third electro-hydraulic proportional relief valve 22, and the oil inlet A14 of the second hydraulic motor 24 respectively. The oil inlet A12 of the first check valve 20 communicates with the oil tank, the oil outlet T7 of the third electro-hydraulic proportional overflow valve 22 communicates with the oil tank, and the oil outlet B14 of the second hydraulic motor 24 communicates with the fourth electro-hydraulic valve respectively. The oil inlet P8 of the proportional relief valve 23, the oil outlet B13 of the sixth one-way valve 21, and the oil outlet B11 of the second electro-hydraulic reversing valve 19 are connected, and the fourth electro-hydraulic proportional relief valve 23 The oil outlet T8 of the first check valve 21 is connected to the fuel tank, the oil inlet A13 of the sixth check valve 21 is connected to the fuel tank, and the oil return port T6 of the second electro-hydraulic reversing valve 19 is connected to the fuel tank. The control signal of the electro-hydraulic proportional overflow valve 9 is input through the set pressure signal (see Figure 2a), and the control signal of the electro-hydraulic proportional overflow valve 23 is input through another set pressure signal (see Figure 2b). The control signals of the overflow valves 10 and 22 are then input through another set pressure signal (see FIG. 2c). When the system rotates counterclockwise, the functions of the acceleration start circuit and the deceleration brake circuit are interchanged. At this time, the control signal of the electro-hydraulic proportional overflow valve 9 is input through the set pressure signal (see Figure 3a), and the electro-hydraulic proportional overflow The control signal of the valve 23 is input through another set pressure signal (see Fig. 3b), and the control signals of the electro-hydraulic proportional relief valves 10 and 22 are input through another set pressure signal (see Fig. 3c).

Working process of the present invention is as follows:

Referring to Figure 1, when the system drives the large gear to move clockwise, the system is in the acceleration phase, the first hydraulic circuit (the left circuit) is used as the acceleration start circuit, and the second hydraulic circuit (the right circuit) is used as the deceleration brake circuit . When the system starts to start, the electro-hydraulic reversing valve 6 in the first hydraulic circuit is connected to the left position, and the electro-hydraulic reversing valve 19 in the second hydraulic circuit is connected to the right position. The pressure value of the electro-hydraulic proportional relief valve 9 in the first hydraulic circuit is adjusted to the maximum pressure value required by the system to drive the large inertia load, and the pressure value of the electro-hydraulic proportional relief valve in the second hydraulic circuit is adjusted to Make the pinion 35 close to the big gear 18. The pressure oil on the acceleration start circuit passes through the oil outlet B1 of the filter 2 to the oil inlet A2 of the first variable pump 3, and the outlet of the first variable pump 3 The oil port B2 communicates with the oil inlet P1 of the first relief valve 4 and the oil inlet A3 of the first one-way valve 5 respectively, the oil outlet T1 of the first relief valve 4 leads to the oil tank, and the first The oil outlet B3 of the one-way valve 5 is connected to the oil inlet P2 of the first electro-hydraulic reversing valve 6, and the oil outlet A4 of the first electro-hydraulic reversing valve 6 is connected to the outlet of the second one-way valve 7 respectively. The oil port B5, the oil inlet P3 of the first electro-hydraulic proportional relief valve 9, and the oil inlet A7 of the first hydraulic motor 11 are connected, and the oil inlet A5 of the second check valve 7 is connected with the oil tank. The oil outlet T3 of an electro-hydraulic proportional relief valve 9 is connected to the fuel tank, and the oil outlet B7 of the first hydraulic motor 11 is respectively connected to the oil inlet P4 of the second electro-hydraulic proportional relief valve 10, the third single The oil outlet B6 of the directional valve 8 and the oil outlet B4 of the first electro-hydraulic reversing valve 6 are connected, the oil outlet T4 of the second electro-hydraulic proportional relief valve 10 is connected to the fuel tank, and the third one-way valve 8 The oil inlet A6 of the first electro-hydraulic reversing valve 6 is connected to the oil tank, the oil return port T2 of the first electro-hydraulic reversing valve 6 is connected to the oil tank; the oil inlet A8 of the second filter 15 is connected to the oil tank, and the oil outlet B8 of the second filter 15 Through the oil inlet A9 of the second variable pump 16, the oil outlet B9 of the second variable pump 16 is connected with the oil inlet P5 of the second relief valve 17 and the oil inlet of the fourth one-way valve 18 respectively. A10 is connected, the oil outlet T5 of the second relief valve 17 is connected to the fuel tank, the oil outlet B10 of the fourth check valve 18 is connected to the oil inlet P6 of the second electro-hydraulic reversing valve 19, and the second electro-hydraulic reversing valve 19 is connected to the oil inlet P6. The oil outlet A11 of the hydraulic reversing valve 19 is connected with the oil outlet B12 of the fifth check valve 20, the oil inlet P7 of the third electro-hydraulic proportional relief valve 22, and the oil inlet of the second hydraulic motor 24 respectively. The oil inlet A12 of the fifth one-way valve 20 is connected with the oil tank, the oil outlet T7 of the third electro-hydraulic proportional relief valve 22 is connected with the oil tank, and the oil outlet B14 of the second hydraulic motor 24 is respectively It communicates with the oil inlet P8 of the fourth electro-hydraulic proportional relief valve 23, the oil outlet B13 of the sixth one-way valve 21, and the oil outlet B11 of the second electro-hydraulic reversing valve 19. The oil outlet T8 of the hydraulic proportional overflow valve 23 leads to the oil tank, the oil inlet A13 of the sixth check valve 21 leads to the oil tank, and the oil return port T6 of the second electro-hydraulic reversing valve 19 leads to the oil tank. After reaching the moment when deceleration braking is required, the hydraulic system will complete the action of deceleration braking. At this time, the oil supply direction of the hydraulic circuit originally used as acceleration start deceleration braking is still the same, and the reversing valves 6 and 19 do not perform reversing. It’s just that the pressure value of the electro-hydraulic proportional relief valve 9 on the first hydraulic circuit used for acceleration and start-up needs to be reduced. As long as the electro-hydraulic proportional relief valve 9 can ensure that the motor can drive the small gear close to the large gear, And the pressure value side of the electro-hydraulic proportional overflow valve 23 on the deceleration braking circuit needs to rise, so that there can be a large enough pressure value in the deceleration braking system so that the load can reach braking within a specified time. At the moment when the motor is about to brake, the pressure values of the electro-hydraulic proportional overflow valve 9 of the acceleration start hydraulic circuit and the pressure value of the electro-hydraulic proportional overflow valve 23 on the deceleration brake circuit are all increased at the same time. The pressure difference on the upper hydraulic circuit causes the motor to rotate in reverse, and on the other hand, it can form a certain residual oil pressure in the two hydraulic circuits, thereby shortening the time required for the high pressure formation of the starting circuit when the system is started, and achieving a quick start In addition, the high residual pressure on the acceleration start and deceleration brake circuits reduces the pressure difference between the acceleration start and deceleration brake circuits, smoothing the hydraulic shock during startup. When the system is about to rotate counterclockwise, only It is necessary to exchange the functions of the acceleration start and deceleration brake circuits in the original system.

Claims (1)

1. realize large inertia load rapid starting/stopping and the Hydraulic Power Transmission System that steadily commutates for one kind, it is characterized in that system forms by quickening startup loop and retarding braking loop two-part; This Hydraulic Power Transmission System comprises: a fuel tank (1), gearwheel (14), two variable displacement pumps (3,16), filter (2,15), relief valve (4,17), electro-hydraulic reversing valve (6,19), motor (11,24), retarder (12,25), small gear (13,26), four electricity liquid ratio relief valves (9,10,22,23), six one-way valves (5,7,8,18,20,21); The oiler A1 of first filter (2) leads to fuel tank, the oiler A2 of logical first variable displacement pump (3) of the oil outlet B1 of first filter (2), the oil outlet B2 of first variable displacement pump (3) respectively with the oiler P1 of first relief valve (4), the oiler A3 of first one-way valve (5) communicates, the oil outlet T1 of first relief valve (4) leads to fuel tank, the oiler P2 of logical first electro-hydraulic reversing valve (6) of the oil outlet B3 of first one-way valve (5), the oil outlet A4 of first electro-hydraulic reversing valve (6) respectively with the oil outlet B5 of second one-way valve (7), the oiler P3 of first electricity liquid ratio relief valve (9), the oiler A7 of first oil hydraulic motor (11) communicates, the oiler A5 of second one-way valve (7) communicates with fuel tank, the oil outlet T3 of first electricity liquid ratio relief valve (9) leads to fuel tank, the oil outlet B7 of first oil hydraulic motor (11) respectively with the oiler P4 of second electricity liquid ratio relief valve (10), the oil outlet B6 of the 3rd one-way valve (8), the oil outlet B4 of first electro-hydraulic reversing valve (6) communicates, the oil outlet T4 of second electricity liquid ratio relief valve (10) leads to fuel tank, the oiler A6 of the 3rd one-way valve (8) leads to fuel tank, the oil return inlet T 2 logical fuel tanks of first electro-hydraulic reversing valve (6); The oiler A8 of second filter (15) leads to fuel tank, the oiler A9 of logical second variable displacement pump (16) of the oil outlet B8 of second filter (15), the oil outlet B9 of second variable displacement pump (16) respectively with the oiler P5 of second relief valve (17), the oiler A10 of the 4th one-way valve (18) communicates, the oil outlet T5 of second relief valve (17) leads to fuel tank, the oiler P6 of logical second electro-hydraulic reversing valve (19) of the oil outlet B10 of the 4th one-way valve (18), the oil outlet A11 of second electro-hydraulic reversing valve (19) respectively with the oil outlet B12 of the 5th one-way valve (20), the oiler P7 of the 3rd electricity liquid ratio relief valve (22), the oiler A14 of second oil hydraulic motor (24) communicates, the oiler A12 of the 5th one-way valve (20) communicates with fuel tank, the oil outlet T7 of the 3rd electricity liquid ratio relief valve (22) leads to fuel tank, the oil outlet B14 of second oil hydraulic motor (24) respectively with the oiler P8 of the 4th electricity liquid ratio relief valve (23), the oil outlet B13 of the 6th one-way valve (21), the oil outlet B11 of second electro-hydraulic reversing valve (19) communicates, the oil outlet T8 of the 4th electricity liquid ratio relief valve (23) leads to fuel tank, the oiler A13 of the 6th one-way valve (21) leads to fuel tank, the oil return inlet T 6 logical fuel tanks of second electro-hydraulic reversing valve (19), first electricity liquid ratio relief valve (9) control signal is by the first pressure signal input of setting, the 4th electricity liquid ratio relief valve (23) control signal is by the input of the second setting pressure signal, the second and the 3rd electricity liquid ratio relief valve (10,22) control signal is again by the input of the 3rd setting pressure signal.

Images