CN109372810B

CN109372810B - Hydraulic system of large-flow squeezer

Info

Publication number: CN109372810B
Application number: CN201811352228.1A
Authority: CN
Inventors: 余亿坤
Original assignee: Guangzhou Blt Hydraulics & Seals Ltd
Current assignee: Guangzhou Blt Hydraulics & Seals Ltd
Priority date: 2018-11-14
Filing date: 2018-11-14
Publication date: 2020-02-14
Anticipated expiration: 2038-11-14
Also published as: CN109372810A

Abstract

The invention belongs to the technical field of large-flow squeezer, and particularly relates to a novel large-flow squeezer hydraulic system. The system comprises an oil tank device, a main pump device, a circulating filtering and cooling device, a pilot oil motor pump set, a main pump flow control loop, an oil cylinder 2# control loop, an oil cylinder 3# control loop, an oil cylinder 1# control loop and an oil return pressure relief device; the technical problems that the existing hydraulic system of the large-flow squeezer is easy to cause vibration and large in flow change and overflow easily occurs in the processes of starting, stopping and state conversion are solved. The energy consumption is less, and the shock attenuation effect is better, effectively prevents the production of large-traffic overflow phenomenon.

Description

Hydraulic system of large-flow squeezer

Technical Field

The invention belongs to the technical field of large-flow squeezer, and particularly relates to a novel large-flow squeezer hydraulic system.

Background

In the prior art, a high-flow hydraulic system is applied to large-scale equipment in various industries, and the control of flow and pressure is generally realized by combining a constant-pressure variable pump, a two-way plug-in type reversing valve, an overflow valve, a proportional valve and the like. The conventional large-flow hydraulic system is used in the working condition of a large-scale presser, and because the loop flow is large, the pressure is up to 30MPa after pressure maintaining, and the moving part quality is up to 10T, the whole system is easy to cause vibration and impact in the processes of starting, stopping and state conversion. During the deceleration and braking processes of the oil cylinder, the required flow change is large and frequent, the phenomenon of large-flow overflow is easy to occur during the process, and the system consumes energy at the moment.

Disclosure of Invention

The invention provides a novel high-flow squeezer hydraulic system, which solves the technical problems that the existing high-flow squeezer hydraulic system is easy to cause vibration and overflow due to large flow change in the processes of starting, stopping and state conversion.

According to the specific technical scheme, the hydraulic system of the high-flow squeezer comprises an oil tank device, a main pump device, a circulating filtering and cooling device, a pilot oil motor pump set, a main pump flow control loop, an oil cylinder 2# control loop, an oil cylinder 3# control loop, an oil cylinder 1# control loop and an oil return pressure relief device;

the oil tank device is used for storing hydraulic oil;

the main pump device is used for providing pressure for the oil cylinder;

the circulating filtering and cooling device is used for filtering the hydraulic oil in the oil tank to ensure that the hydraulic oil reaches the required oil accuracy and can cool the hydraulic oil;

the pilot oil motor pump group is used for providing pressure oil for pilot control for the main pump flow control loop;

the main pump flow control loop is used for controlling the flow provided by the main pump device to the 1# oil cylinder, the 2# oil cylinder and the 3# oil cylinder, and meeting the speed requirement of the oil cylinder action working condition;

the cylinder 2# control loop is used for controlling the action of the cylinder 2 #;

the 3# oil cylinder control loop is used for controlling the action of the 3# oil cylinder;

the oil cylinder 1# control loop is used for controlling the action of the 1# oil cylinder;

the oil return pressure relief device is used for filtering oil passing through the main loop pipes of the oil cylinders.

Further, the main pump device comprises a seventh pressure sensor, a first electromagnetic valve, a pressure gauge, a sixth one-way valve, a first ball valve, a first shock absorption throat first butterfly valve, a first motor and a first plunger pump; a first electromagnetic overflow valve and a first filter.

Furthermore, the circulating filtration cooling device comprises a twelfth pressure measuring joint, a thirteenth pressure measuring joint, a fifth butterfly valve, a sixth butterfly valve, a fifth shock absorption throat, a sixth shock absorption throat, a fourth motor, a fifth motor, a first screw pump, a second screw pump, a first check valve, a second check valve, a seventh butterfly valve, an eighth butterfly valve, a ninth butterfly valve, a tenth butterfly valve, an eleventh butterfly valve, a second filter, a cooler, a twelfth butterfly valve, a thirteenth butterfly valve, an electromagnetic water valve and a water filter.

Further, the pilot oil motor-pump set comprises a third butterfly valve, a fourth butterfly valve, a third shock-absorbing throat, a fourth shock-absorbing throat, a first plunger pump, a second motor, a third motor, a second filter, a third filter, a second electromagnetic overflow valve, a third electromagnetic overflow valve, a sixth one-way valve and a seventh one-way valve.

Furthermore, the main pump flow control loop comprises a first pressure sensor, a second pressure sensor, a first proportional valve, a second proportional valve, a first electromagnetic valve, a second electromagnetic valve, a first two-way cartridge valve, a second two-way cartridge valve, a first one-way valve, a second one-way valve, a pressure oil filter, a safety valve group, an energy accumulator, a first pressure measuring joint, a second pressure measuring joint, a third pressure measuring joint and a fourth pressure measuring joint.

Further, the oil cylinder 2# control loop comprises a 2# oil cylinder, a third pressure sensor, a fourth pressure sensor, a sixth pressure measuring joint, a seventh pressure measuring joint, an eighth pressure measuring joint, a first overflow valve, a second overflow valve, a third overflow valve, a first electromagnetic ball valve, a second electromagnetic ball valve, a third electromagnetic ball valve, a fourth electromagnetic ball valve, a first pilot overflow valve, a second pilot overflow valve, a first proportional overflow valve, a second proportional overflow valve and a first electromagnetic ball valve; the second electromagnetic ball valve, the first throttle valve, the second throttle valve, the third two-way cartridge valve, the fourth two-way cartridge valve, the fifth two-way cartridge valve, the sixth two-way cartridge valve, the fourth one-way valve, the first shuttle valve and the second shuttle valve.

Further, the oil cylinder 1# control loop comprises a 1# oil cylinder, a fifth pressure sensor, a third throttle valve, a fourth throttle valve, a ninth pressure measuring joint, a tenth pressure measuring joint, an eleventh pressure measuring joint, a fourth overflow valve, a fifth overflow valve, a sixth overflow valve, a seventh overflow valve, a fifth electromagnetic ball valve, a sixth electromagnetic ball valve, a third pilot overflow valve, a third proportional overflow valve, a seventh two-way cartridge valve, a third shuttle valve, a first electromagnetic ball valve, a second electromagnetic ball valve, an eighth two-way cartridge valve, a ninth two-way cartridge valve, a twelfth cartridge valve and a balance valve.

Further, the oil return pressure relief device comprises a fourteenth pressure measuring joint, a fifteenth pressure measuring joint, a fourteenth butterfly valve, a second electromagnetic valve, a fifteenth butterfly valve, a sixteenth butterfly valve and a filter.

The side surface of the oil tank device is provided with an oil suction flange at a low position and is connected with an oil suction pipe fitting of a pump of each part, and the side surface of the oil tank device is connected with an oil return pipe or an oil drainage pipe of each part at a high position; pressure oil pipes P01 and P02 of a main pump device are connected with ports P1, P2 and P3 of a 6 main pump flow control loop, an oil drain pipe is connected with an oil return port of an oil tank device, sensitive control oil ports X01 and X02 of the main pump device are connected with an oil port X1 of the main pump flow control loop, and oil drain ports T01 and T02 of a first electromagnetic overflow valve are connected with an oil return port of the oil tank; an oil suction port of the pilot oil motor pump set is connected with an oil suction port flange at a low position on the side surface of the oil tank device, and an oil drainage port of the pilot oil motor pump set is connected with an oil return port of the oil tank device; oil drain pipes T11 and T12 of the second electromagnetic overflow valve and the third electromagnetic overflow valve are connected with oil drain pipes T11 and T12 of an oil return port of the oil tank device, and are connected with an oil return port of the oil tank device; p1, P2 and P3 of the main pump flow control loop are respectively connected with pressure oil ports P01 and P02 of the main pump device and are connected with an L4 port of the oil return pressure relief device; oil outlets of the first proportional valve, the second proportional valve and the third proportional valve are respectively connected with P4, P5 and P6 of the oil cylinder 2# control circuit, the oil cylinder 3# control circuit and the oil cylinder 1# control circuit, and are connected with oil outlets X01 and X02 of the main pump device after passing through the first one-way valve and the second one-way valve; the oil drainage ports of the first proportional valve, the second proportional valve and the third proportional valve are connected with an oil return port of the oil tank device; an X port of the main pump flow control loop is connected with a pressure oil port X of the pilot oil motor pump set; a pressure oil inlet P4 of the oil cylinder 2# control loop is connected with a P4 of a main pump flow control loop, T2 oil outlets of a fifth two-way cartridge valve and a sixth two-way cartridge valve are connected with a T2 oil drainage port of an oil return pressure relief device, and an L2 oil drainage port is connected with an L2 oil drainage port of the oil return pressure relief device; the pressure oil inlet P6 is connected with the P6 of the main pump flow control loop; oil outlets T1 of the seventh two-way cartridge valve and the ninth two-way cartridge valve are connected with an oil outlet T1 of the oil return pressure relief device, and an oil drain port L1 is connected with an oil drain port L1 of the oil return pressure relief device; oil ports of main loop pipes T1, T2 and T3 of the oil return pressure relief device are respectively connected with oil pipes of main loops T1, T2 and T3 of an oil cylinder 1# control loop, an oil cylinder 2# control loop and an oil cylinder 3# control loop, and oil drainage ports of L1, L2 and L3 are respectively connected with oil drainage ports of L1, L2 and L3 of 3 oil cylinder control loops; the main P spill port L4 is connected to port L4 of the main pump flow control circuit.

The hydraulic system of the high-flow squeezer has the advantages of being smaller in energy consumption, better in shock absorption effect and capable of effectively preventing the high-flow overflow phenomenon.

Drawings

FIG. 1 is a block diagram of the present invention.

Description of reference numerals: 1 an oil tank device; 2 a main pump means; n groups of main pump devices; 4 circulating, filtering and cooling device; 5 a pilot oil pump device; 6, a main pump flow control loop; 7, a cylinder 2# control loop; 8, an oil cylinder 3# control loop; 9 oil cylinder 1# control loop; 10 oil return pressure relief device; 11.1 a first pressure sensor; 11.2 a second pressure sensor; 11.3 a third pressure sensor; 11.4 a fourth pressure sensor; 11.5 a fifth pressure sensor; 11.6 sixth pressure sensor; 11.7 seventh pressure sensor; 12.1 a first proportional valve; 12.2 a second proportional valve; 13 a third proportional valve; 14.1 a first solenoid valve; 14.2 a second solenoid valve; 15 a first two-way cartridge valve; 16 a second two-way cartridge valve; 17.1 a first one-way valve; 17.2 a second one-way valve; 18 a pressurized oil filter; 19 a safety valve group; 20 an accumulator; 21.1 a first pressure tap, 21.2 a second pressure tap; 21.3 a third pressure tap; 21.4 fourth pressure tap; 21.5 a fifth pressure tap; 21.6 sixth pressure tap; 21.7 a seventh pressure tap; 21.8 eighth pressure tap; 21.9 a ninth pressure tap; 21.10 tenth pressure tap; 21.11 eleventh pressure tap; 21.12 twelfth pressure tap; 21.13 a thirteenth pressure tap; 21.14 a fourteenth pressure tap; 21.15 a fifteenth pressure tap; 22.1 a first relief valve; 22.2 a second overflow valve; 22.3 a third overflow valve; 22.4 a fourth overflow valve; 22.5 a fifth relief valve; 22.6 sixth relief valve; 22.7, a seventh overflow valve; 23.1 a first electromagnetic ball valve; 23.2 a second electromagnetic ball valve; 23.3 a third electromagnetic ball valve; 23.4 fourth electromagnetic ball valve; 23.5 a fifth electromagnetic ball valve; 23.6 sixth electromagnetic ball valve; 23.7 seventh electromagnetic ball valve; 24.1 a first pilot overflow valve; 24.2 a second pilot overflow valve; 24.3 a third pilot overflow valve; 25.1 a first proportional relief valve; 25.2 a second proportional relief valve; 25.3 a third proportional relief valve; 26.1 a first electromagnetic ball valve; 26.2 a second electromagnetic ball valve; 27.1 a first throttle valve; 27.2 a second throttle valve; 27.3 a third throttle valve; 27.4 fourth throttle valve; 28 a third two-way cartridge valve; 29 a fourth two-way cartridge valve; 30 a fifth two-way cartridge valve; 31.1 a sixth two-way cartridge valve; 31.2 a seventh two-way cartridge valve; 32.1 a fourth one-way valve; 32.2 a fifth one-way valve; 33.1 a first shuttle valve; 33.2 a second shuttle valve; 33.3 a third shuttle valve; 33.4 a fourth shuttle valve; 34.1 a first electromagnetic ball valve; 34.2 a second electromagnetic ball valve; 35.1 an eighth two-way cartridge valve; 35.2 a ninth two-way cartridge valve; 36 twelfth through cartridge valve; 37 a balancing valve; 38.1 a first solenoid valve; 39.1 pressure gauge; 40.1 a sixth one-way valve; 41.1 a first ball valve; 42.1 first shock throat; 43.1 first butterfly valve; 44.1 a first electric machine; 45 a first plunger pump; 46.1 a first electromagnetic spill valve; 47.1 a first filter; 51.1 third butterfly valve; 51.2 fourth butterfly valve; 52.1 third shock throat; 52.2 fourth shock throat; 53.1 first plunger pump; 53.2 second plunger pump; 54.1 a second motor; 54.2 a third motor; 55.1 a second filter; 55.2 a third filter; 56.1 a second electromagnetic overflow valve; 56.2 a third electromagnetic overflow valve; 57.1 sixth one-way valve; 57.2 seventh check valve; 61.1 fifth butterfly valve, 61.2 sixth butterfly valve; 62.1 fifth shock absorbing throat; 62.2 sixth shock absorbing throat; 63.1 a fourth motor; 63.2 a fifth motor; 64.1 a first screw pump; 64.2 a second screw pump; 65.1 a first check valve; 65.2 second check valve; 66.1 a seventh butterfly valve; 66.2 an eighth butterfly valve; 66.3 ninth butterfly valve; 66.4 tenth butterfly valve; 66.5 an eleventh butterfly valve; 67 a second filter; 68 a cooler; 69.1 twelfth butterfly valve; 69.2 a thirteenth butterfly valve; 70 electromagnetic water valve; 71 a water filter; 80 a fourteenth butterfly valve; 81 a second solenoid valve; 82.1 a fifteenth butterfly valve; 82.2 sixteenth butterfly valve; 83 a third filter; 91 an air cleaner; 92 a liquid level meter; 93 a temperature sensor; 94 liquid level sensors; 95 oil drain ball valve; a11# oil cylinder rodless cavity; the B11# oil cylinder is provided with a rod cavity; a22# oil cylinder rodless cavity; the B22# oil cylinder is provided with a rod cavity; a33# oil cylinder rodless cavity; the B33# oil cylinder is provided with a rod cavity.

Detailed Description

Embodiment 1, as shown in fig. 1, the hydraulic system of the high-flow squeezer comprises an oil tank device 1 and N groups of main pump devices 3, where the N groups of main pump devices represent that the number of the main pump devices 2 may be 1, 2, or 3, or another number, a circulation filtration cooling device 4, a pilot oil motor-pump set 5, a main pump flow control circuit 6, a cylinder 2# control circuit 7, a cylinder 3# control circuit 8, a cylinder 1# control circuit 3, and a return oil pressure relief device 10.

Oil tank device 1: the hydraulic oil storage tank is mainly used for storing hydraulic oil and is provided with monitoring elements such as a liquid level and an oil temperature. The oil tank device 1 is provided with an oil suction flange at the lower side and connected with an oil suction pipe fitting of the pump of each part, and the oil tank device 1 is connected with an oil return or drainage pipe of each part at the higher side.

The circulating filtering and cooling device 4 is used for filtering the hydraulic oil in the oil tank to ensure that the hydraulic oil reaches the required oil accuracy and can cool the hydraulic oil; pressure oil pipes P01 and P02 of the main pump device 2 are connected with ports P1, P2 and P3 of the main pump flow control loop 6, an oil drain pipe is connected with an oil return port of the oil tank device 1, sensitive control oil ports X01 and X02 of the main pump device 2 are connected with an oil port X1 of the main pump flow control loop 6, and an oil drain port T01 and a oil drain port T02 of a first electromagnetic overflow valve 22.1 of the main pump device 2 are connected with an oil return port of the oil tank.

The pilot oil motor-pump set 5 is used for providing pressure oil for pilot control for the main pump flow control loop 6; an oil suction port of the pilot oil motor pump set 5 is connected with an oil suction port flange at a lower position on the side surface of the oil tank device 1, and an oil drainage port of the pilot oil motor pump set 5 is connected with an oil return port of the oil tank device 1; oil drain pipes T11 and T12 of the second electromagnetic overflow valve 56.1 and the third electromagnetic overflow valve 56.2 are connected with an oil return port of the oil tank device 1, and a pressure oil port X of the pilot oil motor pump set 5 is connected with an X port of the main pump flow control loop 6.

The main pump flow control loop 6 is used for controlling the flow provided by the main pump device 2 to the 1# oil cylinder, the 2# oil cylinder and the 3# oil cylinder, and meeting the speed requirement of the oil cylinder action working condition; p1, P2 and P3 of the main pump flow control circuit 6 are respectively connected with pressure oil ports P01 and P02 of the main pump device 2 and are connected with an L4 port of the oil return pressure relief device 10; oil outlets of the first proportional valve 12.1, the second proportional valve 12.2 and the third proportional valve 13 are respectively connected with P4, P5 and P6 of the oil cylinder 2# control circuit 7, the oil cylinder 3# control circuit 8 and the oil cylinder 1# control circuit 9, and are connected with oil outlets X01 and X02 of the main pump device 2 after passing through the first check valve 17.1 and the second check valve 17.2; the oil drainage ports of the first proportional valve 12.1, the second proportional valve 12.2 and the third proportional valve 13 are connected with an oil return port of the oil tank device 1; an X port of the main pump flow control loop 6 is connected with a pressure oil port X of the pilot oil motor pump set 5; a pressure oil inlet P4 of the oil cylinder 2# control loop 7 is connected with a P4 of a main pump flow control loop 6, T2 oil outlets of a fifth two-way cartridge valve 30 and a sixth two-way cartridge valve 31.1 are connected with a T2 oil drainage port of the oil return pressure relief device 10, and an L2 oil drainage port is connected with an L2 oil drainage port of the oil return pressure relief device 10; the pressure oil inlet P6 is connected with the P6 of the main pump flow control loop 6; an oil outlet T1 of T1 of the seventh two-way cartridge valve 31.2 and the ninth two-way cartridge valve 35.2 is connected with an oil outlet T1 of the oil return pressure relief device 10, and an oil drain port L1 is connected with an oil drain port L1 of the oil return pressure relief device 10; oil drainage ports of main loop pipes T1, T2 and T3 of the oil return pressure relief device 10 are respectively connected with oil pipes of main loops T1, T2 and T3 of an oil cylinder 1# control loop 9, an oil cylinder 2# control loop 7 and an oil cylinder 3# control loop 8, and oil drainage ports of L1, L2 and L3 are respectively connected with oil drainage ports of L1, L2 and L3 of the oil cylinder 1# control loop 9, the oil cylinder 2# control loop 7 and the oil cylinder 3# control loop 8; the main P spill port L4 is connected to port L4 of the main pump flow control circuit.

The cylinder 2# control circuit 7 is used for controlling the operation of the 2# cylinder.

The cylinder 3# control circuit 8 is used for controlling the action of the 3# cylinder.

The cylinder 1# control circuit 9 is used for controlling the operation of the 1# cylinder.

The oil return pressure relief device 10 is used for filtering oil passing through the main loop pipes of the oil cylinders.

The main pump device 2 comprises a seventh pressure sensor 11.7, a first electromagnetic valve 38.1, a pressure gauge 39.1, a sixth one-way valve 40.1, a first ball valve 41.1, a first shock absorption throat 42.1, a first butterfly valve 43.1, a first motor 44.1 and a first plunger pump 45; first electromagnetic spill valve 46.1, first filter 47.1.

The circulating filtering cooling device 4 comprises a twelfth pressure measuring joint 21.12, a thirteenth pressure measuring joint 21.13, a fifth butterfly valve 61.1, a sixth butterfly valve 61.2, a fifth shock absorbing throat 62.1, a sixth shock absorbing throat 62.2, a fourth motor 63.1, a fifth motor 63.2, a first screw pump 64.1, a second screw pump 64.2, a first check valve 65.1, a second check valve 65.2, a seventh butterfly valve 66.1, an eighth butterfly valve 66.2, a ninth butterfly valve 66.3, a tenth butterfly valve 66.4, an eleventh butterfly valve 66.5, a second filter 67, a cooler 68, a twelfth butterfly valve 69.1, a thirteenth butterfly valve 69.2, an electromagnetic water valve 70 and a water filter 71.

The pilot oil motor-pump group 5 comprises a third butterfly valve 51.1, a fourth butterfly valve 51.2, a third shock absorption throat 52.1, a fourth shock absorption throat 52.2, a first plunger pump 53.1, a second plunger pump 53.2, a second motor 54.1, a third motor 54.2, a second filter 55.1, a third filter 55.2, a second electromagnetic overflow valve 56.1, a third electromagnetic overflow valve 56.2, a sixth one-way valve 57.1 and a seventh one-way valve 57.2.

The main pump flow control loop 6 comprises a first pressure sensor 11.1, a second pressure sensor 11.2, a first proportional valve 12.1, a second proportional valve 12.2, a proportional valve 13, a first electromagnetic valve 14.1, a second electromagnetic valve 14.2, a first two-way cartridge valve 15, a second two-way cartridge valve 16, a first one-way valve 17.1, a second one-way valve 17.2, a pressure oil filter 18, a safety valve group 19, an energy accumulator 20, a first pressure measuring joint 21.1, a second pressure measuring joint 21.2, a third pressure measuring joint 21.3 and a fourth pressure measuring joint 21.4.

The oil cylinder 2# control circuit 7 comprises a 2# oil cylinder rodless cavity A2, a 2# oil cylinder rod cavity B2, a third pressure sensor 11.3, a fourth pressure sensor 11.4, a sixth pressure measuring joint 21.6, a seventh pressure measuring joint 21.7, an eighth pressure measuring joint 21.8, a first overflow valve 22.1, a second overflow valve 22.2, a third overflow valve 22.3, a first electromagnetic ball valve 23.1, a second electromagnetic ball valve 23.2, a third electromagnetic ball valve 23.3, a fourth electromagnetic ball valve 23.4, a first pilot overflow valve 24.1, a second pilot overflow valve 24.2, a first proportional overflow valve 25.1, a second proportional overflow valve 25.2 and a first electromagnetic ball valve 26.1; a second electromagnetic ball valve 26.2, a first throttle valve 27.1, a second throttle valve 27.2, a third two-way cartridge valve 28, a fourth two-way cartridge valve 29, a fifth two-way cartridge valve 30, a sixth two-way cartridge valve 31.1, a fourth one-way valve 32.1, a first shuttle valve 33.1 and a second shuttle valve 33.2. The control circuit 3# 8 is similar to the control circuit 7 # 2# in structure, as shown in fig. 1, and will not be described in detail herein.

The oil cylinder 1# control circuit 9 comprises a 1# oil cylinder, and the 1# oil cylinder comprises a 1# oil cylinder rodless cavity A1; the 1# oil cylinder is provided with a rod cavity B1; a fifth pressure sensor 11.5, a third pressure sensor 11.3, a third check valve 17.3, a fourth check valve 17.4, a ninth pressure tap 21.9, a tenth pressure tap 21.10, an eleventh pressure tap 21.11, a fourth relief valve 22.4, a fifth relief valve 22.5, a sixth relief valve 22.6, a seventh relief valve 22.7, a fifth electromagnetic ball valve 23.5, a sixth electromagnetic ball valve 23.6, a third pilot relief valve 24.3, a third proportional relief valve 25.3, a seventh two-way cartridge valve 31.2, a third shuttle valve 33.3, a third shuttle valve 33.4, a first electromagnetic ball valve 34.1, a second electromagnetic ball valve 34.2, an eighth two-way cartridge valve 35.1, a ninth two-way cartridge valve 35.2, a twelfth cartridge valve 36 and a balance valve 37.

The oil return pressure relief device 10 comprises a fourteenth pressure measuring joint 21.14, a fifteenth pressure measuring joint 21.15, a fourteenth butterfly valve 80, a second electromagnetic valve 81, a fifteenth butterfly valve 82.1, a sixteenth butterfly valve 82.2 and a filter 83.

As shown in fig. 1, the high-flow press hydraulic system further includes an air cleaner 91, a liquid level meter 92, a temperature sensor 93, a liquid level sensor 94 and an oil drain ball valve 95;

the function of the hydraulic system of the large-flow squeezer is realized by the following steps as shown in figure 1:

s1: preparation before boot

A first ball valve 41.1, a first butterfly valve 43.1, a third butterfly valve 51.1, a fourth butterfly valve 51.2, a fifth butterfly valve 61.1, a sixth butterfly valve 61.2, an eighth butterfly valve 66.2, a ninth butterfly valve 66.3, a tenth butterfly valve 66.4, a twelfth butterfly valve 69.1 and a thirteenth butterfly valve 69.2; the fourteenth butterfly valve 80, the fifteenth butterfly valve 82.1, the sixteenth butterfly valve 82.2, etc. are in an open state as required, wherein the seventh butterfly valve 66.1 and the eleventh butterfly valve 66.5 are in a closed state.

S2: the circulation cooling and filtering device 4 is started

When any one of the fourth motor 63.1 and the fifth motor 63.2 of the circulating filtering and cooling device 4 is started, the oil in the oil suction cavity of the oil tank device 1 returns to the oil suction cavity of the oil tank device 1 through the fifth butterfly valve 61.1, the sixth butterfly valve 61.2, the fifth damping throat 62.1, the sixth damping throat 62.2, the first screw pump 64.1, the second screw pump 64.2, the check valve 65, the eighth butterfly valve 66.2, the second filter 67, the ninth butterfly valve 66.3, the cooler 68 and the tenth butterfly valve 66.4, thereby completing the circulating filtering action. If the temperature of the oil tank (the temperature sensor 93 provides analog quantity data) is higher than 50 ℃, the electromagnetic water valve 70 is powered on, cooling water flows back to the water tank after passing through the water filter 71, the electromagnetic water valve 70, the twelfth butterfly valve 69.1, the cooler 68 and the thirteenth butterfly valve 69.2, and the exchange of oil and water cooling heat is realized inside the cooler 68, so that the oil in the oil tank achieves the cooling effect. The seventh butterfly valve 66.1 is opened for use when oil is drained or supplemented from the oil tank; the eleventh butterfly valve 66.5 is used for not influencing the circulation filtering work when the cooler 68 is in failure, and can also be used for replacing the cooler 68 without stopping the machine, when the ninth butterfly valve 66.3 and the tenth butterfly valve 66.4 need to be closed, the eleventh butterfly valve 66.5 is opened, and the hydraulic oil of the second filter 67 flows back to the oil tank through the eleventh butterfly valve 66.5. The second screw pump 64.2 is equipped with a relief valve for safety, and the pressure is generally set to 1 MPa.

S3: starting the leading oil motor-pump set 5

Either the second motor 54.1 or the third motor 54.2 is started. The pressure of the first plunger pump 53.1 and the second plunger pump 53.2 is set to 16 MPa. The second electromagnetic overflow valve 56.1 and the third electromagnetic overflow valve 56.2 are set to be 18MPa, when the electromagnetic overflow valves 56.1 and 56.2 are not electrified, the pressure relief effect is achieved, and the pressure of a pilot oil system is almost zero at the moment; when the second electromagnetic overflow valve 56.1 and the third electromagnetic overflow valve 56.2 are powered on, the safety storage function is performed, and the pressure of the pilot system is 16MPa, which is consistent with the set pressure of the first plunger pump 53.1 and the set pressure of the second plunger pump 53.2. During operation, the oil liquid passes through the 51.1 third butterfly valve and the 51.2 fourth butterfly valve, the third damper throat 52.1 and the fourth damper throat 52.2, the first plunger pump 53.1 and the second plunger pump 53.2, the second filter 55.1 and the third filter 55.2, the sixth check valve 57.1 and the seventh check valve 57.2, then reaches the port X of the main pump flow control loop 6, and passes through the first two-way cartridge valve 15, and then hydraulic oil for pilot valve control is provided for the first proportional valve 12.1, the second proportional valve 12.2 and the third proportional valve 13 of the main pump flow control loop 6.

S4: main system pressure oil supply

Motors in the main pump device 2 and the N main pump devices 3 are started successively (the number of the N main pump devices can be selected according to the total flow of the system required actually), the highest pressure of the first plunger pump 45 is set to be 30MPa, the first electromagnetic overflow valve 46.1 is set to be 32MPa, when the first electromagnetic overflow valve 46.1 is not powered, the pressure relief effect is achieved, and at the moment, the main system has no pressure; when the first electromagnetic overflow valve 46.1 is powered on, the safety storage function is performed, and the pressure of the main system is determined by the first motor 44.1. The first motor 44.1 selects the functions of constant power, load sensitivity and constant pressure variable, and the load pressure oil is led from the P4, the P5 and the P6 in the main pump flow control loop 6, passes through the first check valve 17.1, the second check valve 17.2, the third check valve 17.3, the fourth check valve 17.4 and the first electromagnetic valve 38.1 and then is connected to the X2 port of the first plunger pump 45. When the first solenoid valve 38.1 is de-energized, the load-sensitive functions of the eighth and ninth two-way cartridges 35.1, 35.2 are active, with the flow rate of the main pump being determined by the size of the openings of the first, second and third proportional valves 12.1, 12.2, 13 at P4, P5, P6, etc. When the first electromagnetic valve 38 is energized, the first plunger pump 45 is in an energy-saving standby state with low pressure (about 2MPa) close to zero displacement. In operation, hydraulic oil in the oil tank flows through the first butterfly valve 43.1, the first shock absorption throat 42.1, the first plunger pump 45, the first filter 47.1, the sixth check valve 40 and the first ball valve 41.1 to the P1, the P2 and the P3 of the main pump flow control loop 6. P1 and P2 pass through the first and second proportional valves 12.1 and 12.2, respectively. When the oil cylinder needs to rapidly act, the first electromagnetic valve 14.1 and the second electromagnetic valve 14.2 are not electrified, the first two-way cartridge valve 15 is opened, and the P1 and the P2 are combined to allow one oil cylinder to rapidly act. When the first solenoid valve 14.1 and the second solenoid valve 14.2 are electrified, the first two-way cartridge valve 15 is in a closed state, and then P1 controls the actuating speed of the 2# oil cylinder, and P2 controls the actuating speed of the 3# oil cylinder. P3 controls the action speed of the 1# oil cylinder through the third proportional valve 13.

S5: 1# Cylinder actuation

A. 1# oil cylinder extending action

The first electromagnetic ball valve 34.1 is electrified, and the eighth two-way cartridge valve 35.1 is opened; and the second electromagnetic ball valve is de-energized, and the ninth two-way cartridge valve 35.2 is closed. The pressure of the balance valve 37 is set to be 3MPa, and the pressure of the fourth overflow valve 22.4 is set to be 20MPa, so that the safety protection effect is achieved; the fifth overflow valve 22.5 is set to be 15MPa, and when the sixth electromagnetic ball valve 23.6 is powered on, the fifth overflow valve is used for pushing material safety protection; the maximum pressure of the third pilot relief valve 24.3 is adjusted to 20MPa, the working pressure of the third pilot relief valve can be determined by the third proportional relief valve 25.3 on the pilot oil path, and the third proportional relief valve 25.3 acts when the seventh electromagnetic ball valve 23.7 is electrified. The fifth pressure sensor 11.5 and the sixth pressure sensor 11.6 can monitor the pressure values of the two cavities of the oil cylinder in real time, and the third throttle valve 27.3 and the fourth throttle valve 27.4 can adjust the closing speed of the eighth two-way cartridge valve 35.1 and the ninth two-way cartridge valve 35.2 of the two-way cartridge valve. The flow rate of oil supplied by the oil cylinder is determined by the third proportional valve 13.

When the oil cylinder extends, pressure oil provided by a main pump reaches P3, then is electrically opened through the third proportional valve 13 to reach P6, and reaches the rodless cavity A1 of the No. 1 oil cylinder through the eighth two-way cartridge valve 35.1, and along with the pressure rise of the cavity A1, the hydraulic oil opens the balance valve 37 through the X3, and then opens the two-way cartridge valve 36. Oil from the cylinder B1 may flow back to the tank through the twelfth-way cartridge 36, thereby pushing the cylinder out.

When the oil cylinder extends to push the material, the sixth electromagnetic ball valve 23.6 is electrified, the fifth overflow valve 22.5 is in action, and the maximum pressure of the No. 1 oil cylinder rodless cavity A1 is determined by the fifth overflow valve 22.5 and is 15 MPa.

When the oil cylinder extends to the terminal, the electric signal value of the third proportional valve 13 is continuously reduced until the power is cut off, the oil cylinder extends out and stops, and meanwhile the first electromagnetic ball valve 34.1 and the sixth electromagnetic ball valve 23.6 are powered off.

B. 1# oil cylinder pressure maintaining action

When the oil cylinder completely extends out and stops, the sixth electromagnetic ball valve 23.6 and the first electromagnetic ball valve 34.1 lose electricity, the oil cylinder is self-locked and maintains pressure, and at the moment, the fourth overflow valve 22.4 and the sixth electromagnetic ball valve 23.6 play a role in safety protection. The piston rod is subjected to the acting force of retreating during the pressure maintaining period, and in order to prevent the rod cavity from being damaged in a sealing mode, the fifth one-way valve 32.2 can realize oil supplement.

C. 1# oil cylinder return motion

The fifth electromagnetic ball valve 23.5 is electrified, the 1# oil cylinder rodless cavity A1 is decompressed, the seventh electromagnetic ball valve 23.7 is electrified, the third proportional overflow valve 25.3 does not give a signal, and the eighth two-way cartridge valve is opened at the moment. When the pressure of the rodless cavity A1 of the 1# oil cylinder is reduced to be lower than 2MPa, the second electromagnetic ball valve 34.2 is electrified, the ninth two-way cartridge valve 35.2 is opened, hydraulic oil reaches the rod cavity B1 of the 1# oil cylinder after passing through the ninth two-way cartridge valve, the oil tank is pushed to move back, and the hydraulic oil in the rodless cavity A1 of the 1# oil cylinder flows back to the oil tank through the seventh two-way cartridge valve 31.2.

When the return motion is near the terminal, the third proportional overflow valve 25.3 gives an increasing signal, and the third proportional valve 13 gives a decreasing signal at the same time, until the oil cylinder stops in place, the seventh electromagnetic ball valve 23.7, the second electromagnetic ball valve 34.2, the third proportional overflow valve 25.3 and the third proportional valve 13 are all de-energized.

S6: 2# Cylinder actuation

A. Fast forward extending action of 2# oil cylinder

The first electromagnetic ball valve 26.1 is electrified, and the third two-way cartridge valve 28 is opened; the second electromagnetic ball valve 26.2 is energized and the fourth two-way cartridge valve 29 is opened. The first overflow valve 22.1 is set to be 30MPa, so that the safety protection effect is realized; the second overflow valve 22.2 is set to be 20MPa, and when the first electromagnetic ball valve 23.1 is electrified, the second overflow valve is used for pushing material safety protection; the maximum pressure of the first pilot relief valve 24.1 is adjusted to 30MPa, the working pressure of the first pilot relief valve can be determined by the first proportional relief valve 25.1 on the pilot oil path, and the first proportional relief valve 25.1 acts when the second electromagnetic ball valve 23.2 is electrified. The third pressure sensor 11.3 and the fourth pressure sensor 11.4 can monitor the pressure values of the two cavities of the oil cylinder in real time, and the first throttle valve 27.1 and the second throttle valve 27.2 can adjust the opening and closing speeds of the third two-way cartridge valve 28 and the fourth two-way cartridge valve 29. The flow rate of oil supplied by the oil cylinder is determined by the proportional valve 12.

All main pump devices including the main pump control device 2 and all main pump devices in the N groups supply oil simultaneously, the first proportional valve 12.1 and the second proportional valve 12.2 supply maximum electric signal values simultaneously, meanwhile, the first electromagnetic ball valve 26.1 and the second electromagnetic ball valve 26.2 are electrified, and the third two-way cartridge valve 28 and the fourth two-way cartridge valve 29 are opened simultaneously. At the moment, hydraulic oil of the main pump passes through the P1 and the first proportional valve 12.1 to reach the P4, and is merged with hydraulic oil passing through the P2, the second proportional valve 12.2 and the first two-way cartridge valve 15 at the P4, so that the maximum oil supply amount of the system is realized. Because the area difference exists between the rodless cavity of the oil cylinder and the marked cavity, under the condition that the oil pressure in the two cavities is the same, the force of the rodless cavity A2 of the 2# oil cylinder acting on the oil plug is larger than the force of the rodless cavity B2 of the 2# oil cylinder acting on the piston in a counter action mode (generally, the acting force of the rodless cavity is about 2 times of that of the rodless cavity). When the P4 communicates the 2# oil cylinder rodless cavity A2 with the 2# oil cylinder rod cavity B2, the oil cylinder can extend under the action of the difference of the two cavity surfaces, and at the moment, the oil in the 2# oil cylinder rod cavity B2 flows back to the 2# oil cylinder rodless cavity A2, so that the flow of the 2# oil cylinder rodless cavity A2 is increased, which is generally 2 times of the normal action, and the rapid extending action is realized. When the first electromagnetic ball valve extends out quickly, the first electromagnetic ball valve 23.1 is electrified, and the second overflow valve 22.2 plays a role in pushing safety protection.

B. Working feed and extension action of 2# oil cylinder

When the oil cylinder rapidly extends to a specified position or the pressure of a rodless cavity A2 of the No. 2 oil cylinder reaches a specified value, the fourth electromagnetic ball valve 23.4 is electrified, and the second proportional overflow valve 25.2 gives a certain signal value for controlling the opening size of the sixth two-way cartridge valve 31.1. Then the second electromagnetic ball valve 26.2 is de-energized and the fourth two-way cartridge valve 29 is closed. At the moment, the hydraulic oil of P4 reaches the No. 2 cylinder rodless cavity A2, and pushes the cylinder to extend. Oil in a rod cavity B2 of the No. 2 oil cylinder flows back to the oil tank through the sixth two-way cartridge valve, and the switching of the fast extension and the operation of the extension of the rotary tool is realized.

When the work enters and extends out, the first electromagnetic ball valve 23.1 loses power, and the second overflow valve 22.2 does not work; at this time, the first overflow valve 22.1 and the first electromagnetic ball valve 23.1 play a safety protection role.

When the oil cylinder extends to the terminal, the second proportional valve 12.2 does not give a signal value, the electric signal value of the first proportional valve 12.1 is continuously reduced until power failure, meanwhile, the second proportional overflow valve 25.2 gives an incremental signal value until the oil cylinder extends to stop, and oil inlet proportional throttling and oil return proportional throttling are adopted in the braking process, so that stable braking is realized. After the oil cylinder stops in place, the first electromagnetic ball valve 26.1 and the fourth electromagnetic ball valve 23.4 lose power at the same time, and the second proportional overflow valve 25.2 does not give a signal value.

C. Pressure maintaining action of 2# oil cylinder

When the oil cylinder completely extends out and stops, the first electromagnetic ball valve 26.1 and the fourth electromagnetic ball valve 23.4 lose electricity, the oil cylinder is self-locked and maintains pressure, and at the moment, the first overflow valve 22.1, the first pilot overflow valve 24.1 and the third overflow valve 22.3 play a safety protection role. The piston rod is subjected to the acting force of retreating during the pressure maintaining period, and in order to prevent the rod cavity from being damaged in a sealing mode, the fourth one-way valve 32.1 can realize oil supplement.

D. 2# oil cylinder retreating action

First, the third electromagnetic ball valve 23.3 is electrified, the 2# oil cylinder rodless cavity A2 is decompressed, meanwhile, the second electromagnetic ball valve 23.2 is electrified, the first proportional overflow valve 25.1 does not give a signal, and at the moment, the fifth two-way cartridge valve 30 is opened. The second electromagnetic ball valve 26.2 is electrified, the fourth two-way cartridge valve 29 is opened, hydraulic oil reaches the rod cavity B2 of the 2# oil cylinder after passing through the fourth two-way cartridge valve 29 to push the oil tank to move back, and the hydraulic oil in the rod-free cavity A2 of the 2# oil cylinder flows back to the oil tank through the fifth two-way cartridge valve.

When the return motion is fast to the terminal, the first proportional overflow valve 25.1 gives an increasing signal, the second proportional valve 12.2 does not give a signal value, the first proportional valve 12.1 gives a decreasing signal, the second electromagnetic ball valve 23.2 and the second electromagnetic ball valve 26.2 lose power until the oil cylinder stops in place, and the first proportional overflow valve 25.1 and the second proportional valve 12.2 do not give signals. The action of the 3# oil cylinder is similar to that of the 2# oil cylinder, and the description is not repeated.

The following table is a comparison table of the energy saving effect of the hydraulic system of the squeezer in the technical scheme of the application and two prior arts.

Compared with the technical scheme in the prior art, the technical scheme in the application has the advantages that the total power is much smaller under the same flow and pressure, the total power of the constant power scheme in the prior art is 375KW when the flow is 850L/min and the pressure is 20Mpa, a single motor can be used only by high power, and the total power of the constant power scheme is 285 KW; when the flow is 1700L/min, the total power of the constant power scheme with the pressure of 5Mpa is 200KW, the total power of the constant pressure is 200KW, but the total power of the constant pressure is 142KW, and the phenomenon of large flow overflow does not occur.

Claims

1. The utility model provides a large-traffic squeezer hydraulic system which characterized in that: the system comprises an oil tank device, a main pump device, a circulating filtering and cooling device, a pilot oil motor pump set, a main pump flow control loop, an oil cylinder 2# control loop, an oil cylinder 3# control loop, an oil cylinder 1# control loop and an oil return pressure relief device;

the oil tank device is used for storing hydraulic oil;

the main pump device is used for providing pressure for the oil cylinder;

the oil return pressure relief device is used for filtering oil passing through the main loop pipes of the oil cylinders;

an oil suction port flange is arranged at the lower position of the side surface of the oil tank device; pressure oil pipes P01 and P02 of a main pump device are connected with ports P1, P2 and P3 of a main pump flow control loop, an oil drain pipe is connected with an oil return port of an oil tank device, sensitive control oil ports X01 and X02 of the main pump device are connected with an oil port X1 of the main pump flow control loop, and oil drain ports T01 and T02 of a first electromagnetic overflow valve are connected with an oil return port of the oil tank; an oil suction port of the pilot oil motor pump set is connected with an oil suction port flange at a low position on the side surface of the oil tank device, and an oil drainage port of the pilot oil motor pump set is connected with an oil return port of the oil tank device; oil drain pipes T11 and T12 of the second electromagnetic overflow valve and the third electromagnetic overflow valve are connected with an oil return port of the oil tank device, and a pressure oil port X of a pilot oil motor pump set is connected with an X port of a main pump flow control loop; p1, P2 and P3 of the main pump flow control loop are respectively connected with pressure oil ports P01 and P02 of the main pump device and are connected with an L4 port of the oil return pressure relief device; oil outlets of the first proportional valve, the second proportional valve and the third proportional valve are respectively connected with P4, P5 and P6 of the oil cylinder 2# control circuit, the oil cylinder 3# control circuit and the oil cylinder 1# control circuit, and are connected with oil outlets X01 and X02 of the main pump device after passing through the first one-way valve and the second one-way valve; the oil drainage ports of the first proportional valve, the second proportional valve and the third proportional valve are connected with an oil return port of the oil tank device; an X port of the main pump flow control loop is connected with a pressure oil port X of the pilot oil motor pump set; a pressure oil inlet P4 of the oil cylinder 2# control loop is connected with a P4 of a main pump flow control loop, T2 oil outlets of a fifth two-way cartridge valve and a sixth two-way cartridge valve are connected with a T2 oil drainage port of an oil return pressure relief device, and an L2 oil drainage port is connected with an L2 oil drainage port of the oil return pressure relief device; the pressure oil inlet P6 is connected with the P6 of the main pump flow control loop; oil outlets T1 of the seventh two-way cartridge valve and the ninth two-way cartridge valve are connected with an oil outlet T1 of the oil return pressure relief device, and an oil drain port L1 is connected with an oil drain port L1 of the oil return pressure relief device; oil drainage ports of main loop pipes T1, T2 and T3 of the oil return pressure relief device are respectively connected with oil pipes T1, T2 and T3 of a main loop of an oil cylinder 1# control loop, an oil cylinder 2# control loop and an oil cylinder 3# control loop, and oil drainage ports L1, L2 and L3 are respectively connected with oil drainage ports L1, L2 and L3 of the oil cylinder 1# control loop, the oil cylinder 2# control loop and the oil cylinder 3# control loop; the main P spill port L4 is connected to port L4 of the main pump flow control circuit.

2. The high flow press hydraulic system of claim 1, characterized in that: the main pump device comprises a seventh pressure sensor, a first electromagnetic valve, a pressure gauge, a sixth one-way valve, a first ball valve, a first shock-absorbing throat, a first butterfly valve, a first motor, a first plunger pump, a first electromagnetic overflow valve and a first filter.

3. The high flow press hydraulic system of claim 2, characterized in that: the circulating filtration cooling device comprises a twelfth pressure measuring joint, a thirteenth pressure measuring joint, a fifth butterfly valve, a sixth butterfly valve, a fifth shock absorbing throat, a sixth shock absorbing throat, a fourth motor, a fifth motor, a first screw pump, a second screw pump, a first check valve, a second check valve, a seventh butterfly valve, an eighth butterfly valve, a ninth butterfly valve, a tenth butterfly valve, an eleventh butterfly valve, a second filter, a cooler, a twelfth butterfly valve, a thirteenth butterfly valve, an electromagnetic water valve and a water filter.

4. The high flow press hydraulic system of claim 3, characterized in that: the pilot oil motor pump set comprises a third butterfly valve, a fourth butterfly valve, a third shock absorption throat, a fourth shock absorption throat, a first plunger pump, a second motor, a third motor, a second filter, a third filter, a second electromagnetic overflow valve, a third electromagnetic overflow valve, a sixth one-way valve and a seventh one-way valve.

5. The high flow press hydraulic system of claim 4, wherein: the main pump flow control loop comprises a first pressure sensor, a second pressure sensor, a first proportional valve, a second proportional valve, a third proportional valve, a first electromagnetic valve, a second electromagnetic valve, a first two-way cartridge valve, a second two-way cartridge valve, a first one-way valve, a second one-way valve, a pressure oil filter, a safety valve group, an energy accumulator, a first pressure measuring joint, a second pressure measuring joint, a third pressure measuring joint and a fourth pressure measuring joint.

6. The high flow press hydraulic system of claim 5, wherein: the oil cylinder 2# control loop comprises a 2# oil cylinder, a third pressure sensor, a fourth pressure sensor, a sixth pressure measuring joint, a seventh pressure measuring joint, an eighth pressure measuring joint, a first overflow valve, a second overflow valve, a third overflow valve, a first electromagnetic ball valve, a second electromagnetic ball valve, a third electromagnetic ball valve, a fourth electromagnetic ball valve, a first pilot overflow valve, a second pilot overflow valve, a first proportional overflow valve, a second proportional overflow valve and a first electromagnetic ball valve; the second electromagnetic ball valve, the first throttle valve, the second throttle valve, the third two-way cartridge valve, the fourth two-way cartridge valve, the fifth two-way cartridge valve, the sixth two-way cartridge valve, the fourth one-way valve, the first shuttle valve and the second shuttle valve.

7. The high flow press hydraulic system of claim 6, characterized in that: the oil cylinder 1# control loop comprises a 1# oil cylinder, a fifth pressure sensor, a third throttle valve, a fourth throttle valve, a ninth pressure measuring joint, a tenth pressure measuring joint, an eleventh pressure measuring joint, a fourth overflow valve, a fifth overflow valve, a sixth overflow valve, a seventh overflow valve, a fifth electromagnetic ball valve, a sixth electromagnetic ball valve, a third pilot overflow valve, a third proportional overflow valve, a seventh two-way cartridge valve, a third shuttle valve, a first electromagnetic ball valve, a second electromagnetic ball valve, an eighth two-way cartridge valve, a ninth two-way cartridge valve, a twelfth cartridge valve and a balance valve.

8. The high flow press hydraulic system of claim 7, wherein: the oil return pressure relief device comprises a fourteenth pressure measuring joint, a fifteenth pressure measuring joint, a fourteenth butterfly valve, a second electromagnetic valve, a fifteenth butterfly valve, a sixteenth butterfly valve and a filter.