CN105465077B - A kind of hydraulic system of rack-and-pinion lifting device - Google Patents
A kind of hydraulic system of rack-and-pinion lifting device Download PDFInfo
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- CN105465077B CN105465077B CN201510974458.1A CN201510974458A CN105465077B CN 105465077 B CN105465077 B CN 105465077B CN 201510974458 A CN201510974458 A CN 201510974458A CN 105465077 B CN105465077 B CN 105465077B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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Abstract
The invention discloses a kind of hydraulic system of rack-and-pinion lifting device, belong to oil drilling machine jacking system field.The hydraulic system of the rack-and-pinion lifting device, the hydraulic system includes：Hydraulic pump module, main control valve group, multiple motor control components and multiple air bleeding valves positioned at pipeline peak, each motor control component include：Motor balancing valve group and double-speed motor control valve group, the main control valve group include：2/2-way proportional reversing valve, the first inserted valve, the second inserted valve, the 3rd inserted valve, the 4th inserted valve, the 5th inserted valve, the first two four-way electromagnetic reversing valves, the second two four-way electromagnetic reversing valves, 2/2-way reversal valve and overflow valves.The hydraulic system is vented automatically by air bleeding valve, to ensure not having air in hydraulic oil, is prevented the shock and vibration of the system caused by air is present, is reduced the danger of hydraulic system.
Description
Technical field
The present invention relates to oil drilling machine jacking system field, more particularly to a kind of hydraulic pressure of rack-and-pinion lifting device
System.
Background technology
Because oil is the important energy source resource of country, the strategic resource always fought for as various countries is more and more
Oil drilling machine be applied to the land and Sea area of oil rich.It is used as the important component of oil drilling machine
Drilling machinery lifting device, the use for the oil drilling machine that the quality of its performance is directly affected, so as to influence economic benefit.
Conventional drilling machinery lifting device is rack-and-pinion lifting device, and rack-and-pinion lifting device is included with braking
Motor, reductor, the little gear on speed reducer output shaft and the hoisting mechanism of device, rack is fixed and support is used as
Point, makes pinion rotation by motor driving and speed reducer drive, then is engaged by little gear with rack, so as to drive elevator
Structure moves up and down, and completes the processes such as drilling well.When needing stop motion, motor can be pinned by brake, to keep lifting
Mechanism stable is motionless.
During the present invention is realized, inventor has found that prior art at least has problems with：
Due to rack-and-pinion lifting device hydraulic system in the process of running, hydraulic oil can adulterate air, and existing
The hydraulic system of rack-and-pinion lifting device does not possess degassing function again, so the air in hydraulic oil can not be excluded, so, mixes
The hydraulic oil of miscellaneous air can produce noise, vibration and impact in the process of running, have a strong impact on rack-and-pinion lifting device
Stability.
The content of the invention
In order to solve problem of the prior art, the embodiments of the invention provide a kind of hydraulic pressure system of rack-and-pinion lifting device
System.The technical scheme is as follows：
The embodiments of the invention provide a kind of hydraulic system of rack-and-pinion lifting device, the hydraulic system includes：Liquid
Press pump component, main control valve group, multiple motor control components and multiple air bleeding valves positioned at pipeline peak, each motor
Control assembly includes：Motor balancing valve group and double-speed motor control valve group, the main control valve group include：2/2-way ratio
Reversal valve, the first inserted valve, the second inserted valve, the 3rd inserted valve, the 4th inserted valve, the 5th inserted valve, the first two four be powered
Magnetic reversal valve, the second two four-way electromagnetic reversing valves, 2/2-way reversal valve and overflow valves.
The oil-out of the hydraulic pump module is connected with the oil inlet of the 2/2-way proportional reversing valve, 2/2-way ratio
The oil-out A mouths respectively with first inserted valve of example reversal valve, the A mouths of second inserted valve, described the first two four
The P mouths of electric change valve are connected with the P mouths of the second two four-way electromagnetic reversing valves, and the first two four-way electromagnetics are changed
Connected respectively with the X mouths of second inserted valve and the X mouths of the 3rd inserted valve to the A mouths of valve, the second two four-ways
The A mouths of solenoid directional control valve are connected with the X mouths of first inserted valve and the X mouths of the 4th inserted valve respectively, and described first inserts
The B mouths of dress valve are connected with the B mouths of the 3rd inserted valve, the A of the A mouths of the 3rd inserted valve respectively with the 5th inserted valve
Mouth is connected with the A mouths of the 4th inserted valve, and the B mouths of the 4th inserted valve are connected with the B mouths of second inserted valve, described
After the T mouths connection of the T mouths of the first two four-way electromagnetic reversing valves and the second two four-way electromagnetic reversing valves respectively with it is described
The B mouths of 5th inserted valve are connected with the X mouths of the 5th inserted valve, the B mouths and the 5th inserted valve of the 5th inserted valve
X mouths connection after connected with fuel tank.
The oil inlet of the 2/2-way reversal valve is connected with the oil-out of the 2/2-way proportional reversing valve, and described two
The oil-out of the logical reversal valve in position two is connected with the oil inlet of the overflow valve, and the oil-out of the overflow valve connects with the fuel tank
Logical, the rated pressure of the overflow valve is less than the Opening pressure of brake.
The B mouths of second inserted valve A mouths respectively with the motor balancing valve group, the double-speed motor control valve group
A mouthfuls connect with the air bleeding valve, the B mouths of the 3rd inserted valve B mouths respectively with the motor balancing valve group, the double speed horse
B mouths up to control valve group are connected with the air bleeding valve.
Specifically, the motor balancing valve group includes：Balanced valve, A1 mouths and second inserted valve of the balanced valve
B mouthfuls of connections, the B1 mouths of the balanced valve are connected with the B mouths of the 3rd inserted valve.
Further, the motor balancing valve group also includes：First shuttle valve and first pressure sensor, first shuttle valve
A mouths connected with the A2 mouths of the balanced valve, the B mouths of first shuttle valve are connected with the B2 mouths of the balanced valve, described first
The C mouths of shuttle valve are connected with the first pressure sensor；The double-speed motor control valve group includes：Variable oil cylinder, motor variable
Mechanism and the first two-bit triplet solenoid directional control valve, the B mouths of the first two-bit triplet solenoid directional control valve are inserted with the described 3rd respectively
The B mouths of dress valve are connected with the B mouths of second inserted valve, C mouths and the variable of the first two-bit triplet solenoid directional control valve
The rod chamber connection of oil cylinder, the rodless cavity of the variable oil cylinder is connected with the B mouths of the first two-bit triplet solenoid directional control valve, institute
The A mouths for stating the first two-bit triplet solenoid directional control valve are connected with the fuel tank, and piston rod and the motor of the variable oil cylinder become
Measuring mechanism is connected.
Further, the double-speed motor control valve group also includes the first check valve and the second check valve, and described second is single
The B mouths of oil inlet and second inserted valve to valve are connected, oil-out and the two-bit triplet electricity of second check valve
The C mouths connection of magnetic reversal valve, the oil inlet of first check valve is connected with the B mouths of the 3rd inserted valve, and described first is single
The C mouths of oil-out and the two-bit triplet solenoid directional control valve to valve are connected.
Further, the motor balancing valve group also includes：Second shuttle valve, the second two-bit triplet reversal valve and brake pressure
Force snesor 24a, the A mouths of second shuttle valve are connected with the A1 mouths of the balanced valve, and the B mouths of second shuttle valve are put down with described
The B1 mouths connection of weighing apparatus valve, the C mouths of second shuttle valve are connected with the A mouths of the second two-bit triplet reversal valve, described second liang
The position B mouths of three-way diverter valve are connected with the R mouths of the brake, and the brake pressure sensor 24a is connected to described second
On the B mouths of two-bit triplet reversal valve 24, the C mouths of the second two-bit triplet reversal valve are connected with the fuel tank.
Further, the hydraulic system also includes brake control assembly, and the brake control assembly includes：3rd
Check valve, the oil inlet of the 3rd check valve is connected with the R mouths of the brake, the oil-out of the 3rd check valve and institute
State fuel tank connection.
Further, the motor balancing valve group also includes：First damping hole and the second damping hole, first damping hole
It is opened in respectively on the control oil circuit of the balanced valve with second damping hole.
Specifically, the hydraulic pump module includes being mounted on multiple hydraulic pumps, the oil-out of each hydraulic pump
4th check valve, the oil inlet of the 4th check valve is connected with the oil-out of the hydraulic pump, each 4th check valve
Oil inlet of the oil-out with the 2/2-way proportional reversing valve connect.
Further, the hydraulic pump module also includes elastic compensator, and the elastic compensator is arranged on the hydraulic pressure
Between the oil inlet of pump and the fuel tank.
Specifically, the main control valve group also includes：First manual reversal valve and the second hand-operated direction valve, it is described first-hand
The oil inlet of dynamic reversal valve is connected with the oil-out of the hydraulic pump module, the oil-out of the first manual reversal valve with it is described
The B mouths connection of 3rd inserted valve, the oil inlet of second hand-operated direction valve is connected with the oil-out of the hydraulic pump module, institute
The oil-out of the second hand-operated direction valve is stated to connect with the B mouths of second inserted valve.
The beneficial effect that technical scheme provided in an embodiment of the present invention is brought is：The present invention implements the rack-and-pinion of offer
The hydraulic system of lifting device, before hydraulic system life's work, makes 2/2-way solenoid directional control valve obtain electric, overflow valve it is specified
Pressure is less than the Opening pressure of brake so that hydraulic oil can not open brake, and motor will not be rotated, and hydraulic system can be
It is vented automatically by air bleeding valve under the operating pressure of the setting pressure of overflow valve, enters fuel-displaced without going to close motor
Mouthful, to ensure there is no air in hydraulic oil, the shock and vibration of the system caused by air is present are prevented, the danger of hydraulic system is reduced
It is dangerous.
Brief description of the drawings
Technical scheme in order to illustrate the embodiments of the present invention more clearly, makes required in being described below to embodiment
Accompanying drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the present invention, for
For those of ordinary skill in the art, on the premise of not paying creative work, other can also be obtained according to these accompanying drawings
Accompanying drawing.
Fig. 1 is the schematic diagram of hydraulic system provided in an embodiment of the present invention；
Fig. 2 is the schematic diagram of main control valve group provided in an embodiment of the present invention；
Fig. 3 is the schematic diagram of motor balancing valve group provided in an embodiment of the present invention；
Fig. 4 is the schematic diagram of double-speed motor control valve group provided in an embodiment of the present invention.
Embodiment
To make the object, technical solutions and advantages of the present invention clearer, below in conjunction with accompanying drawing to embodiment party of the present invention
Formula is described in further detail.
Embodiment
The embodiments of the invention provide a kind of hydraulic system of rack-and-pinion lifting device, the hydraulic system includes：Hydraulic pressure
Pump group part 1, main control valve group 2, multiple motor control components 3 and multiple air bleeding valves 4 positioned at pipeline peak, each motor control
Component 3 processed includes：Motor balancing valve group and double-speed motor control valve group, main control valve group 2 include：2/2-way ratio commutates
Valve 5, the first inserted valve 6, the second inserted valve 7, the 3rd inserted valve 8, the 4th inserted valve 9, the 5th inserted valve 10, the first two four-ways
Solenoid directional control valve 11, the second two four-way electromagnetic reversing valves 12,2/2-way reversal valve 21 and overflow valves 22.
The oil-out of hydraulic pump module 1 is connected with the oil inlet of 2/2-way proportional reversing valve 5, the commutation of 2/2-way ratio
The oil-out of valve 5 A mouths respectively with the first inserted valve 6, the A mouths of the second inserted valve 7, the first two four-way electromagnetic reversing valves 11
P mouthfuls connect with the P mouths of the second two four-way electromagnetic reversing valves 12, and the A mouths of the first two four-way electromagnetic reversing valves 11 are respectively with
The X mouths of two inserted valves 7 are connected with the X mouths of the 3rd inserted valve 8, and the A mouths of the second two four-way electromagnetic reversing valves 12 are respectively with first
The X mouths of inserted valve 6 are connected with the X mouths of the 4th inserted valve 9, and the B mouths of the first inserted valve 6 are connected with the B mouths of the 3rd inserted valve 8, the
The A mouths of three inserted valves 8 are connected with the A mouths of the 5th inserted valve 10 and the A mouths of the 4th inserted valve 9 respectively, the B mouths of the 4th inserted valve 9
Connected with the B mouths of the second inserted valve 7, the T mouths of the first two four-way electromagnetic reversing valves 11 and the second two four-way electromagnetic reversing valves
Connected respectively with the B mouths of the 5th inserted valve 10 and the X mouths of the 5th inserted valve 10 after 12 T mouths connection, the B mouths of the 5th inserted valve 10
Connected after being connected with the X mouths of the 5th inserted valve 10 with fuel tank.
The oil inlet of 2/2-way reversal valve 21 is connected with the oil-out of 2/2-way proportional reversing valve 5, and 2/2-way is changed
Connected to the oil-out of valve 21 with the oil inlet of overflow valve 22, the oil-out of overflow valve 22 is connected with fuel tank, the volume of overflow valve 22
Constant-pressure is less than brake a Opening pressure.
A mouths, the A mouths and air bleeding valve of double-speed motor control valve group of the B mouths of second inserted valve 7 respectively with motor balancing valve group
4 connections, B mouths, the B mouths and air bleeding valve 4 of double-speed motor control valve group of the B mouths of the 3rd inserted valve 8 respectively with motor balancing valve group
Connection.In addition, the B mouths of the 3rd inserted valve 8 and the B mouths of the second inserted valve 7 are connected with second pressure sensor 37 respectively.
Specifically, motor balancing valve group can include：Balanced valve 13, the A1 mouths of balanced valve 13 and the B mouths of the second inserted valve 7
Connection, the B1 mouths of balanced valve 13 are connected with the B mouths of the 3rd inserted valve 8.The setting pressure of the balanced valve 13 must assure that brake a
Open and completed before the unlatching of balanced valve 13.In the present embodiment, the rated pressure of balanced valve 13 can be 31MPa.
Further, motor balancing valve group can also include：First shuttle valve 14 and first pressure sensor 15, the first shuttle valve
14 A mouths are connected with the A2 mouths of balanced valve 13, and the B mouths of the first shuttle valve 14 are connected with the B2 mouths of balanced valve 13, the C of the first shuttle valve 14
Mouth is connected with first pressure sensor 15；Double-speed motor control valve group can include：Variable oil cylinder 16, the and of motor stroking mechanism 17
First two-bit triplet solenoid directional control valve 18, the B mouths of the B mouths of the first two-bit triplet solenoid directional control valve 18 respectively with the 3rd inserted valve 8
Connected with the B mouths of the second inserted valve 7, the C mouths of the first two-bit triplet solenoid directional control valve 18 connect with the rod chamber 16b of variable oil cylinder 16
Logical, the rodless cavity 16a of variable oil cylinder 16 is connected with the B mouths of the first two-bit triplet solenoid directional control valve 18, the first two-bit triplet electromagnetism
The A mouths of reversal valve 18 are connected with fuel tank, and piston rod 16c and the motor stroking mechanism 17 of variable oil cylinder 16 are connected.First shuttle
Hydraulic oil is handed on first pressure sensor 15 by the A mouths of valve 14 and B mouthfuls by the C oral instructions of the first shuttle valve 14 respectively, by the
One pressure sensor 15 can compare the A mouths of the first shuttle valve 14 and the pressure of B mouthfuls of both sides.In addition, variable oil cylinder 16, motor variable
The two-bit triplet solenoid directional control valve 18 of mechanism 17 and first belongs to double-speed motor control valve group, and double-speed motor control valve group can realize horse
Up to the switching of b huge discharge and small displacement, motor b can be divided into two kinds of operating modes of low-speed heave-load and high speed light loading, be carried by rack-and-pinion
Rise the weight of the load cell monitoring load of device.When load is heavy duty, the first two-bit triplet solenoid directional control valve 18 must not
Electricity, hydraulic oil is flowed into the rod chamber 16b of variable oil cylinder 16, and hydraulic oil can promote the piston driving variable oil cylinder of variable oil cylinder 16
16 piston rod 16c is moved to the rodless cavity 16a directions of variable oil cylinder 16, the hydraulic oil in the rodless cavity 16a of variable oil cylinder 16
The A mouths of the first two-bit triplet solenoid directional control valve 18 are flow to by the C mouths of the first two-bit triplet solenoid directional control valve 18, and are finally flow to
In fuel tank, now, motor stroking mechanism 17 makes motor b be in huge discharge state；When load is underloading, first pressure sensor
15 the first two-bit triplet solenoid directional control valves 18 of control obtain electric, and hydraulic oil is flowed into by the B mouths of the first two-bit triplet solenoid directional control valve 18,
The C mouths outflow of first two-bit triplet solenoid directional control valve 18, and the rodless cavity 16a of variable oil cylinder 16 is flowed into, due to variable oil cylinder 16
Rodless cavity 16a in hydraulic oil active area be more than variable oil cylinder 16 rod chamber 16b in hydraulic oil active area, hydraulic pressure
Oil can promote the piston rod 16c of the piston driving variable oil cylinder 16 of variable oil cylinder 16 to the rod chamber 16b directions of variable oil cylinder 16
Mobile, the hydraulic oil in the rod chamber 16b of variable oil cylinder 16 flows back to the B mouths of the first two-bit triplet solenoid directional control valve 18 again, is formed
Circulating oil path so that hydraulic oil can be recycled, in addition, motor stroking mechanism 17 makes motor b be in small displacement state.Motor
B big small displacement can be set according to system-computed.
Further, double-speed motor control valve group can also include the first check valve 19 and the second check valve 20, and second is single
The B mouths of oil inlet and the second inserted valve 7 to valve 20 are connected, oil-out and the two-bit triplet solenoid directional control valve of the second check valve 20
18 C mouths connection, the oil inlet of the first check valve 19 connects with the B mouths of the 3rd inserted valve 8, the oil-out of the first check valve 19 and
The C mouths connection of two-bit triplet solenoid directional control valve 18.First check valve 19 and the second check valve 20 are used to prevent oil return, and ensure stream
Hydraulic oil through the first check valve 19 and the second check valve 20 is slow and smoothly flows out.
Further, the motor balancing valve group can also include：Second shuttle valve 23, the second two-bit triplet reversal valve 24 and system
Dynamic device pressure sensor 24a (see Fig. 3), the A mouths of second shuttle valve 23 are connected with the A1 mouths of balanced valve 13, the second shuttle valve 23
B mouthfuls are connected with the B1 mouths of balanced valve 13, and the C mouths of the second shuttle valve 23 are connected with the A mouths of the second two-bit triplet reversal valve 24, second liang
The position B mouths of three-way diverter valve 24 are connected with brake a R mouths, and brake pressure sensor 24a is connected to the second two-bit triplet and changed
To on the B mouths of valve 24, the C mouths of the second two-bit triplet reversal valve 24 are connected with fuel tank.Second shuttle valve 23 and the second two-bit triplet are changed
It is used for control brake a to valve 24, after the second two-bit triplet reversal valve 24 must be electric, the hydraulic oil on brake a is vented so that
Brake can not be opened.Wherein, brake pressure sensor 24a is used for the pressure for monitoring the hydraulic oil for flowing through brake.
Further, as shown in figure 1, the hydraulic system can also include brake control assembly, brake control assembly
It can include：3rd check valve 25, the oil inlet of the 3rd check valve 25 connects with brake a R mouths, and the 3rd check valve 25 goes out
Hydraulic fluid port is connected with fuel tank.3rd check valve 25 can increase the back pressure of brake a oil return circuits, make brake a oil return circuit
Can slowly it close.
Further, the main control valve group 2 can also include：Pressure compensator 26, the oil inlet of pressure compensator 26
Connected with the oil inlet of 2/2-way reversal valve 21, the oil-out of pressure compensator 26 is connected with the oil-out of overflow valve 22.
In the present embodiment, the rated pressure of the pressure compensator 26 can be 19MPa.
Further, the main control valve group 2 can also include：Pressure compensation overflow valve 27, pressure compensation overflow valve 27
Pilot port connected with the oil inlet of pressure compensator 26, the commutation of the oil inlet and 2/2-way ratio of pressure compensation overflow valve 27
Valve 5 is connected, and the oil-out of pressure compensation overflow valve 27 is connected with fuel tank.In the present embodiment, the pressure compensation overflow valve 27
Rated pressure can be 1MPa.
Further, the motor balancing valve group can also include：First damping hole 13a and the second damping hole 13b, the first resistance
Buddhist nun hole 13a and the second damping hole 13b are opened on the control oil circuit of balanced valve 13 respectively, specifically, and the first damping hole 13a's enters
Hydraulic fluid port is connected with the B1 mouths of balanced valve 13, and the first damping hole 13a oil-out is connected with the C1 mouths (control port) of balanced valve 13,
Second damping hole 13b oil inlet is connected with the A1 mouths of balanced valve 13, the second damping hole 13b oil-out and the C2 of balanced valve 13
Mouth (control port) connection.First damping hole 13a and the second damping hole 13b can ensure to close in balanced valve 13 and motor b stops
After motion, brake a is turned off, and reduces the impact to hydraulic system.First damping hole 13a and the second damping hole 13b can be
Detachable damping hole, when there is situation about blocking, can pull down replacing.Meanwhile, the first damping hole 13a and the second damping hole 13b
The stability of balanced valve 13 can be increased, under a load drop when, temperature it is higher when and load it is larger when, reduce balanced valve 23 occur
Fluctuation, it is to avoid the performance of influence hydraulic system.In addition, the first damping hole 13a and the second damping hole 13b aperture can be
0.4mm。
Specifically, hydraulic pump module 1 includes being mounted on the 4th on multiple hydraulic pumps 28, the oil-out of each hydraulic pump 28
Check valve 29, the oil inlet of the 4th check valve 29 is connected with the oil-out of hydraulic pump 28, the oil-out of each 4th check valve 29
Oil inlet with 2/2-way proportional reversing valve 5 is connected.Multiple hydraulic pumps 28 can provide abundant hydraulic pressure for hydraulic system
Oil, in the present embodiment, hydraulic pump 28 can be 12, and every three hydraulic pumps 28 are one group and driven by a motor.The
Four check valves 29 can prevent hydraulic oil oil return.
Further, the hydraulic pump module 1 can also include elastic compensator 32, and elastic compensator 32 is arranged on hydraulic pump
Between 28 oil inlet and fuel tank.Specifically, one group of hydraulic pump 28 can share an elastic compensator 32.
In addition, can also set butterfly valve 33 and filter 34 between elastic compensator 32 and fuel tank, the butterfly valve 33 is used for
The closing and unlatching of control port, the filter 34 are used to filter the hydraulic oil flowed through in filter 34.
Specifically, main control valve group 2 also includes：The hand-operated direction valve 31 of first manual reversal valve 30 and second, second is manual
The oil inlet of reversal valve 31 is connected with the oil-out of hydraulic pump 28, the oil-out and the 3rd inserted valve 8 of the second hand-operated direction valve 31
B mouths connections, the oil inlet of first manual reversal valve 30 connects with the oil-out of hydraulic pump 28, and first manual reversal valve 30 goes out
Hydraulic fluid port is connected with the B mouths of the second inserted valve 7.Because the flow of the hydraulic system is larger, therefore inserted valve is used, still, when first
When two four-way electromagnetic reversing valves 11 and the second two four-way electromagnetic reversing valves 12 break down, and it can not be repaiied in the short time
It is multiple, first manual reversal valve 30 can be first operated, rack-and-pinion lifting device is raised up, is inserted after lower drilling rod, then operate second
Hand-operated direction valve 31, rack-and-pinion lifting device is transferred to safe position, and the first two four-way electromagnetics are then overhauled again and are changed
To valve 11 and the second two four-way electromagnetic reversing valves 12.
In addition, being provided with the first stop valve 35 at the B mouths of the second inserted valve 7, set at the B mouths of the 3rd inserted valve 8
Have the second stop valve 36, the oil inlet of the first stop valve 35 is connected with the B mouths of the second inserted valve 7, the first stop valve 35 it is fuel-displaced
Mouth is connected with the A mouths of motor balancing valve group, and the oil inlet of the second stop valve 36 is connected with the B mouths of the 3rd inserted valve 8, the second cut-off
The oil-out of valve 36 is connected with the B mouths of motor balancing valve group, and the first stop valve 35 and the second stop valve 36 are used to quick blocking
Oil circuit.
The work that following is a brief introduction of the hydraulic system of rack-and-pinion lifting device provided in an embodiment of the present invention is former
Reason：
Hydraulic pump module 1 provides hydraulic oil for hydraulic system, and hydraulic oil is flowed into by 2/2-way proportional reversing valve 5, when
When the first two four-way electromagnetic reversing valves 11 are powered, hydraulic oil by the first two four-way electromagnetic reversing valves 11 the inflow of P mouths, by the
The A mouths outflow of one or two four-way electromagnetic reversing valve 11, hydraulic oil separately flows into the X mouths and the 3rd inserted valve 8 of the second inserted valve 7
X mouthfuls, now, the second inserted valve 7 is opened, and hydraulic oil flows into B mouthfuls by the A mouths of the second inserted valve 7, and hydraulic oil separately flows into motor
Balance A mouths, the A mouths and air bleeding valve 4 of double-speed motor control valve group of valve group；When the second two four-way electromagnetic reversing valves 12 are powered
When, hydraulic oil is flowed into by the P mouths of the second two four-way electromagnetic reversing valves 12, by the A mouths of the second two four-way electromagnetic reversing valves 12
Outflow, hydraulic oil separately flows into the X mouths of the first inserted valve 6 and the X mouths of the 4th inserted valve 9, and now, the first inserted valve 6 is opened,
Hydraulic oil flows into B mouthfuls by the A mouths of the first inserted valve 6, and hydraulic oil separately flows into the B mouths of motor balancing valve group, double-speed motor control
The B mouths and air bleeding valve 4 of valve group.When before hydraulic system life's work, it is necessary to hydraulic system be exhausted, to ensure in hydraulic oil
There is no air, prevent the shock and vibration of the system caused by air is present, reduce the danger of hydraulic system.During exhaust, two
Two electric change valves 21 obtain electric, in the present embodiment, and the setting pressure of the overflow valve 22 can be 1MPa, and open brake
A about needs 2MPa or so, and now the pressure of hydraulic system can not open brake a, and motor b will not be rotated, and hydraulic system can be
It is exhausted under 1MPa operating pressure by air bleeding valve 4, the oil inlet and outlet without removing closing motor a.
The present invention implements the hydraulic system of the rack-and-pinion lifting device of offer, before hydraulic system life's work, makes
2/2-way solenoid directional control valve obtains electric, and the rated pressure of overflow valve is less than the Opening pressure of brake so that hydraulic oil can not be beaten
Open brake, and motor will not rotate, hydraulic system can be entered under the operating pressure of the setting pressure of overflow valve by air bleeding valve
The automatic exhaust of row, without going the oil inlet and outlet for closing motor, to ensure not having air in hydraulic oil, prevent because air is present
The shock and vibration of system are caused, the danger of hydraulic system is reduced.
The foregoing is only presently preferred embodiments of the present invention, be not intended to limit the invention, it is all the present invention spirit and
Within principle, any modification, equivalent substitution and improvements made etc. should be included in the scope of the protection.
Claims (10)
1. a kind of hydraulic system of rack-and-pinion lifting device, it is characterised in that the hydraulic system includes：Hydraulic pump module
(1), main control valve group (2), multiple motor control components (3) and multiple air bleeding valves (4) positioned at pipeline peak, it is each described
Motor control component (3) includes：Motor balancing valve group and double-speed motor control valve group, the main control valve group (2) include：Two
The logical proportional reversing valves (5) in position two, the first inserted valve (6), the second inserted valve (7), the 3rd inserted valve (8), the 4th inserted valve (9),
5th inserted valve (10), the first two four-way electromagnetic reversing valves (11), the second two four-way electromagnetic reversing valves (12), 2/2-ways
Reversal valve (21) and overflow valve (22)；
The oil-out of the hydraulic pump module (1) is connected with the oil inlet of the 2/2-way proportional reversing valve (5), 2/2-way
It is the oil-out of proportional reversing valve (5) A mouths respectively with first inserted valve (6), the A mouths of second inserted valve (7), described
The P mouths of the first two four-way electromagnetic reversing valves (11) are connected with the P mouths of the second two four-way electromagnetic reversing valves (12), described
The X mouths and the 3rd inserted valve of the A mouths of first two four-way electromagnetic reversing valves (11) respectively with second inserted valve (7)
(8) X mouths connection, the X mouths of the A mouths of the second two four-way electromagnetic reversing valves (12) respectively with first inserted valve (6)
Connected with the X mouths of the 4th inserted valve (9), the B mouths of first inserted valve (6) connect with the B mouths of the 3rd inserted valve (8)
It is logical, the A mouths and the A of the 4th inserted valve (9) of the A mouths of the 3rd inserted valve (8) respectively with the 5th inserted valve (10)
Mouthful connection, B mouths of the 4th inserted valve (9) connect with the B mouths of second inserted valve (7), the first two four energizations
Inserted respectively with the described 5th after the T mouths connection of the T mouths of magnetic reversal valve (11) and the second two four-way electromagnetic reversing valves (12)
The B mouths of dress valve (10) are connected with the X mouths of the 5th inserted valve (10), the B mouths and the described 5th of the 5th inserted valve (10)
Connected after the X mouths connection of inserted valve (10) with fuel tank；
The oil inlet of the 2/2-way reversal valve (21) is connected with the oil-out of the 2/2-way proportional reversing valve (5), institute
The oil-out for stating 2/2-way reversal valve (21) is connected with the oil inlet of the overflow valve (22), the overflow valve (22) it is fuel-displaced
Mouth is connected with the fuel tank, and the rated pressure of the overflow valve (22) is less than the Opening pressure of brake (a)；
A mouths, the A of the double-speed motor control valve group of the B mouths of second inserted valve (7) respectively with the motor balancing valve group
Mouthful connected with the air bleeding valve (4), it is the B mouths of the 3rd inserted valve (8) B mouths respectively with the motor balancing valve group, described
The B mouths of double-speed motor control valve group are connected with the air bleeding valve (4).
2. hydraulic system according to claim 1, it is characterised in that the motor balancing valve group includes：Balanced valve (13),
The A1 mouths of the balanced valve (13) are connected with the B mouths of second inserted valve (7), the B1 mouths of the balanced valve (13) and described the
The B mouths connection of three inserted valves (8).
3. hydraulic system according to claim 2, it is characterised in that the motor balancing valve group also includes：First shuttle valve
(14) and first pressure sensor (15), the A mouths of first shuttle valve (14) are connected with the A2 mouths of the balanced valve (13), described
The B mouths of first shuttle valve (14) are connected with the B2 mouths of the balanced valve (13), the C mouths of first shuttle valve (14) and the described first pressure
Force snesor (15) is connected；The double-speed motor control valve group includes：Variable oil cylinder (16), motor stroking mechanism (17) and first
Two-bit triplet solenoid directional control valve (18), the B mouths of the first two-bit triplet solenoid directional control valve (18) are inserted with the described 3rd respectively
The B mouths of valve (8) are connected with the B mouths of second inserted valve (7), the C mouths of the first two-bit triplet solenoid directional control valve (18) with
Rod chamber (16b) connection of the variable oil cylinder (16), the rodless cavity (16a) of the variable oil cylinder (16) with described the first two
The B mouths connection of three-way solenoid valve (18), A mouths and the fuel tank of the first two-bit triplet solenoid directional control valve (18) connect
Logical, the piston rod (16c) of the variable oil cylinder (16) is connected with the motor stroking mechanism (17).
4. hydraulic system according to claim 3, it is characterised in that it is single that the double-speed motor control valve group also includes first
To valve (19) and the second check valve (20), the oil inlet of second check valve (20) and the B mouths of second inserted valve (7) connect
Logical, the oil-out of second check valve (20) is connected with the C mouths of the two-bit triplet solenoid directional control valve (18), and described first is single
Connected to the oil inlet of valve (19) with the B mouths of the 3rd inserted valve (8), the oil-out of first check valve (19) with it is described
The C mouths connection of two-bit triplet solenoid directional control valve (18).
5. hydraulic system according to claim 2, it is characterised in that the motor balancing valve group also includes：Second shuttle valve
(23), the second two-bit triplet reversal valve (24) and brake pressure sensor (24a), the A mouths of second shuttle valve (23) and institute
The A1 mouths connection of balanced valve (13) is stated, the B mouths of second shuttle valve (23) connect with the B1 mouths of the balanced valve (13), described the
The C mouths of two shuttle valves (23) are connected with the A mouths of the second two-bit triplet reversal valve (24), the second two-bit triplet reversal valve
(24) B mouths are connected with the R mouths of the brake (a), and the brake pressure sensor (24a) is connected to described the second two
On the B mouths of three-way diverter valve (24), the C mouths of the second two-bit triplet reversal valve (24) are connected with the fuel tank.
6. hydraulic system according to claim 5, it is characterised in that the hydraulic system also includes brake control group
Part, the brake control assembly includes：3rd check valve (25), oil inlet and the braking of the 3rd check valve (25)
The R mouths connection of device (a), the oil-out of the 3rd check valve (25) is connected with the fuel tank.
7. hydraulic system according to claim 6, it is characterised in that the motor balancing valve group also includes：First damping
Hole (13a) and the second damping hole (13b), first damping hole (13a) and second damping hole (13b) are opened in institute respectively
On the control oil circuit for stating balanced valve (13).
8. hydraulic system according to claim 1, it is characterised in that the hydraulic pump module includes multiple hydraulic pumps
(28) the 4th check valve (29), is mounted on the oil-out of each hydraulic pump (28), the 4th check valve (29)
Oil inlet is connected with the oil-out of the hydraulic pump (28), the oil-out of each 4th check valve (29) with described two
The oil inlet connection of two logical proportional reversing valves (5).
9. hydraulic system according to claim 8, it is characterised in that the hydraulic pump module (1) also includes elastic compensating
Device (32), the elastic compensator (32) is arranged between the oil inlet of the hydraulic pump (28) and the fuel tank.
10. hydraulic system according to claim 1, it is characterised in that the main control valve group (2) also includes：It is first-hand
Dynamic reversal valve (30) and the second hand-operated direction valve (31), oil inlet and the hydraulic pressure pump group of the first manual reversal valve (30)
The oil-out connection of part (1), the oil-out of the first manual reversal valve (30) is connected with the B mouths of the 3rd inserted valve (8),
The oil inlet of second hand-operated direction valve (31) is connected with the oil-out of the hydraulic pump module (1), and the second-hand moves
Connected to the oil-out of valve (31) with the B mouths of second inserted valve (7).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510974458.1A CN105465077B (en) | 2015-12-23 | 2015-12-23 | A kind of hydraulic system of rack-and-pinion lifting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510974458.1A CN105465077B (en) | 2015-12-23 | 2015-12-23 | A kind of hydraulic system of rack-and-pinion lifting device |
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| CN105465077A CN105465077A (en) | 2016-04-06 |
| CN105465077B true CN105465077B (en) | 2017-09-01 |
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| CN201510974458.1A Active CN105465077B (en) | 2015-12-23 | 2015-12-23 | A kind of hydraulic system of rack-and-pinion lifting device |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105951703B (en) * | 2016-05-03 | 2017-12-01 | 武汉船用机械有限责任公司 | A kind of hydraulic system of gear-rack type lifter structure |
| CN110670451B (en) * | 2019-10-22 | 2024-05-24 | 柳工无锡路面机械有限公司 | Reversing valve group for open type vibration system of road roller |
| CN111608982B (en) * | 2020-04-07 | 2023-01-17 | 武汉船用机械有限责任公司 | Hydraulic system of lifting platform |
| CN111677712B (en) * | 2020-07-21 | 2022-08-16 | 徐州徐工随车起重机有限公司 | Rotary buffer valve device, speed reducer and using method of speed reducer |
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