CN205715009U - The circuit apparatus for hydraulic of well control device IBOP system delay off-load - Google Patents
The circuit apparatus for hydraulic of well control device IBOP system delay off-load Download PDFInfo
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- CN205715009U CN205715009U CN201620428505.2U CN201620428505U CN205715009U CN 205715009 U CN205715009 U CN 205715009U CN 201620428505 U CN201620428505 U CN 201620428505U CN 205715009 U CN205715009 U CN 205715009U
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Abstract
This utility model provides the circuit apparatus for hydraulic of a kind of well control device IBOP system delay off-load, including oil cylinder, major loop and pressure release loop, described major loop includes the first fluid pressure line that the rodless cavity with oil cylinder connects and the second fluid pressure line connected with the rod chamber of oil cylinder, described major loop can promote the piston reciprocating of oil cylinder to move by the first fluid pressure line and the second fluid pressure line, and described pressure release loop is connected with the first fluid pressure line and the second fluid pressure line；When the piston of oil cylinder moves to extreme position, described pressure release loop connects with oil cylinder；Described pressure release loop can reduce in-oil cylinder hydraulic pressure.This utility model can effectively realize the unloading of IBOP oil cylinder, it is to avoid the fatigue failure of IBOP mechanical parts.
Description
Technical field
This utility model relates to hydraulic system Unloading Technology field, and particularly a kind of well control device IBOP system delay unloads
The circuit apparatus for hydraulic of lotus.
Background technology
Top drive drilling system, is called for short " well control device ", instead of traditional drillng operation mode already, greatly
Improve efficiency and the safety of drillng operation, be the indispensable equipment of current high standard and highly difficult drillng operation.
Hydraulic system is the important component part of well control device, and some auxiliary movements of well control device are all to pass through hydraulic pressure system
Unite.Being divided by function, hydraulic system includes back-up tong system, IBOP (Internal Blowout
Prevent) position system, brake system, rotary system, fastening system and brake system etc. in system, inclination.Its
In, IBOP system is to control the mechanism assembly of IBOP valve switch, and it includes mechanical actuating mechanism and hydraulic control system
System two parts, are to process well kick, the key of gas blowout accident and core.
The mechanical actuating mechanism of IBOP system mainly has pinion and-rack and two kinds of structures of crank rotary pin, described machinery
The control system performing structure currently mainly has two kinds of control modes, and one is that the accumulator of China high (Varco) coordinates
The time delay pressure relief system of choke valve, a kind of be that north Shi Wei represents, non-Varco formula actuator is long-term with pressure performs system
System.Wherein, the life-span of IBOP mechanical actuating mechanism is had a certain impact by non-Varco formula long-term band pressure actuator,
Owing to mechanical structured member is chronically under the effect of high-voltage oil cylinder, easily cause the fatigue failure of mechanical parts.Meanwhile, for
Avoid the IBOP ball valve core to be chronically under the effect of high-voltage oil cylinder, Exact calculation and the row controlling IBOP oil cylinder
Journey, thus cause being difficult to judging whether the on off state of IBOP has reached the switching requirements suggested by IBOP ball valve producer.
But, although Varco formula accumulator coordinates the pressure relief system of choke valve can well alleviate the inefficacy of actuator mechanical parts
Problem, but accumulator nitrogen charging pressure and choke valve opening size, needing more accurate calculating and coordinate could be real
Existing more satisfactory delay effect, simultaneously because the opening of choke valve is smaller, is susceptible to block blocking phenomenon, makes
Delay effect lost efficacy, and reliability is under some influence.
Utility model content
For the control mode of above-mentioned existing IBOP system easily cause mechanical parts fatigue failure or cannot effective delay
The problem of off-load, the utility model proposes the circuit apparatus for hydraulic of a kind of well control device IBOP system delay off-load,
Can effectively realize the unloading of IBOP oil cylinder, it is to avoid the fatigue failure of IBOP mechanical parts.
This utility model solves its technical problem and be the technical scheme is that a kind of well control device IBOP system delay
The circuit apparatus for hydraulic of off-load, including oil cylinder, major loop and pressure release loop, described major loop include with oil cylinder without bar
First fluid pressure line of chamber connection and the second fluid pressure line of connecting with the rod chamber of oil cylinder, described major loop can pass through
First fluid pressure line and the second fluid pressure line promote the piston reciprocating of oil cylinder to move, described pressure release loop and the first hydraulic tube
Road and the second fluid pressure line connect；When the piston of oil cylinder moves to extreme position, described pressure release loop connects with oil cylinder,
Described pressure release loop can reduce in-oil cylinder hydraulic pressure.
Described pressure release loop includes shuttle valve, the first reversal valve and the first overflow valve being sequentially connected with, and described pressure release loop leads to
Cross shuttle valve connection oil cylinder.
Shuttle valve includes two oil-ins and an oil-out, and an oil-in in two oil-ins of shuttle valve passes through the 3rd
Fluid pressure line and the connection of the first fluid pressure line, another oil-in in two oil-ins of shuttle valve passes through the 4th hydraulic tube
Road connects with the second fluid pressure line.
Described first reversal valve is bi-bit bi-pass solenoid directional control valve, and bi-bit bi-pass solenoid directional control valve contains oil-in and fuel-displaced
Mouthful, described first overflow valve is direct acting type overflow valve, the oil-in of bi-bit bi-pass solenoid directional control valve and the oil-out of shuttle valve
Connection, the oil-out of bi-bit bi-pass solenoid directional control valve connects with the oil-in of direct acting type overflow valve.
Described first reversal valve is two-position four-way solenoid directional control valve, and two-position four-way solenoid directional control valve contains oil-in, oil return
Mouth, the first outlet and the second outlet, described first overflow valve is direct acting type overflow valve, the oil-out of shuttle valve and two four
The oil-in connection of electric change valve, the oil return opening of two-position four-way solenoid directional control valve and the oil-out of direct acting type overflow valve
Connection, the first outlet of two-position four-way solenoid directional control valve connects with the oil-in of direct acting type overflow valve.
Described major loop includes air relief valve, the second reversal valve and dual hydraulic control one-way valve, the dual hydraulic control one-way valve being sequentially connected with
Containing two outlets and two entrances, an outlet in two outlets of dual hydraulic control one-way valve is by the first fluid pressure line
Connect with the rodless cavity of oil cylinder, another outlet in two of dual hydraulic control one-way valve outlets by the second fluid pressure line with
The rod chamber connection of oil cylinder.
Second reversal valve is three-position four-way electromagnetic directional valve, and the second reversal valve contains oil-in, oil return opening, the first outlet
With the second outlet, the first outlet of the second reversal valve connects with an entrance in two entrances of dual hydraulic control one-way valve,
Second outlet of the second reversal valve connects with another entrance in two entrances of dual hydraulic control one-way valve.
Air relief valve for decompression overflow valve, air relief valve contains oil-in, oil-out and drain tap, the oil-out of air relief valve with
The oil-in connection of the second reversal valve.
The oil return opening of the second reversal valve connects low-pressure oil return pipe line, the drain tap of air relief valve and described low-pressure oil return pipe line
Connection, the oil-in of air relief valve connects high pressure feed line.
Being provided with the first pressure detecting mouth on the first fluid pressure line between described pressure release loop and oil cylinder, described pressure release is returned
The second pressure detecting mouth it is provided with on the second fluid pressure line between road and oil cylinder.
The beneficial effects of the utility model are: by arranging described pressure release loop, the piston at oil cylinder moves to limit position
When putting, make in-oil cylinder hydraulic oil flow into the described pressure release loop being connected with oil cylinder, and thus reduce in-oil cylinder liquid
Pressure, effectively realizes the unloading of IBOP oil cylinder, it is to avoid the fatigue failure of IBOP mechanical parts；Meanwhile, IBOP spool institute
The hydraulic pressure born also decreases, it is to avoid IBOP spool is affected by high pressure for a long time, also protects IBOP spool.
The circuit apparatus for hydraulic simple in construction of well control device IBOP system delay off-load of the present utility model, unloading effect is obvious,
Easily operation, failture evacuation is convenient, and does not affect system worked well, be suitable for various multichannel high pressure unloading and
Do not affect the hydraulic circuit of main control hydraulic system.
Accompanying drawing explanation
Fig. 1 is the structural representation of major loop of the present utility model；
Fig. 2 is the structural representation of an embodiment in pressure release loop of the present utility model；
Fig. 3 is the structural representation of an embodiment of the present utility model；
Fig. 4 is the structural representation of another embodiment in pressure release loop of the present utility model；
Fig. 5 is the structural representation of another embodiment of the present utility model.
Description of reference numerals:
1, air relief valve, the 2, second reversal valve, 3, dual hydraulic control one-way valve, 4, shuttle valve, 5, bi-bit bi-pass electromagnetism changes
To valve, 51, two-position four-way solenoid directional control valve, 6, direct acting type overflow valve, 7, oil cylinder, 8, fuel tank, 81, first
Fuel tank, the 91, first fluid pressure line, the 92, second fluid pressure line, the 93, the 3rd fluid pressure line, the 94, the 4th hydraulic tube
Road, the 101, first pressure detecting mouth, the 102, second pressure detecting mouth, the 103, the 3rd pressure detecting mouth.
Detailed description of the invention
In order to technical characteristic of the present utility model, purpose and effect are more clearly understood from, now comparison accompanying drawing explanation
Detailed description of the invention of the present utility model.
As shown in Figures 1 to 5, the utility model proposes the hydraulic pressure of a kind of well control device IBOP system delay off-load
Loop apparatus, including oil cylinder 7, major loop and pressure release loop, described major loop includes connecting with the rodless cavity of oil cylinder 7
The first fluid pressure line 91 and the second fluid pressure line 92 of connecting of the rod chamber with oil cylinder 7, described major loop can lead to
Cross the first fluid pressure line 91 and the second fluid pressure line 92 promote the piston reciprocating of oil cylinder 7 to move, described pressure release loop with
First fluid pressure line 91 and the second fluid pressure line 92 connect；When the piston of oil cylinder 7 moves to extreme position, described
Pressure release loop connects with oil cylinder 7, and described pressure release loop can reduce the hydraulic pressure in oil cylinder 7.
The circuit apparatus for hydraulic of well control device IBOP system delay off-load of the present utility model returns by arranging described pressure release
Road, when the piston of oil cylinder 7 moves to extreme position, makes the hydraulic oil (such as, 12MPa) in oil cylinder 7 flow into
The described pressure release loop being connected with oil cylinder 7, and thus reduce the hydraulic pressure in oil cylinder 7, effectively realize IBOP oil cylinder
The unloading of 7, it is to avoid the fatigue failure of IBOP mechanical parts；Meanwhile, the hydraulic pressure that IBOP spool is born also decreases,
Avoid IBOP spool to be affected by high pressure for a long time, also protect IBOP spool.Return at hydraulic pressure of the present utility model
In the device of road, the actuator of the piston rod stretchy IBOP spool (not shown) of oil cylinder 7 is moved.When described
When major loop is by promoting the piston reciprocating of oil cylinder 7 to move, the piston of oil cylinder 7 can promote the piston rod of oil cylinder 7 and draw
Dynamic IBOP spool moves back and forth.When the piston of oil cylinder 7 is moved to extreme position in the effect of described major loop
Time, IBOP spool close or open, described major loop interrupt, the pressure meeting in the rodless cavity of oil cylinder 7 and rod chamber
It is locked in the described major loop of part that oil cylinder 7 connects and the part institute connected with described oil cylinder 7 with described oil cylinder 7
State in pressure release loop, oil cylinder 7, to oil cylinder 7 oil-feed described major loop and with the oil-feed fluid pressure line of described major loop
The described pressure release loop of connection can be in high pressure conditions；Connect described pressure release loop, the hydraulic oil of oil cylinder 7 can flow into
The described pressure release loop that oil cylinder 7 is connected, the hydraulic pressure in oil cylinder 7 thus reduces, it is achieved the unloading of IBOP oil cylinder 7.
In one preferred embodiment, described pressure release loop include shuttle valve the 4, first reversal valve of being sequentially connected with and
First overflow valve, described pressure release loop connects oil cylinder 7 by shuttle valve 4.Particularly, shuttle valve 4 includes two oil-feeds
Mouth and an oil-out, an oil-in in two oil-ins of shuttle valve 4 passes through the 3rd fluid pressure line 93 and first
Fluid pressure line 91 connects, and another oil-in in two oil-ins of shuttle valve 4 is by the 4th fluid pressure line 94 and the
Two fluid pressure lines 92 connect.Two oil-ins of shuttle valve 4 can not be opened simultaneously, say, that when the two of shuttle valve 4
When an oil-in in individual oil-in is opened, another oil-in in two oil-ins of shuttle valve 4 is closed, otherwise,
An oil-in in two oil-ins of shuttle valve 4 when another oil-in in two oil-ins of shuttle valve 4 is opened
Can close.Therefore, when the rodless cavity of oil cylinder 7 builds the pressure formation hydraulic oil, the hydraulic oil in the rodless cavity of oil cylinder 7 leads to
Cross the first fluid pressure line 91 and the 3rd fluid pressure line 93 enters shuttle valve 4；Otherwise, when the rod chamber of oil cylinder 7 builds the pressure shape
When becoming hydraulic oil, the hydraulic oil in the rod chamber of oil cylinder 7 passes through the second fluid pressure line 92 and the 4th fluid pressure line 94
Enter shuttle valve 4.After the hydraulic oil in oil cylinder 7 enters shuttle valve 4, this hydraulic oil will flow through described first successively and change
To valve and described first overflow valve, and by described first overflow valve blood pressure lowering, the hydraulic pressure in oil cylinder 7 also can thus reduce.
And, it follows that either form hydraulic oil in the rodless cavity of oil cylinder 7 or the rod chamber of oil cylinder 7, described in let out
Push back road and all can reduce the hydraulic pressure in oil cylinder 7, be effectively realized the unloading of IBOP oil cylinder, it is to avoid IBOP mechanical parts
Fatigue failure, protect IBOP spool.
In an embodiment in pressure release loop as shown in Figure 2, for the ease of control described pressure release loop unlatching with
Closing, described first reversal valve selects bi-bit bi-pass solenoid directional control valve 5, the oil-in of bi-bit bi-pass solenoid directional control valve 5
Connecting with the oil-out of shuttle valve 4, described first overflow valve selects direct acting type overflow valve 6, bi-bit bi-pass solenoid directional control valve
5 oil-ins containing oil-in and oil-out, the oil-out of bi-bit bi-pass solenoid directional control valve 5 and direct acting type overflow valve 6
Connection.When the piston reciprocating that described major loop controls oil cylinder 7 moves not up to extreme position, the rodless cavity of oil cylinder 7
With the rod chamber of oil cylinder 7 is low pressure oil (such as 3MPa), make bi-bit bi-pass solenoid directional control valve 5 power-off, two
The electric magnet dead electricity of two electric change valves 5, the oil-in of bi-bit bi-pass solenoid directional control valve 5 changes with bi-bit bi-pass electromagnetism
Disconnecting to the oil-out of valve 5, direct acting type overflow valve 6 disconnects with described major loop, described pressure release loop and oil cylinder 7
Between do not connect, described pressure release loop do not interfere with described major loop control oil cylinder 7 piston move back and forth.And
When the piston of oil cylinder 7 reaches the limit of position, the rodless cavity of oil cylinder 7 or the rod chamber of oil cylinder 7 are hydraulic oil (example
As, 12MPa), bi-bit bi-pass solenoid directional control valve 5 is energized, and described hydraulic oil sequentially passes through each fluid pressure line, shuttle valve 4
With the oil-in of bi-bit bi-pass solenoid directional control valve 5, and flow through direct acting by the oil-out of bi-bit bi-pass solenoid directional control valve 5
Type overflow valve 6 finally flows out, and the hydraulic pressure in oil cylinder 7 thus reduces.In a specific embodiment, Ke Yi
The drain tap of direct acting type overflow valve 6 is communicated with fuel tank 8, makes described hydraulic oil finally be refluxed by direct acting type overflow valve 6
To fuel tank 8.Furthermore, it is also possible to bi-bit bi-pass solenoid directional control valve 5 oil-out and the oil-in of direct acting type overflow valve 6
Between pressure detecting mouth is set, to test the pressure in direct acting type overflow valve 6.As shown in Figure 3 of the present utility model
One embodiment of circuit apparatus for hydraulic, including major loop as shown in Figure 1 with such as the pressure release loop of Fig. 2.
As it is shown on figure 3, be an embodiment of circuit apparatus for hydraulic of the present utility model.Wherein, described major loop is
Major loop as shown in Figure 1, described pressure release loop is an embodiment in pressure release loop as shown in Figure 2.
In another embodiment in pressure release loop as shown in Figure 4, described first reversal valve is that two-position four-way electromagnetism changes
To valve 51, two-position four-way solenoid directional control valve 51 exports B containing oil inlet P, oil return inlet T, the first outlet A and second,
Described first overflow valve is direct acting type overflow valve 6, and the oil-out of shuttle valve 4 enters with two-position four-way solenoid directional control valve 51
Hydraulic fluid port P connects, and the oil return inlet T of two-position four-way solenoid directional control valve 51 connects with the oil-out of direct acting type overflow valve 6,
First outlet A of two-position four-way solenoid directional control valve 51 connects with the oil-in of direct acting type overflow valve 6, two-position four-way electricity
Second outlet B of magnetic reversal valve 51 closes.When the piston reciprocating of described major loop control oil cylinder 7 moves not up to pole
During extreme position, the rodless cavity of oil cylinder 7 and the rod chamber of oil cylinder 7 are low pressure oil (such as 3MPa), make two four
Electric change valve 51 power-off, the electric magnet dead electricity of two-position four-way solenoid directional control valve 51, two-position four-way solenoid directional control valve
The oil inlet P of 51 connects, due to two-position four-way electromagnetic switch with the second outlet B of two-position four-way solenoid directional control valve 51
Second outlet B of valve 51 is closed mode, and therefore, direct acting type overflow valve 6 disconnects with described major loop, described in let out
Pushing back and do not connect between road with oil cylinder 7, the piston that described pressure release loop does not interferes with described major loop control oil cylinder 7 is past
Multiple mobile.And when the piston of oil cylinder 7 reaches the limit of position, the rodless cavity of oil cylinder 7 or the rod chamber of oil cylinder 7 are
Hydraulic oil (such as, 12MPa), two-position four-way solenoid directional control valve 51 is energized, the electricity of two-position four-way solenoid directional control valve 51
Magnet obtains electric, and the first of the oil inlet P connection two-position four-way solenoid directional control valve 51 of two-position four-way solenoid directional control valve 51 goes out
Mouth A, the second outlet B of the oil return inlet T connection two-position four-way solenoid directional control valve 51 of two-position four-way solenoid directional control valve 51,
Described hydraulic oil sequentially passes through each fluid pressure line, shuttle valve 4 and the oil inlet P of two-position four-way solenoid directional control valve 51, and
Flow through direct acting type overflow valve 6 by the first outlet A of two-position four-way solenoid directional control valve 51 finally to flow out, in oil cylinder 7
Hydraulic pressure thus reduce.In a specific embodiment, can be communicated with at the drain tap of direct acting type overflow valve 6
First fuel tank 81, makes described hydraulic oil be finally back in the first fuel tank 81 by direct acting type overflow valve 6, and,
The can also be arranged between first outlet A and the oil-in of direct acting type overflow valve 6 of two-position four-way solenoid directional control valve 51
Three pressure detecting mouths 103, to test the pressure in direct acting type overflow valve 6.
As it is shown in figure 5, be another embodiment of circuit apparatus for hydraulic of the present utility model.Wherein, described major loop
For major loop as shown in Figure 1, described pressure release loop is another embodiment in pressure release loop as shown in Figure 4.
In the specific embodiment shown in Fig. 1, described major loop includes air relief valve the 1, second reversal valve being sequentially connected with
2 and dual hydraulic control one-way valve 3, dual hydraulic control one-way valve 3 containing two outlets and two entrances, dual hydraulic control one-way valve 3
An outlet in two outlets is connected with the rodless cavity of oil cylinder 7 by the first fluid pressure line 91, dual hydraulic control one-way valve
Another outlet in two outlets of 3 is connected with the rod chamber of oil cylinder 7 by the second fluid pressure line 92.Hydraulic Main
The high pressure liquid force feed of pumping system output, through high pressure feed line, after being reduced pressure by air relief valve 1, flows through the second reversal valve
2 and dual hydraulic control one-way valve 3, by the outlet of dual hydraulic control one-way valve 3 through the first fluid pressure line 91 or the second hydraulic pressure
Pipeline 92 enters oil cylinder 7, thus promotes extending and retracting of oil cylinder 7, it is achieved the purpose of switch IBOP ball valve.With
Time, when the stroke of oil cylinder 7 is reached home, when namely the piston of oil cylinder 7 moves to extreme position, described hydraulic pressure
The post-decompression secondary pressure of gate valve 1 of main pump system acts on oil cylinder 7 completely, and is acted on by oil cylinder 7
To spool and the rotary crank thereof of IBOP ball valve, the hydraulic oil simultaneously producing described active force connects through three way cock
To described pressure release loop, described unloader group is made up of shuttle valve 4, described first reversal valve and described first overflow valve,
When reaching to impose a condition, the described first reversal valve commutation of described unloader group, connect described pressure release loop and oil cylinder
7, then the pressure in the high pressure chest (having rodless cavity or the rod chamber of hydraulic oil) of oil cylinder 7, through the 3rd fluid pressure line
93 or the 4th fluid pressure line 94, shuttle valve 4, described first reversal valve and described first overflow valve backflow unloading, it is achieved
The purpose of IBOP oil cylinder 7 discharge degree, thus avoid the fatigue failure of IBOP mechanical parts.
For the ease of controlling the reciprocating motion of oil cylinder 7, selecting the second reversal valve 2 is solenoid directional control valve, and described first
Reversal valve the second reversal valve 2 electric time dead electricity, described major loop promotes the piston reciprocating of oil cylinder 7 to move, described in let out
Push back road to disconnect with oil cylinder 7.Described first reversal valve obtains electric when the second reversal valve 2 dead electricity, i.e. when the work of oil cylinder 7
When plug moves to extreme position, described pressure release loop connects with oil cylinder 7, and described pressure release loop can reduce oil cylinder 7
Interior hydraulic pressure.
In a feasible embodiment, the second reversal valve 2 is three-position four-way electromagnetic directional valve, the second reversal valve 2
Containing oil inlet P, oil return inlet T, first outlet A and second outlet B, the second reversal valve 2 first outlet A with
An entrance connection in two entrances of dual hydraulic control one-way valve 3, the second outlet B and double hydraulic control of the second reversal valve 2
Another entrance connection in two entrances of check valve 3.
Further, air relief valve 1, subtracts containing oil-in, oil-out and drain tap for decompression overflow valve, air relief valve 1
The oil-out of pressure valve 1 and the oil-in connection of the second reversal valve 2.The oil return opening of the second reversal valve 2 connects low pushing back
Oil pipeline, the drain tap of air relief valve 1 connects with described low-pressure oil return pipe line, and the oil-in of air relief valve 1 connects high pressure
Feed line.Meanwhile, the first fluid pressure line 91 between described pressure release loop and oil cylinder 7 is provided with the first pressure
Power detection mouth 101, the second fluid pressure line 92 between described pressure release loop and oil cylinder 7 is provided with the second pressure inspection
Survey mouth 102.
Below as a example by Fig. 3, the hydraulic circuit dress of well control device IBOP system delay off-load of the present utility model is described
Put work process:
As it is shown on figure 3, the high pressure liquid force feed of the 16MPa of hydraulic power source main pump system output is through high pressure feed line, stream
Entering air relief valve 1 (decompression overflow valve), the decompressing effect through air relief valve 1 drops to 12MPa, is then passed through second and changes
To valve 2 (three-position four-way electromagnetic directional valve), the top electric magnet of three-position four-way electromagnetic directional valve obtains electric, promotes spool
Move down, flow into the right branch of dual hydraulic control one-way valve 3 through the hydraulic oil of post-decompression 12MPa through solenoid directional control valve 2,
Open left loop by control port, it is simple to oil return simultaneously；Flow through the hydraulic oil of dual hydraulic control one-way valve 3 through second
Fluid pressure line the 92, the 4th hydraulic line 94 enters shuttle valve 4, promotes the spool of shuttle valve 4 to move to left, and described hydraulic oil arrives
After reaching bi-bit bi-pass solenoid directional control valve 5, form blocking pressurize, can reach 12MPa；Flow through double hydraulic control list simultaneously
Flow into oil cylinder 7 to the hydraulic oil of valve 3 through the second fluid pressure line 92, and promote oil cylinder 7 to pull the execution of IBOP spool
Mechanism, to close IBOP valve, the pressure of oil cylinder 7 can be measured by the second pressure detecting mouth 102, oil
The oil return of the opposite side of cylinder 7 is through the first hydraulic line 91, dual hydraulic control one-way valve the 3, second reversal valve 2, air relief valve 1
With the fuel tank of low-pressure oil return pipe line flow back fluid potential source main pump system, when after the Overstroke of oil cylinder 7, IBOP spool closes
Close.
After IBOP spool is closed, the top electric magnet dead electricity of the second reversal valve 2, closedown high pressure is oily, passes through simultaneously
The middle position unloading function of the second reversal valve 2, it is achieved off-load, then the rodless cavity of oil cylinder 7 and the pressure of rod chamber are by biliquid
Control check valve 3 is locked in first hydraulic line the 91, second hydraulic line the 92, the 3rd hydraulic line the 93, the 4th hydraulic pressure
In pipeline 94 and each actuator, Hydraulic Elements, now hydraulic line the second hydraulic line the 92, the 4th hydraulic tube
The rod chamber of line 94 and oil cylinder 7 is in high pressure conditions, and IBOP spool is affected by oil cylinder 7 active force of 12MPa.
In order to protect IBOP spool, it is to avoid it is for a long time by affected by high, at the restriction bar of the second reversal valve 2 dead electricity
Under part, bi-bit bi-pass solenoid directional control valve 5 electric, in the rod chamber of oil cylinder 7 and the second hydraulic line 92, shuttle valve 4
High pressure liquid force feed be back in fuel tank 8 by bi-bit bi-pass solenoid directional control valve 5, direct acting type overflow valve 6, direct acting type
The pressure of overflow valve 6 can set as required, and being normally set up pressure is 3MPa, then the active force of oil cylinder 7 is 3MPa
It is applied on IBOP spool, it is simple to the life-span of prolonged mechanical mechanism.
In like manner, when IBOP spool is opened, the bottom electric magnet of the second reversal valve 2 obtains electric, and hydraulic power source main pump system is defeated
The 16MPa high pressure liquid force feed gone out flows into air relief valve 1 through high pressure feed line, and the decompressing effect through air relief valve 1 drops
To 12MPa, it is then passed through the second reversal valve 2, flows into the left branch of dual hydraulic control one-way valve 3, simultaneously by controlling
Hydraulic fluid port opens right loop, it is simple to oil return, flow through the hydraulic oil of dual hydraulic control one-way valve 3 through the first hydraulic line 91,
3rd hydraulic line 93 enters shuttle valve 4, promotes the spool of shuttle valve 4 to move to right, and hydraulic oil arrives solenoid directional control valve 5, shape
Become blocking pressurize, can reach 12MPa；Flow through the hydraulic oil of dual hydraulic control one-way valve 3 through the first hydraulic line simultaneously
Another road of 91 flows into oil cylinder 7, and promotes oil cylinder 7 to pull the actuator of IBOP spool, to open IBOP valve,
The pressure of oil cylinder 7 can be measured by the first pressure detecting mouth 101, and the oil return of oil cylinder 7 opposite side is through the second liquid
Pressure pipeline 92, dual hydraulic control one-way valve the 3, second reversal valve 2, air relief valve 1 and low-pressure oil return pipe line flow back fluid potential source master
The fuel tank of pumping system, when, after oil cylinder 7 Overstroke, IBOP spool is opened.
The middle position unloading function of the second reversal valve 2, it is achieved off-load, the then rodless cavity of oil cylinder 7 and the pressure quilt of rod chamber
Dual hydraulic control one-way valve 3 is locked in first hydraulic line the 91, second hydraulic line the 92, the 3rd hydraulic line the 93, the 4th
In hydraulic line 94 and each actuator, Hydraulic Elements, now hydraulic line the first hydraulic line the 91, the 3rd liquid
The rod chamber of pressure pipeline 93 and oil cylinder 7 is in high pressure conditions, and IBOP spool is by oil cylinder 7 active force of 12MPa
Impact.
In order to protect IBOP spool, it is to avoid it is for a long time by affected by high, at the restriction bar of the second reversal valve 2 dead electricity
Under part, bi-bit bi-pass solenoid directional control valve 5 electric, in the rod chamber of oil cylinder 7 and the first hydraulic line 91, shuttle valve 4
High pressure liquid force feed be back in fuel tank 8 by bi-bit bi-pass solenoid directional control valve 5, direct acting type overflow valve 6, direct acting type
The pressure of overflow valve 6 can set as required, and being normally set up pressure is 3MPa, then the active force of oil cylinder 7 is 3MPa
It is applied on IBOP spool, it is simple to the life-span of prolonged mechanical mechanism.
By foregoing description, the circuit apparatus for hydraulic of well control device IBOP system delay off-load of the present utility model
Have the advantages that
1, the circuit apparatus for hydraulic simple in construction of well control device IBOP system delay off-load of the present utility model, including main
Loop and pressure release loop, described major loop is responsible for the execution of the opening and closing action of IBOP oil cylinder 7, described pressure release
The life-span protection of the relevant executive component of IBOP oil cylinder and relevant IBOP spool action is responsible in loop, and described major loop can
With independent of described pressure release loop individualism；The unloading effect in described pressure release loop is obvious, and whole uninstall process is easy
Operating, and described pressure release loop does not affect the normal work of described major loop, failture evacuation is convenient, it is possible to be suitable for
Various multichannel high pressure unloadings and do not affect the hydraulic circuit of main control hydraulic system；
2, described pressure release loop is by arranging shuttle valve so that either the rodless cavity of oil cylinder 7 or oil cylinder 7 has bar
Intracavity forms hydraulic oil, and described pressure release loop all can reduce the hydraulic pressure in oil cylinder 7, be effectively realized IBOP oil cylinder
Unloading, it is to avoid the fatigue failure of IBOP mechanical parts, protect IBOP spool.
The foregoing is only the schematic detailed description of the invention of this utility model, be not limited to model of the present utility model
Enclose.Any those skilled in the art, the equivalent made on the premise of without departing from design of the present utility model and principle
Change and amendment, all should belong to the scope of this utility model protection.And it should be noted that of the present utility model respectively
Ingredient is not limited in above-mentioned overall applicability, and each technical characteristic described in description of the present utility model can root
According to being actually needed one independent employing of selection or selecting the multinomial use that combines, therefore, this utility model is natural
Cover other combinations relevant with this case innovative point and specifically apply.
Claims (10)
1. the circuit apparatus for hydraulic of a well control device IBOP system delay off-load, it is characterised in that described hydraulic pressure returns
Road device includes oil cylinder (7), major loop and pressure release loop, and described major loop includes that the rodless cavity with oil cylinder (7) is even
Logical the first fluid pressure line (91) and the second fluid pressure line (92) connected with the rod chamber of oil cylinder (7), described
Major loop can be past by the piston of the first fluid pressure line (91) and the second fluid pressure line (92) promotion oil cylinder (7)
Multiple mobile, described pressure release loop is connected with the first fluid pressure line (91) and the second fluid pressure line (92)；When oil cylinder (7)
Piston when moving to extreme position, described pressure release loop connects with oil cylinder (7), and described pressure release loop can reduce
Hydraulic pressure in oil cylinder (7).
Circuit apparatus for hydraulic the most according to claim 1, it is characterised in that described pressure release loop includes successively
Shuttle valve (4), the first reversal valve and the first overflow valve connected, described pressure release loop connects oil cylinder by shuttle valve (4)
(7)。
Circuit apparatus for hydraulic the most according to claim 2, it is characterised in that shuttle valve (4) includes two oil-feeds
Mouth and an oil-out, an oil-in in two oil-ins of shuttle valve (4) passes through the 3rd fluid pressure line (93)
Connecting with the first fluid pressure line (91), another oil-in in two oil-ins of shuttle valve (4) passes through the 4th liquid
Pressure pipe road (94) connects with the second fluid pressure line (92).
Circuit apparatus for hydraulic the most according to claim 3, it is characterised in that described first reversal valve is two
Two electric change valves (5), bi-bit bi-pass solenoid directional control valve (5) contains oil-in and oil-out, and described first overflows
Stream valve is direct acting type overflow valve (6), the oil-in of bi-bit bi-pass solenoid directional control valve (5) and the oil-out of shuttle valve (4)
Connection, the oil-out of bi-bit bi-pass solenoid directional control valve (5) connects with the oil-in of direct acting type overflow valve (6).
Circuit apparatus for hydraulic the most according to claim 3, it is characterised in that described first reversal valve is two
Four-way electromagnetic reversing valve (51), two-position four-way solenoid directional control valve (51) is containing oil-in, oil return opening, the first outlet
With the second outlet, described first overflow valve is direct acting type overflow valve (6), the oil-out of shuttle valve (4) and two-position four-way
The oil-in connection of solenoid directional control valve (51), the oil return opening of two-position four-way solenoid directional control valve (51) and direct acting type overflow
The oil-out connection of valve (6), the first outlet of two-position four-way solenoid directional control valve (51) and direct acting type overflow valve (6)
Oil-in connection.
Circuit apparatus for hydraulic the most according to claim 1, it is characterised in that described major loop includes connecting successively
Air relief valve (1), the second reversal valve (2) and the dual hydraulic control one-way valve (3) connect, dual hydraulic control one-way valve (3) contains two
Individual outlet and two entrances, an outlet in two outlets of dual hydraulic control one-way valve (3) is by the first fluid pressure line
(91) rodless cavity with oil cylinder (7) connects, and another outlet in two outlets of dual hydraulic control one-way valve (3) is logical
Cross the second fluid pressure line (92) to connect with the rod chamber of oil cylinder (7).
Circuit apparatus for hydraulic the most according to claim 6, it is characterised in that the second reversal valve (2) is three
Four-way electromagnetic reversing valve, the second reversal valve (2) exports containing oil-in, oil return opening, the first outlet and second, the
First outlet of two reversal valves (2) connects with an entrance in two entrances of dual hydraulic control one-way valve (3), and second
Second outlet of reversal valve (2) connects with another entrance in two entrances of dual hydraulic control one-way valve (3).
Circuit apparatus for hydraulic the most according to claim 7, it is characterised in that air relief valve (1) is decompression overflow
Valve, air relief valve (1) is containing oil-in, oil-out and drain tap, the oil-out of air relief valve (1) and the second reversal valve
(2) oil-in connection.
Circuit apparatus for hydraulic the most according to claim 8, it is characterised in that the oil return of the second reversal valve (2)
Mouth connects has low-pressure oil return pipe line, the drain tap of air relief valve (1) to connect with described low-pressure oil return pipe line, air relief valve (1)
Oil-in connect have high pressure feed line.
Circuit apparatus for hydraulic the most according to claim 1, it is characterised in that described pressure release loop and oil cylinder (7)
Between the first fluid pressure line (91) on be provided with the first pressure detecting mouth (101), described pressure release loop and oil cylinder
(7) the second pressure detecting mouth (102) it is provided with on the second fluid pressure line (92) between.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620428505.2U CN205715009U (en) | 2016-05-12 | 2016-05-12 | The circuit apparatus for hydraulic of well control device IBOP system delay off-load |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620428505.2U CN205715009U (en) | 2016-05-12 | 2016-05-12 | The circuit apparatus for hydraulic of well control device IBOP system delay off-load |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205715009U true CN205715009U (en) | 2016-11-23 |
Family
ID=57298921
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620428505.2U Active CN205715009U (en) | 2016-05-12 | 2016-05-12 | The circuit apparatus for hydraulic of well control device IBOP system delay off-load |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205715009U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113758698A (en) * | 2021-09-22 | 2021-12-07 | 北京捷杰西石油设备有限公司 | IBOP test device and test method thereof |
-
2016
- 2016-05-12 CN CN201620428505.2U patent/CN205715009U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113758698A (en) * | 2021-09-22 | 2021-12-07 | 北京捷杰西石油设备有限公司 | IBOP test device and test method thereof |
| CN113758698B (en) * | 2021-09-22 | 2023-12-22 | 北京捷杰西科技股份有限公司 | IBOP test device and test method thereof |
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| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 100007 Dongzhimen North Street, Dongcheng District, Dongcheng District, Beijing Co-patentee after: Drilling Engineering Technology Research Institute, China National Petroleum Corp. Patentee after: China National Petroleum Corporation Co-patentee after: Beijing Petroleum Machinery Co., Ltd. Address before: 100007 Dongzhimen North Street, Dongcheng District, Dongcheng District, Beijing Co-patentee before: Drilling Engineering Technology Research Institute, China National Petroleum Corp. Patentee before: China National Petroleum Corporation Co-patentee before: Beijing Petroleum Machinery plant |
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| CP01 | Change in the name or title of a patent holder |