CN102022395A - Valve arrangement - Google Patents

Valve arrangement Download PDF

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Publication number
CN102022395A
CN102022395A CN201010287807XA CN201010287807A CN102022395A CN 102022395 A CN102022395 A CN 102022395A CN 201010287807X A CN201010287807X A CN 201010287807XA CN 201010287807 A CN201010287807 A CN 201010287807A CN 102022395 A CN102022395 A CN 102022395A
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CN
China
Prior art keywords
valve
valve arrangement
hydraulic cylinder
oil hydraulic
safety check
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201010287807XA
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Chinese (zh)
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CN102022395B (en
Inventor
马丁·路透
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marco Systemanalyse und Entwicklung GmbH
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Marco Systemanalyse und Entwicklung GmbH
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Publication of CN102022395A publication Critical patent/CN102022395A/en
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Publication of CN102022395B publication Critical patent/CN102022395B/en
Expired - Fee Related legal-status Critical Current
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH DRILLING; MINING
    • E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
    • E21D23/00—Mine roof supports for step- by- step movement, e.g. in combination with provisions for shifting of conveyors, mining machines, or guides therefor
    • E21D23/16—Hydraulic or pneumatic features, e.g. circuits, arrangement or adaptation of valves, setting or retracting devices
    • E21D23/18—Hydraulic or pneumatic features, e.g. circuits, arrangement or adaptation of valves, setting or retracting devices of advancing mechanisms
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/0406—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed during starting or stopping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/85—Control during special operating conditions
    • F15B2211/851—Control during special operating conditions during starting

Abstract

The invention provides a valve arrangement comprising two pressure pipe joints, two cylinder joints, a check-valve, and a cushion valve, the latter two being disposed among the joints.

Description

Valve arrangement
The present invention relates to valve arrangement, it is used for the step type oil hydraulic cylinder (Schreitzylinder) of the building support (Ausbaugestell) of building (Untertagebau) under the control well.
When control is used for the step type oil hydraulic cylinder of stepping mechanism of down-hole building, because the quality that will move is very big, so need special method.Known by prior art, a kind of openable safety check (R ü ckschlagventil) can be set, it should stop conveyor
Figure BSA00000278396900011
Because the strength of roll (Walze) or the pulling force on the adjacent backplate (Nachbarschild) are pulled.Yet when having only the building support to be pushed away forward, must cancel braking safely.
Further by prior art as can be known, the connection of step type oil hydraulic cylinder has gap (spielbehaftet).But because speed should be very fast during the step type hydraulic cylinder works, what the frequent generation of (Spiel) end was not wished to occur in the gap impacts.For stoping this impacting, provide a kind of trimmer valve in the prior art
Figure BSA00000278396900012
It is opened against backpressure.Reverse pressure and the pressure minimum on the whole system thereof act on usually and make on the pressure that trimmer valve opens.Backpressure acts under the hydraulic pressure (Schaltdruck) of trimmer valve, and therefore the outward pressure to the gap only keeps subtle difference.
Task of the present invention is to create improved, as to be used to control step type oil hydraulic cylinder valve arrangement, uses this valve arrangement can be fast and control the step type oil hydraulic cylinder safely, and can not produce impacting of not wishing to occur.
The solution of above-mentioned task can realize by the technical characteristics in the claim 1.
Among the present invention favourable mode of execution will specification, accompanying drawing and below claims in describe.
Thus, openable safety check is not opened with can having time-delay, and the control wiring of openable safety check can keep being connected with another pressure connection (Anschluss).
Further, maybe advantageously, a throttle non-return valve is installed on the control wiring of openable safety check, by this type of valve, safety check is not opened with having time-delay, and safety check is by the pressure control of about 300 crust on the control wiring here.And safety check is braked lentamente by set throttle valve.
Another mode of execution according to the present invention when trimmer valve is opened against dominant pressure on pressure connection PB, is particularly advantageous.Thus, between pressure connection PB and trimmer valve, compensated line can be set.
For jamproof working state
Figure BSA00000278396900021
May be even more advantageously, when an extra safety check was parallel to trimmer valve and is arranged, it was being braked to the direction of another oil hydraulic cylinder joint A from another pressure connection PA.Can guarantee by this way,, guarantee that hydraulic medium flows into rapidly in another pressure connection PA by supercharging on pressure connection PB.
Next exemplarily also with reference to the accompanying drawings the present invention is described in detail pure by a favourable mode of execution.Be illustrated as:
Fig. 1 is used to control the valve arrangement schematic representation of step type oil hydraulic cylinder;
Fig. 2 is according to the sectional drawing of a valve module of valve arrangement among Fig. 1; And
Fig. 3 is according to the enlarged diagram of the throttle non-return valve among Fig. 2.
Figure 1 shows that a valve arrangement 12, it is used for the step type oil hydraulic cylinder 10 of the building support of building under the control well, and wherein, valve arrangement 12 comprises the first pressure connection PA, the second pressure connection PB, the first oil hydraulic cylinder joint A and the second oil hydraulic cylinder joint B.According to the illustrated embodiment example, the piston area joint of step type oil hydraulic cylinder 10 is set on the first oil hydraulic cylinder joint A, and the anchor ring joint of step type oil hydraulic cylinder 10 is set on the second oil hydraulic cylinder joint B.And vice versa.
As Fig. 1 further shown in, an openable safety check 14 is set between pressure connection PB and the oil hydraulic cylinder joint B, and one be equipped with the trimmer valve of throttle valve 16 to be set between another pressure connection PA and another oil hydraulic cylinder joint A.
Openable safety check 14 is connected with another pressure connection PA by control wiring 20, and can be by the supercharging of the control joint PA of position shown in Figure 1 is connected to off position against the power of spring 22, wherein, be impossible flow on the direction of pressure connection PB from the liquid of the second oil hydraulic cylinder joint B.One throttle non-return valve 24 is set on the control wiring 20 between another pressure connection PA and the openable safety check 14, and it comprises that a safety check 26 and is parallel to the throttle valve 28 that safety check 26 is connected.Here brake the safety check 26 on another pressure connection PA direction, described pressure connection PA is then on the direction of openable safety check 14.
On position as shown in Figure 1, wherein throttle valve 16 is connected between the first pressure connection PA and the first oil hydraulic cylinder joint A, trimmer valve 18 can switch to off position against the power of spring 30, the joint PA of described off position place freely be connected with A and need not throttle valve in the middle of connect.The control wiring 32 of trimmer valve 18 keeps being connected with the first oil hydraulic cylinder joint A, makes that described trimmer valve can switch to its off position from its throttle position when joint A supercharging.
Be parallel to trimmer valve 18 and be furnished with another safety check 34, it is being braked on the direction of the first oil hydraulic cylinder joint A by the first pressure connection PA.By reference line 31, trimmer valve 18 is connected with the second pressure connection PA, so that must realize the pressure of one side against spring 30 in the motion of off position place trimmer valve 18, on the other hand against the pressure on the pressure connection PB.Therefore, trimmer valve 18 is opened to its off position against dominant pressure on pressure connection PB from its throttle position, that is to say, spring 30 is taken as the reference point with respect to the system pressure on the pressure connection PB (backpressure).
Reference mark 36 is illustrated in valve arrangement 12 outsides, is arranged in the pressure limit valve at oil hydraulic cylinder joint B place.
As shown in Figure 2, all component of above-mentioned valve arrangement 12 all is disposed in the integral body that is called as associating valve module 15.
Valve module 15 comprises the first pressure connection PA, the second pressure connection PB, the first oil hydraulic cylinder joint A and the second oil hydraulic cylinder joint B.The joint of reference mark B ' expression pressure limit valve 36.
In valve module, the trimmer valve 18 between pressure connection PA and oil hydraulic cylinder joint A is united by control piston 40 and valve cone 42 and is constituted, wherein valve cone 42 and sealing surface 44 ' contact.Control piston 40 is configured as sleeve, comprise flow channel 60, and pass through sealedly in piston boring, control piston shown in it 40 is pushed left up to running into an arrester by the spring among Fig. 2 30, and this arrester forms by a ring 44 that is inserted in the piston boring.
Comprise the valve cone 42 that can promote in control piston inside, it has a boring in the valve head zone, forms throttle valve 16 therefrom.In the outer peripheral areas of valve head 42, be provided with through-flow mouthful in the annulus 46, wherein annulus 46 has the mobile connection to openable safety check 14, and throttle non-return valve 24 is positioned at described connection, as Fig. 3 magnifying show.Throttle non-return valve 24 comprises that one has the safety check 26 of load on spring, forms throttling boring in it, and this boring forms the throttle valve 28 of throttle non-return valve 24.
The outlet of throttle non-return valve 24 enters openable safety check 14.Described safety check 14 comprises control piston 50, and it is connected with valve cone 52, makes relatively moving between two parts become possibility.Here control piston 50 comprises the piston base of sealing, and the one side relative with this piston base is provided with banded boring 54, wherein inserts the movably protruding part 56 of valve cone 52.As long as control piston 50 and valve cone 52 can be positioned on the axial direction, that is to say motion irrespectively each other on the direction of the boring of having inserted described two parts therein.And the piston base of control piston 50 is pressurized, and as shown in Figure 2, it is by protruding part 56 downward pressure valve cones 52, makes the valve base rise of valve cone under 52 from its, and spring 22 is extruded to together.Under static state, valve cone 52 is extruded with respect to valve base by spring 22, as shown in Fig. 2 and 3.
Further, guide pressure pipe joint PB in openable safety check 14 zones, it is between control piston 50 and valve cone 52.Therefore when pressure connection PB was pressurized, valve cone 52 also rose from its valve base.
The function of trimmer valve 18 is as described below:
In the position of rest of trimmer valve 18, controlling rod 40 is promoted left by the spring among Fig. 2 30, until the arrester of running on the ring 44.And valve cone 42 still can be free movable in boring inside and control piston 40 inside.The building support should be pushed forward, and pressure connection PA is pressurized, and valve cone 42 is with respect to sealing surface 44 ' be extruded.In this case, pressure medium only flows into by throttling opening 16.Correspondingly, the step type oil hydraulic cylinder that is connected with interface A only moves lentamente.When the gap from stepping mechanism by after the outside extruding, the pressure increase at joint A place, the power that acts on the valve cone 42 reduces.When power that the power of power on the described valve cone and spring 30 is produced less than the control piston 40 by sleeve shape, valve open.Internal compensation by reference channel 31 makes this mechanism not rely on retardation pressure.Yet if when valve head 42 and control piston 40 are rigidly connected, the internal pressure compensation is braked sealing surface once more.Flexible connection by spaced two pistons forms an extra safety check (safety check 34 among Fig. 1), and it makes opposite activity (on PB pressurization and open safety check 14) become possibility.

Claims (14)

1. valve arrangement (12), it is used for the step type oil hydraulic cylinder (10) of the building support of building under the control well, and described valve arrangement (12) comprising:
First pressure connection (PA) and second pressure connection (PB);
The first oil hydraulic cylinder joint (A) and the second oil hydraulic cylinder joint (B);
Openable safety check (14), it is arranged between pressure connection (PB) and the oil hydraulic cylinder joint (B); And
Be equipped with the trimmer valve (18) of throttle valve (16), this trimmer valve (18) is arranged between another pressure connection (PA) and another oil hydraulic cylinder joint (A).
2. valve arrangement as claimed in claim 1 is characterized in that, the control wiring (20) of described openable safety check (14) keeps being connected with described another pressure connection (PA).
3. valve arrangement as claimed in claim 2 is characterized in that, a throttle non-return valve (24) is set on the described control wiring (20).
4. at least one described valve arrangement in the claim as described above is characterized in that described openable safety check (14) comprises a closing spring (22).
5. at least one described valve arrangement in the claim as described above is characterized in that described trimmer valve (18) comprises a closing spring.
6. at least one described valve arrangement in the claim as described above is characterized in that described trimmer valve (18) can switch to off position by throttle position.
7. at least one described valve arrangement in the claim as described above is characterized in that the control wiring (32) of described trimmer valve (18) is connected with described another oil hydraulic cylinder joint (A) maintenance.
8. at least one described valve arrangement in the claim as described above, it is characterized in that, be parallel to described trimmer valve (18) and be furnished with a safety check (34), this safety check (34) is being braked on the direction of described another oil hydraulic cylinder joint (A) by described another pressure connection (PA).
9. at least one described valve arrangement in the claim as described above is characterized in that described trimmer valve (18) is opened against going up dominant pressure in pressure connection (PB).
10. at least one described valve arrangement in the claim as described above is characterized in that all component of described valve arrangement (12) are arranged in the holistic valve module (15).
11. at least one described valve arrangement in the claim as described above, it is characterized in that, described openable safety check (14) comprises a control piston (50), and described control piston (50) is connected with valve cone (52), makes relatively moving between two parts become possibility.
12. valve arrangement as claimed in claim 11 is characterized in that, the control piston (50) of described openable safety check (14) comprises the piston base of sealing.
13. at least one described valve arrangement in the claim as described above, it is characterized in that, described trimmer valve (18) comprises a control piston (40), and described control piston (40) is connected with valve cone (42), makes relatively moving between two parts become possibility.
14. valve arrangement as claimed in claim 13 is characterized in that, the control piston (40) of described trimmer valve (18) comprises a flow channel (60).
CN201010287807.XA 2009-09-18 2010-09-17 Valve arrangement Expired - Fee Related CN102022395B (en)

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DE102009042120.3A DE102009042120B4 (en) 2009-09-18 2009-09-18 valve assembly
DE102009042120.3 2009-09-18

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CN102022395B CN102022395B (en) 2015-06-17

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DE (1) DE102009042120B4 (en)
PL (1) PL215887B1 (en)
RU (1) RU2448255C1 (en)
UA (1) UA98699C2 (en)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
KR20150018448A (en) * 2013-08-08 2015-02-23 만 디젤 앤 터보 에스이 Valve arrangement for a fuel supply system and fuel supply system

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DE3709504A1 (en) * 1987-03-23 1988-10-06 Rexroth Mannesmann Gmbh Valve device
DE4313250A1 (en) * 1993-04-23 1994-10-27 Bosch Gmbh Robert Hydraulic control device
KR19980015286A (en) * 1996-08-20 1998-05-25 추호석 Hydraulic cylinder with cushion device
CN2289108Y (en) * 1996-11-15 1998-08-26 田银香 Hydraulic buffering vavle
US20040088972A1 (en) * 2000-05-11 2004-05-13 Edwin Harnischfeger Hydraulic control arrangement
US20070277519A1 (en) * 2004-07-09 2007-12-06 Soenke Jessen Lifting Gear Valve Arrangement
CN101403312A (en) * 2007-10-05 2009-04-08 玛珂系统分析和开发有限公司 Valve device
CN101413395A (en) * 2007-10-16 2009-04-22 玛珂系统分析和开发有限公司 Valve arrangement

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Publication number Priority date Publication date Assignee Title
KR20150018448A (en) * 2013-08-08 2015-02-23 만 디젤 앤 터보 에스이 Valve arrangement for a fuel supply system and fuel supply system
CN104454277A (en) * 2013-08-08 2015-03-25 曼柴油机和涡轮机欧洲股份公司 Valve assembly for fuel supply system and the fuel supply system
KR102125102B1 (en) 2013-08-08 2020-06-19 만 에너지 솔루션즈 에스이 Valve arrangement for a fuel supply system and fuel supply system

Also Published As

Publication number Publication date
UA98699C2 (en) 2012-06-11
DE102009042120A1 (en) 2011-03-24
DE102009042120B4 (en) 2016-11-17
PL215887B1 (en) 2014-02-28
PL392437A1 (en) 2011-03-28
CN102022395B (en) 2015-06-17
RU2448255C1 (en) 2012-04-20

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