CN104847724B - For the valve group of the movement of crane suspension - Google Patents
For the valve group of the movement of crane suspension Download PDFInfo
- Publication number
- CN104847724B CN104847724B CN201510083672.8A CN201510083672A CN104847724B CN 104847724 B CN104847724 B CN 104847724B CN 201510083672 A CN201510083672 A CN 201510083672A CN 104847724 B CN104847724 B CN 104847724B
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- China
- Prior art keywords
- valve
- interface
- control plane
- pressure
- pressure chamber
- 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.)
- Expired - Fee Related
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/82—Luffing gear
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/22—Control systems or devices for electric drives
-
- 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
- F15B11/003—Systems with 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
- 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
- F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
-
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet 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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-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
- F15B2211/30—Directional control
- F15B2211/355—Pilot pressure control
-
- 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
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- 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
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
-
- 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
- F15B2211/50—Pressure control
- F15B2211/575—Pilot pressure control
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
Abstract
The present invention relates to valve groups（20）, there is the first customer interface（21）, the second customer interface（22）, pump interface（23）With tank interface（24a；24b）, the first customer interface connect by the first valve with tank interface, and pump interface passes through the second valve（40）It is connect with the second customer interface, first throttling device is connected in series in customer side to the first valve（60）, so as to obtain First pressure chamber between first throttling device and the first valve（37）.The first control plane on the first valve of pressure-loaded in First pressure chamber（33）, the first control plane causes becoming larger for free valve cross section, second pressure chamber（67）In the first valve of pressure-loaded on the second control plane（34）, the second control plane causes the reduction of free valve cross section, sets second throttling device（63）Second pressure chamber is made to be connect with tank interface, third throttling set is set（64）The first customer interface is made to be connect with second pressure chamber.
Description
Technical field
The present invention relates to a kind of valve groups.
Background technology
A kind of crane is disclosed by 2012/0305513 A1 of US, the suspension of the energy pendulum motion of the crane can be by means of
One cylinder hydraulically moves.In addition it is known：The cylinder is manipulated by means of the first valve and the second independent valve, they are a valve groups
Component part.The valve group has the first customer interface and the second customer interface, on these customer interfaces described in connection
Cylinder.In addition, valve group has a pump interface and a tank interface.Can be optionally that work functions and control function set independent pump
Interface and tank interface.Such fluid stream is controlled using the second valve, which flows to the second customer interface from pump interface.
Such fluid stream is controlled using the first valve, which is flowed to by tank interface in tank from the first customer interface.In addition,
The throttling set adjusted can be continued by being connected in series with one in customer side to the first valve, and the movement velocity of suspension can utilize the throttling
Device is delicately adjusted.There is first pressure between the throttling set and the first valve that can be adjusted.
Occurs the noticeable wear in the region that can continue the throttling set adjusted when crane is run, this is because there
Must throttle the power of such as 300kW for example, by the narrow gap of 0.1mm wide, which discharges when suspension declines.In valve group
The abrasion that material on housing cuts down form is strong in this wise so that crane of the valve group significantly than leaving fails earlier.
A kind of solution of the problem has been proposed in also undocumented DE 10 2,013 215 750.9.But
Confirm be：It is insufficient to be used to support the dynamic loads being applied on crane, especially wind lotus with the pump power of the solution
It carries.
Invention content
It is an advantage of the invention that minimize the abrasion being previously mentioned.High dynamic loads can be supported simultaneously, this is high dynamic
State load action is to being connected on the crane in valve group.
It is proposed according to the present invention：The first control plane described in pressure-loaded in the First pressure chamber on the first valve, should
First control plane causes becoming larger for free valve cross section, wherein, described in the pressure-loaded in second pressure chamber on the first valve
Second control plane, second control plane cause the reduction of free valve cross section, wherein, a second throttling device is provided with, it should
Second throttling device makes second pressure chamber be connect at least indirectly at least one tank interface, wherein, it is provided with a third
Throttling set, the third throttling set are connect with the second pressure chamber at least indirectly making the first customer interface.The
Pressure in two pressure chambers therefore with the pressure correlation on the first customer interface and with second and the ruler of third throttling set
Very little setting is related.Correspondingly, when the pressure in First pressure chamber is increased to such a value, the first valve is just opened, the value
To the pressure correlation in second pressure chamber and related with the area relationship of the first and second control planes.In first throttling device
Pressure drop drops to the difference between the pressure in pressure and First pressure chamber on the first customer interface relative to the prior art
In value.Therefore reduce the abrasion in first throttling device.It has been found surprisingly that：Now by the pressure drop to be throttled of the first valve
Cause the low-down abrasion on the first valve in all cases, which influences the use of valve group not worth mentioningly
Service life.
When the first customer interface is unloaded based on dynamic loads such as wind load, then that in the first and second pressure chambers
A little pressure also accordingly reduce, so that remaining function of valve group is not disturbed by the solution according to the present invention.
Second throttling device and third throttling set preferably have unalterable free cross-sectional area.
The second pressure chamber can be connect by one the 4th throttling set with the First pressure chamber, wherein, described
Two control planes are more than first control plane.If the pressure on the first customer interface is quickly improved based on dynamic loads, that
First valve tight closure, so that crane does not move.When pressure current can out pass through the second throttling from second pressure chamber
When device flows out, the first valve can just be opened as described above.It needs to open the first pilot valve cited below thus.
Preferably, second and third throttling set have the free cross-sectional area more significantly larger than the 4th throttling set,
So that the pressure in second pressure chamber is mainly related to the size setting of second and third throttling set and disappears with first
Consume the pressure correlation on device interface.Influence of the first throttling device to the pressure in second pressure chamber that can be adjusted is relatively very
It is small.
The free cross-sectional area of the free cross-sectional area of the second throttling device and the third throttling set it
Between quotient can be between 0.5 and 2.Thus it is about throttled respectively by the first throttling device and the first valve that can adjust to realize
Half pressure drop.
The second throttling device can be connect by least one first pilot valve at least one tank interface,
In, first pilot valve is selectively opened wide or is closed.When crane should not when in motion, it is to be cut that the first pilot valve, which is preferable over,
It changes in closed state.But if crane suspension should decline, then the first pilot valve is switched in opening state.The
One pilot valve is actuated preferably by an electromagnetism.It is preferably configured as centre valve, therefore it is closely closed completely.As a result, when
When first valve is closed, the slow decline of crane suspension should be especially prevented.
The second throttling device and the third throttling set can pass through first check-valve and the second pressure chamber
Connection, the first check-valve only allow the fluid stream left from the second pressure chamber.Thus it is in tank or corresponding to realize
Interface pipeline in inevitable pressure fluctuations second pressure chamber in pressure.Which thereby enhance the operation peace of valve group
Quan Xing.
One second pilot valve can be provided with, second pilot valve is selectively opened or is closed the third throttling dress
Put at least indirectly connection between the second pressure chamber.When crane should not when in motion, the second pilot valve is preferably cut
It changes in closed state, wherein, which opens wide when crane suspension declines.
Second pilot valve can be selectively opened or be closed the third throttling set and first customer
At least indirectly connection between interface, as follows, that is, opens simultaneously or is closed two connections mentioned.Thus it improves
The safety in operation of valve group.
First valve can have movable first valve body, and first control plane is set on first valve body
With second control plane, wherein, be provided with the first valve seat, which can be closed by first valve body.Therefore and
Crane suspension is eliminated based on the leakage on the first valve and is slowly declined in itself.First valve seat is closely closed completely by the first valve body
It closes.Preferably, second valve is also configured as centre valve.
An independent third valve can be provided with, the third valve is connected to the first throttling device and described first and disappears
It consumes between device interface, wherein, the third valve only allows what is gone from the first customer interface to the throttling set that can be adjusted
Fluid stream.Using third valve, the connection between the first customer interface and tank interface is discharged when moving into cylinder.Third valve is excellent herein
Choosing design in this way so that small pressure drop only occur there and small abrasion accordingly occur.It is logical on first customer interface
The first throttling device and the first valve that pressure caused by crossing suspension gravity can be adjusted as described above reduce.
The third throttling set can be connected between the third valve and the first throttling device.It which thereby enhances
The safety in operation of valve group.
A the 4th independent valve can be provided with, the 4th valve is connected to the second customer interface and described first
Between throttling set, wherein, the 4th valve only allows the fluid gone from the second customer interface to the first throttling device
Stream.Using third valve, the connection between the second customer interface and tank interface is discharged when removing cylinder.4th valve herein preferably this
Sample designs so that small pressure drop only occurs there and small abrasion accordingly occurs.For it is fixed be tensioned the cylinder, rising
Counter-pressure desired during suspension is played to be generated by the throttling set that can be adjusted and the first valve as described above.
Preferably, the third and fourth valve and first throttling device are connected on a common channel, are made in the channels
With the pressure different from the pressure in First pressure chamber.
A second check-valve can be provided with, the second check-valve makes the first customer interface be pressed with described first
Power chamber connects, wherein, the second check-valve only allows the fluid stream gone from First pressure chamber to the first customer interface.
Therefore, from the pressure that pump interface comes, there is only on the piston rod side of cylinder and in the presence of on piston bottom side.Because cylinder
Piston has the area than bigger on piston rod side on piston bottom side, so cylinder removes.The hydraulic pressure squeezed on piston rod side
Fluid flows to the piston bottom side of the cylinder by second check-valve.Here, the hydraulic fluid additionally by the 4th valve and
The throttling set flowing that can be adjusted.Therefore the pump being connected on the pump interface must also only push such flow of pressurized
Body, the hydraulic fluid are squeezed by the piston rod of cylinder.It is preferable that in order to control speed, by the 4th valve presented above to
Tank exports a part for pump push stream with going.
Second valve and/or the third valve and/or the 4th valve can include a reversal valve, the reversal valve
Outlet is connected on third control plane, and the third control plane causes the reduction of involved free valve cross section, wherein, institute
The first entrance for stating reversal valve is connected on the 4th control plane, and the 4th control plane causes involved free valve cross section
Become larger, wherein, the second entrance of the reversal valve is connected on attached troops to a unit third pilot valve, wherein, the 4th control plane
It is configured to be less than the third control plane.Therefore, these valves mentioned allow for fluid stream only in one direction, similar to one
Check-valves.Using the second pilot valve, they can be independently switched to the pressure dependence of application in the state being closed completely.
Fluid power system has a valve group according to the present invention, and in the fluid power system, a cylinder can connect
Onto the first customer interface and the second customer interface, wherein, a movable component is provided with, this can be moved
The movement of component and the cylinder couple so that the gravity of the movable component causes on the first customer interface
First pressure, wherein, that pressure that first valve is opened is made to be between the 30% of the first pressure and 70%.In these pressures
Especially small abrasion is obtained under power relationship.
The piston bottom side of the cylinder may be coupled on the first customer interface, wherein, the piston rod side of the cylinder
It is connected on the second customer interface.Thus the cylinder is realized with reference to check-valves above-mentioned to pass through on pump interface
Pressure removes.
It is to be understood that feature also to be illustrated above-mentioned and below can not only be in the combination of corresponding explanation
In, and can be applied in others combine or in the form of individual in the case of without departing from the frame of the present invention.
Description of the drawings
Below by way of the exemplary detailed explaination present invention of attached drawing.Wherein：
Fig. 1 shows the hydraulic circuit diagram of the fluid power system with valve group according to the present invention.
Specific embodiment
Fig. 1 shows the hydraulic circuit diagram of the fluid power system 10 with valve group 20 according to the present invention.The hydraulic pressure
Drive system 10 is used to be lifted and fall the suspension 16 of the crane 15 schematically shown roughly, which for example can be according to US
2012/0305513 A1 is constructed.With actual ratio on the contrary, the movement between suspension 16 and cylinder 11 is coupled by means of symbolistic coupling
Bar 17 is closed to show.In fact, it is encased in crane 15 as being shown in such as 2012/0305513 A1 of US of cylinder 11.Suspension
The gravity of 16 or movable components 14 causes cylinder 11 to be moved into herein, wherein, generate first on the first customer interface 21
Pressure, the weight of the first pressure supporting suspension 16.It should be noted that the immigration of cylinder 11 can be assisted by pump 12, so as to
Such as overcome wind-force under the extremity of suspension 16.
Valve group 20 has the first customer interface 21, the second customer interface 22, pump interface 23 and two tank interface 24a；
24b.Oil and leakage rate will be controlled to return and be oriented to the tank 13 in primary side by tank interface 24b, and big volume flow passes through tank
Interface 24a flows.The housing of valve group 20 is preferably made of aluminium to save weight, wherein, wear problem according to the present invention
It is especially severe.The piston bottom side 11b of cylinder 11 is connected on the first customer interface 21.Connect on the second customer interface 22
Meet the piston rod side 11a of cylinder 11.
In addition the hydraulic fluid of tank 13, substantially no pressure, especially hydraulic oil is provided with to be in the tank.Hydraulic fluid
It is aspirated from pump 12 and is pushed to pump interface 23.Flow out tank interface 24a；The hydraulic fluid of 24b returns to stream on shortest path
Into tank 13, so that generally in tank interface 24a；The upper environment pressure of 24b, the environmental pressure can also exist on tank 13
In.If very big volume flow passes through tank interface 24a；24b flows, then can also obtain other pressure dependence.
The second valve 40 is connected between 23 and second customer interface 22 of pump interface.Second valve includes the second valve body 50,
Second valve body can tightly shut off the second valve seat completely.Second valve body 50 includes third and the 4th opposite control plane
47；48, wherein, the 4th control plane 48 is less than third control plane 47, because the second valve body 50 is constructed in the form of multi-level piston.The
Two valve seats are arranged in the region of the 4th control plane 48.Pressure on pump interface 23 is applied on the 4th control plane 48, so as to make
Thus obtaining the second valve 40 can be opened.The outlet 44 of reversal valve 43 is connected on third control plane 47.The first of the reversal valve
Entrance 45 is connected on the second customer interface 22.Thus it prevents：Hydraulic fluid can be from the second customer interface 22 or the
The return of four valves, 42 ground flows to pump interface 23.Third pilot valve 49 is connected in the second entrance 46 of reversal valve 43, the second valve 40
It can independently be tightly shut off with existing pressure dependence using the third pilot valve.
Third and fourth valve 41；42 construct identically with the second valve 40.Only size set and with valve group 20 remaining
It has any different in the connection of component.Here, the 4th control plane 48 can selectively by be in multi-level piston form the second valve body 50
Anchor ring or small disc formed.
Between the first customer interface 21 and tank interface 24a, third valve 41 can continue the throttling set 60 adjusted and the
One valve is connected in series with, so that hydraulic fluid must flow through to successive these valves mentioned, so as to from the first customer
Interface 21 reaches tank interface 24a.Third valve 41 designs in this wise herein so that occurs small pressure drop there.It is only used
In the fluid path that release and cut-off are previously mentioned.In contrast, make work using 60 and first valve of first throttling device that can be adjusted
Drop to the environmental pressure on tank interface 24a with the pressure on the first customer interface 21.
Here, adjusting of the first throttling device 60 that can be adjusted for the desired movement speed of cylinder 11, wherein, example there
As declined in the pressure between 60bar and 140bar.The first throttling device 60 that can be adjusted is come preferably by means of an electromagnet
It adjusts.Decline such as 100bar pressure on the first valve, the pressure especially with the pressure correlation on the first customer interface 21.This
Pass through second and third throttling set 63；64 realize.
First valve includes the first valve body 31, which is configured to the form of multi-level piston.First valve body 31 has the
One control plane and the second control plane 33；34, they are directed toward in opposite direction, wherein, the first control plane 33 is less than the second control
Face 34.First control plane 34 is arranged in the region of the first valve seat 32, so that pressure there be makes the first valve body
31 lift from the first valve seat 32, wherein, free valve cross-sectional area becomes larger.
First pressure chamber 37, the first control of First pressure chamber connection are obtained between 60 and first valve of first throttling device
Face 33.Second control plane 34 connection second pressure chamber 67, which passes through the 4th throttling set 65 and First pressure chamber
37 connections.In addition, second pressure chamber 67 connects the second pilot control valve 36, which is not powered on shape in shown
It is off under state.In this state, the first valve works as check-valves, which ends from 21 mistake of the first customer interface
The fluid stream come.
If the second pilot valve 36 is made to be switched to channel status now, then second pressure chamber is connected by first check-valve 66
It is connected to second and third throttling set 63；On 64, they are respectively provided with constant free cross-sectional area, the free cross section
Area is significantly greater than the free cross-sectional area of the 4th throttling set 65.Here, second throttling device 63 passes through the first pilot valve
35 connect with tank interface 24b, wherein, the first pilot valve 35 is preferably switched to channel status together with the second pilot valve 36, with
Just decline suspension 16.Third throttling set 64 is connected to the first throttling device 60 that can be adjusted and by the second pilot valve 36
On connecting line between three valves 41.Correspondingly, in second and third throttling set 63；Pressure as occurring between 64, should
Pressure is between the pressure in the pressure on the first customer interface 21 and tank interface 24b.The pressure is applied to the second control
On face 34.Correspondingly, it is just opened when pressure of first valve in First pressure chamber 37 has sufficiently large value.
As long as the first valve is closed and first throttling device 60 is at least minimally opened, the pressure in First pressure chamber 37
It is substantially identical with the pressure on the first customer interface 21 and be therefore sufficiently large, to open the first valve or to make the
One valve body 31 lifts from the first valve seat 32.Next, the first valve body 31 works in a manner that pressure claims, so that in the first pressure
Pressure as occurring in power chamber 37, the pressure is substantially only with the pressure correlation in second pressure chamber 67 and with first and second
Control plane 33；34 area relationship is related.It correspondingly can be by proper choice of the first and second throttling sets 60；63 are adjusted
Pressure percentage share on first customer interface 21 should decline at the first valve.The reserve part for the pressure being previously mentioned
Divide and decline at first throttling device 60.
It should be appreciated that：First check-valve 66 only allows the fluid stream left from second pressure chamber 67.Thus be excluded that
Fluid stream is flowed to from tank 11 in second pressure chamber 67, even if the pressure near the first customer interface 21 is very low.
The first entrance 45 of the reversal valve 43 of third valve 41 is connected on the 4th control plane 48 of the third valve, so that
The third valve 41 only allows the fluid stream gone from the first customer interface 21 to the throttling set 60 that can be adjusted.From the 4th valve
42, which flow over the hydraulic fluid come, to be flowed out by third valve 41.It only flows to the throttling set 60 that can be adjusted.
In turn, the 4th control plane 48 of third valve 41 is also connected to the first entrance 45 of involved reversal valve 43
On, so that hydraulic fluid is only capable of flowing to the throttling set 60 that can be adjusted from the second customer interface 22.From third valve 41
The hydraulic fluid that ground becomes a mandarin cannot be flowed out by the 4th valve 42.It only flows to the throttling set 60 that can be adjusted.
As a result the third and fourth valve 41 can be utilized；42 selectively make the hydraulic fluid be connect from first or second customer
Mouth 21；22 are oriented to tank interface 24a, wherein, utilize 60 and first valve of throttling set that can be adjusted in the two generations
Throttling.
It is also noted that second check-valve 61, which makes the first customer interface 21 connect with First pressure chamber 37
It connects.The second check-valve only allows the fluid stream gone from First pressure chamber 37 to the first customer interface 21.But in Fig. 1
View is on the contrary, second check-valve 61 must design in this wise so that the pressure in First pressure chamber 37 cannot make check-valves 61
Valve body moves.
Reference numerals list
10 fluid power systems
11 cylinders
11a piston rod sides
11b pistons bottom side
12 pumps
13 tanks
14 movable components
15 cranes
16 suspensions
17 coupling bars
20 valve groups
21 first customer interfaces
22 second customer interfaces
23 pump interfaces
24a tank interfaces
24b tank interfaces
31 first valve bodies
32 first valve seats
33 first control planes
34 second control planes
35 first pilot valves
36 second pilot valves
37 First pressure chambers
40 second valves
41 third valves
42 the 4th valves
43 reversal valves
44 outlets
45 first entrances
46 second entrances
47 third control planes
48 the 4th control planes
49 third pilot valves
50 second valve bodies
60 first throttling devices
61 second check-valves
62 overload safety devices
63 second throttling devices
64 third throttling sets
65 the 4th throttling sets
66 first check-valves
67 second pressure chambers.
Claims (16)
1. valve group（20）, there is one first customer interface（21）, one second customer interface（22）, a pump interface（23）With
At least one tank interface（24a；24b）, wherein, the first customer interface（21）Pass through the first valve and at least one tank
Interface（24a；24b）Connection, wherein, the pump interface（23）Pass through individual second valve（40）It is connect with second customer
Mouthful（22）Connection, wherein, the first throttling device adjusted can be continued by being connected in series with one in customer side to first valve（60）,
So that in the first throttling device（60）First pressure chamber is obtained between first valve（37）,
It is characterized in that, the First pressure chamber（37）In pressure-loaded described in the first control plane on the first valve（33）, institute
It states the first control plane and causes becoming larger for free valve cross section, wherein, second pressure chamber（67）In pressure-loaded described in first
The second control plane on valve（34）, second control plane causes the reduction of free valve cross section, wherein, it is provided with one second
Throttling set（63）, the second throttling device makes the second pressure chamber（67）It is connect at least indirectly at least one tank
Mouthful（24a；24b）Connection, wherein, it is provided with a third throttling set（64）, the third throttling set is at least indirectly making
State the first customer interface（21）With the second pressure chamber（67）Connection.
2. valve group according to claim 1, which is characterized in that the second pressure chamber（67）Pass through one the 4th throttling set
（65）With the First pressure chamber（37）Connection, wherein, second control plane（34）More than first control plane（33）.
3. valve group according to claim 2, which is characterized in that the second throttling device（63）Free cross-sectional area
With the third throttling set（64）Free cross-sectional area between quotient between 0.5 and 2.
4. according to the valve group described in one of claim 1-3, which is characterized in that the second throttling device（63）Pass through at least one
A first pilot valve（35）With at least one tank interface（24a；24b）Connection, wherein, first pilot valve（35）Selection
Open wide or be closed to property.
5. according to the valve group described in one of claim 1-3, which is characterized in that the second throttling device（63）With the third
Throttling set（64）Pass through first check-valve（66）With the second pressure chamber（67）Connection, the first check-valve only allow from
The second pressure chamber（67）The fluid stream left.
6. according to the valve group described in one of claim 1-3, which is characterized in that be provided with one second pilot valve（36）, described
Two pilot valves are selectively opened or are closed the third throttling set（64）With the second pressure chamber（67）Between at least
Indirectly connection.
7. valve group according to claim 6, which is characterized in that second pilot valve（36）It is selectively opened or is closed
The third throttling set（64）With the first customer interface（21）Between at least indirectly connection, as follows,
Open simultaneously or be closed the connection described in two.
8. according to the valve group described in one of claim 1-3, which is characterized in that first valve has movable first valve body
（31）, first control plane is set on first valve body（33）With second control plane（34）, wherein, it is provided with
One valve seat（32）, first valve seat can be by first valve body（31）It closes.
9. according to the valve group described in one of claim 1-3, which is characterized in that be provided with an independent third valve（41）, it is described
Third valve is connected to the first throttling device（60）With the first customer interface（21）Between, wherein, the third valve
（41）Only allow from the first customer interface（21）To the first throttling device（60）The fluid stream gone.
10. valve group according to claim 9, which is characterized in that the third throttling set（64）It is connected to the third
Valve（41）With the first throttling device（60）Between.
11. valve group according to claim 9, which is characterized in that be provided with a 4th independent valve（42）, the 4th valve
It is connected to the second customer interface（22）With the first throttling device（60）Between, wherein, the 4th valve（42）Only
Allow from the second customer interface（22）To the first throttling device（60）The fluid stream gone.
12. according to the valve group described in one of claim 1-3, which is characterized in that be provided with a second check-valve（61）, described
Two check-valves make the first customer interface（21）With the First pressure chamber（37）Connection, wherein, the second check-valve
（61）Only allow from the First pressure chamber（37）To the first customer interface（21）The fluid stream gone.
13. valve group according to claim 11, which is characterized in that second valve（40）And/or the third valve（41）
And/or the 4th valve（42）Including a reversal valve（43）, the outlet of the reversal valve（44）It is connected to third control plane（47）
On, the third control plane causes the reduction of involved free valve cross section, wherein, the reversal valve（43）First enter
Mouthful（45）It is connected to the 4th control plane（48）On, the 4th control plane causes becoming larger for involved free valve cross section,
Wherein, the reversal valve（43）Second entrance（46）It is connected to attached troops to a unit third pilot valve（49）On, wherein, the described 4th
Control plane（48）It is configured to be less than the third control plane（47）.
14. fluid power system（10）, there is a valve group according to one of preceding claims（20）, wherein, a cylinder
（11）It is connected to the first customer interface（21）With the second customer interface（22）On, wherein, being provided with one can transport
Dynamic component（14）, the movable component and the cylinder（11）Movement coupling, so that the weight of the movable component
Power is in the first customer interface（21）On cause first pressure, wherein, be in that pressure that first valve is opened
Between the 30% of the first pressure and 70%.
15. fluid power system according to claim 14, which is characterized in that the cylinder（11）Piston bottom side（11b）
It is connected to the first customer interface（21）On, wherein, the cylinder（11）Piston rod side（11a）Described second is connected to disappear
Consume device interface（21）On.
16. crane（15）, there is a fluid power system according to claims 14 or 15, wherein, it is described to move
Component（14）It is the suspension of the crane（16）.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102014202784.5A DE102014202784A1 (en) | 2014-02-17 | 2014-02-17 | Valve block for moving a crane jib |
| DE102014202784.5 | 2014-02-17 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104847724A CN104847724A (en) | 2015-08-19 |
| CN104847724B true CN104847724B (en) | 2018-07-03 |
Family
ID=53758837
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510083672.8A Expired - Fee Related CN104847724B (en) | 2014-02-17 | 2015-02-16 | For the valve group of the movement of crane suspension |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104847724B (en) |
| DE (1) | DE102014202784A1 (en) |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3221160C2 (en) * | 1982-06-04 | 1986-05-07 | Mannesmann Rexroth GmbH, 8770 Lohr | Control valve device consisting of two control blocks for several hydraulic drives, especially for mobile devices |
| DE3621854A1 (en) * | 1986-06-30 | 1988-01-07 | Rexroth Mannesmann Gmbh | CONTROL CIRCUIT FOR A HYDRAULIC POWER LIFT CONTROL SYSTEM |
| DE4223389C2 (en) * | 1992-07-16 | 2001-01-04 | Mannesmann Rexroth Ag | Control arrangement for at least one hydraulic consumer |
| CN100360257C (en) * | 2006-01-06 | 2008-01-09 | 太原科技大学 | Control system for great flow of electrohydraulic hammer |
| CN201144909Y (en) * | 2007-12-29 | 2008-11-05 | 江苏国力锻压机床有限公司 | Hydraulic control system of hydraulic machine |
| DE102010007545A1 (en) | 2010-02-11 | 2011-08-11 | Gottwald Port Technology GmbH, 40597 | Crane, especially mobile harbor crane, with a hybrid propulsion system |
| CN203019708U (en) * | 2012-11-30 | 2013-06-26 | 江苏沃得机电集团有限公司 | Hydraulic control system |
| DE102013215750A1 (en) | 2013-08-09 | 2015-02-12 | Robert Bosch Gmbh | Valve block for moving a crane jib |
-
2014
- 2014-02-17 DE DE102014202784.5A patent/DE102014202784A1/en not_active Withdrawn
-
2015
- 2015-02-16 CN CN201510083672.8A patent/CN104847724B/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN104847724A (en) | 2015-08-19 |
| DE102014202784A1 (en) | 2015-08-20 |
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