CN112855650A - Landing leg hydraulic control system and crane - Google Patents
Landing leg hydraulic control system and crane Download PDFInfo
- Publication number
- CN112855650A CN112855650A CN201911183918.3A CN201911183918A CN112855650A CN 112855650 A CN112855650 A CN 112855650A CN 201911183918 A CN201911183918 A CN 201911183918A CN 112855650 A CN112855650 A CN 112855650A
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- leg
- cylinder
- control system
- 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
Links
Images
Classifications
-
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
- F15B13/08—Assemblies of units, each for the control of a single servomotor only
- F15B13/0803—Modular units
- F15B13/0807—Manifolds
-
- 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
- B66C13/20—Control systems or devices for non-electric drives
-
- 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
- B66C23/72—Counterweights or supports for balancing lifting couples
- B66C23/78—Supports, e.g. outriggers, for mobile cranes
- B66C23/80—Supports, e.g. outriggers, for mobile cranes hydraulically actuated
-
- 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
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
-
- 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
- F15B13/027—Check 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
- 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
- F15B13/029—Counterbalance valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The utility model relates to a landing leg hydraulic control system and hoist, landing leg hydraulic control system include hydraulic pump, multiple unit valve, horizontal landing leg hydro-cylinder, vertical landing leg hydro-cylinder, control valve subassembly and oil tank. The multi-way valve comprises a first and a second combined reversing valve, and the control valve assembly comprises a back pressure valve which has a first working position for communicating the oil inlet C1 and the oil outlet C2 and a second working position for only allowing one-way communication of the oil inlet C1 to the oil outlet C2. The oil outlet C2 is respectively communicated with the rod cavities of the horizontal and vertical leg oil cylinders. An oil inlet P1 of the first joint reversing valve is communicated with the hydraulic pump, and two working oil ports D1 and D2 of the first joint reversing valve are respectively communicated with an oil inlet C1 and an oil inlet P2 of the second joint reversing valve. Working oil ports A1 and B1 of the second joint reversing valve are respectively communicated with rodless cavities of the horizontal and vertical supporting leg oil cylinders. The first joint change valve is configured such that the working port D1 can communicate with the oil tank when neither of the working ports D1, D2 is supplied with oil.
Description
Technical Field
The disclosure relates to the field of engineering machinery, in particular to a support leg hydraulic control system and a crane.
Background
Engineering machinery such as concrete trucks and cranes are generally provided with oil cylinders for controlling the swinging of supporting legs. The horizontal support leg and the vertical support leg are controlled by a horizontal oil cylinder and a vertical oil cylinder respectively to realize the extending and retracting actions of the support legs along the horizontal direction or the vertical direction. When the crane makes a sharp turn while in a traveling state, the outriggers may be thrown out together with the piston rods of the horizontal cylinders due to inertia, causing a danger.
Disclosure of Invention
The purpose of the disclosure is to provide a landing leg hydraulic control system and a crane, which can prevent a horizontal landing leg from being separated from a horizontal oil cylinder and the horizontal landing leg from being thrown out under the conditions of sharp turning and the like.
In order to achieve the above object, the present disclosure provides a support leg hydraulic control system, which includes a hydraulic pump, a multi-way valve, a horizontal support leg cylinder, a vertical support leg cylinder, a control valve assembly and an oil tank, wherein the multi-way valve includes a first joint reversing valve and a second joint reversing valve, the control valve assembly includes a back pressure valve, the back pressure valve at least includes an oil inlet C1 and an oil outlet C2, and has a first working position for conducting the oil inlet C1 and the oil outlet C2 and a second working position for allowing only the oil inlet C1 to flow to the oil outlet C2 in a one-way conduction manner, the oil outlet C2 is respectively communicated with a rod chamber of the horizontal support leg cylinder and a rod chamber of the vertical support leg cylinder, an oil inlet P1 of the first joint reversing valve is communicated with the hydraulic pump, two working D1, D2 of the first joint reversing valve are respectively communicated with the oil inlet C1 and an oil inlet P2 of the second joint reversing valve, the second allies oneself with the switching-over valve and includes two work hydraulic fluid ports A1, B1, work hydraulic fluid port A1, B1 respectively with the rodless chamber of horizontal landing leg hydro-cylinder with the rodless chamber intercommunication of vertical landing leg hydro-cylinder, first allies oneself with the switching-over valve and is configured as when work hydraulic fluid port D1, D2 are all not when not supplying oil, work hydraulic fluid port D1 can with the oil tank intercommunication.
Optionally, the back pressure valve is a hydraulic control valve, a hydraulic control port X1 of the hydraulic control valve is communicated with the oil inlet P1 of the first joint reversing valve, and when the hydraulic control port X1 reaches the opening pressure, the hydraulic control valve is located at the first working position.
Optionally, the opening pressure of the hydraulic control valve is 3-5 bar.
Optionally, the control valve assembly further comprises a check valve and a throttling element, wherein a forward end of the check valve is communicated with the oil inlet P1 of the first joint reversing valve, a reverse end of the check valve is communicated with the hydraulic control port X1, and the throttling element is connected between the forward end and the reverse end of the check valve in parallel.
Optionally, the throttling element is a throttling valve, or the throttling element is a throttling hole arranged in a pipeline between the forward end and the reverse end of the one-way valve in parallel.
Optionally, the leg hydraulic control system further includes a bidirectional hydraulic lock connected to a pipeline between the working oil port B1, the oil outlet C2, and the rod chamber and the rodless chamber of the vertical leg cylinder.
Optionally, the back pressure valve is a two-position two-way reversing valve.
Optionally, the back pressure valve is a zero leakage reversing valve.
Optionally, the single horizontal support leg cylinder, the single vertical support leg cylinder and the single second combination reversing valve form a group of support leg cylinder groups, the number of the support leg cylinder groups is multiple, and the support leg cylinder groups are arranged in parallel, an oil inlet of the second combination reversing valve in each support leg cylinder group is communicated with the working oil port D2, and a rod cavity of the horizontal support leg cylinder and a rod cavity of the vertical support leg cylinder in each support leg cylinder group are communicated with the oil outlet C2.
According to another aspect of the scheme, the crane comprises the support leg hydraulic control system.
Through above-mentioned technical scheme, can enough be when the hoist walking to the horizontal hydro-cylinder pressurize, prevent that horizontal landing leg from being thrown away, can make horizontal hydro-cylinder be in the floating condition when the hoist lifts by crane again, protect horizontal hydro-cylinder and horizontal landing leg, prevent its pressurized damage.
Additional features and advantages of the disclosure will be set forth in the detailed description which follows.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description serve to explain the disclosure without limiting the disclosure. In the drawings:
FIG. 1 is a schematic diagram of a leg hydraulic control system according to an embodiment of the present disclosure in an unactuated state;
fig. 2 is a schematic diagram of a leg hydraulic control system according to an embodiment of the present disclosure in a lifted state.
Description of the reference numerals
100-leg hydraulic control system; 10-a hydraulic pump; 20-a multi-way valve; 21-a first gang change valve; 22-a second gang change valve; 30-a horizontal support oil cylinder; 40-vertical support oil cylinder; 50-a control valve assembly; 51-back pressure valve; 511-a first working position; 512-second working position; 513-one-way valve; 514-throttle; 60-oil tank; 61-return oil filter; 70-bidirectional hydraulic lock.
Detailed Description
The following detailed description of specific embodiments of the present disclosure is provided in connection with the accompanying drawings. It should be understood that the detailed description and specific examples, while indicating the present disclosure, are given by way of illustration and explanation only, not limitation.
In the present disclosure, in a case where no description is made to the contrary, "horizontal leg cylinder" refers to a cylinder for controlling extension or retraction of a horizontal leg of a crane or other machine, and does not mean that the cylinder is disposed in a horizontal direction, and similarly, "vertical leg cylinder" refers to a cylinder for controlling extension or retraction of a vertical leg of a crane or other machine, and does not mean that the cylinder is disposed in a vertical direction. "conductive" means that both directions are capable of conducting. The "back pressure valve" includes various types of valves capable of generating back pressure, not just a certain type of valve. In addition, the terms "first", "second", and the like used in the embodiments of the present disclosure are for distinguishing one element from another, and have no order or importance.
As shown in fig. 1 and 2, according to an aspect of the present disclosure, there is provided a leg hydraulic control system 100 that can be applied to a machine having a leg, such as a crane or a concrete truck, and can maintain pressure of a horizontal leg cylinder 30 while the crane is traveling and can keep the horizontal cylinder in a floating state while the crane is lifting.
The leg hydraulic control system 100 includes a hydraulic pump 10, a multi-way valve 20, a horizontal leg cylinder 30, a vertical leg cylinder 40, a control valve assembly 50, and an oil tank 60. The multiplex valve 20 includes a first gang selector valve 21 and a second gang selector valve 22. The oil return port T1 of the first joint change valve 21 and the oil return port T2 of the second joint change valve 22 are respectively communicated with the oil tank 60. The control valve assembly 50 includes a back pressure valve 51. The back pressure valve 51 comprises at least an inlet port C1 and an outlet port C2, and has a first operating position 511 in which the inlet port C1 and the outlet port C2 are in communication, and a second operating position 512 in which only the inlet port C1 is allowed to communicate unidirectionally to the outlet port C2.
The oil outlet port C2 communicates with the rod chambers of the horizontal leg cylinder 30 and the vertical leg cylinder 40, respectively. An oil inlet P1 of the first joint reversing valve 21 is communicated with the hydraulic pump 10, and two working oil ports D1 and D2 of the first joint reversing valve 21 are respectively communicated with an oil inlet C1 and an oil inlet P2 of the second joint reversing valve 22. The second gang change valve 22 includes two working oil ports a1, B1, the working oil ports a1, B1 are respectively communicated with the rodless chamber of the horizontal leg cylinder 30 and the rodless chamber of the vertical leg cylinder 40. The first joint directional valve 21 is configured such that the working port D1 can communicate with the oil tank 60 when neither of the working ports D1, D2 is supplied with oil.
The hydraulic support leg control system 100 comprises an unactivated state (shown in fig. 1), a support leg folding and unfolding state and a lifting state (shown in fig. 2) according to different states of the crane. The leg retracting state includes a state in which the horizontal leg cylinder 30 is extended and retracted and a state in which the vertical leg cylinder 40 is extended and retracted.
When the crane is running or when the crane is not working and stationary, the support leg hydraulic control system 100 is in an inactive state as shown in fig. 1. The hydraulic oil supplied from the hydraulic pump 10 needs to be supplied to the horizontal leg cylinder 30 and the vertical leg cylinder 40 through the first coupling direction changing valve 21 and the second coupling direction changing valve 22, respectively. In this state, the working oil ports D1 and D2 of the first joint change valve 21 are both blocked from the oil inlet P1, and the oil inlet P2 and the oil return port T2 of the second joint change valve 22 are blocked from the working oil ports a1 and B1, so that no hydraulic oil enters or flows out of the rodless cavity of the horizontal leg cylinder 30. At the same time, the rod chamber of the horizontal leg cylinder 30 communicates with the outlet port C2 of the back pressure valve 51, and the back pressure valve 51 in the second operating position 512 is blocked from the outlet port C2 to the inlet port C1. Therefore, the hydraulic oil in the rod cavity and the rodless cavity of the horizontal leg cylinder 30 can be kept in the horizontal leg cylinder 30 to generate back pressure, so that the horizontal leg cylinder 30 can generate certain holding force for the horizontal leg, and the horizontal leg cannot be separated from the horizontal leg cylinder 30 and thrown out when the crane makes a sharp turn.
When the support leg hydraulic control system 100 is in a lifting state, as shown in fig. 2, the difference from the non-starting state is that the back pressure valve 51 is in the first working position 511 where the oil inlet C1 and the oil outlet C2 are communicated. At this time, since the operating positions of the first joint reversing valve 21 and the second joint reversing valve 22 are the same as those in the non-activated state, no hydraulic oil enters or exits from the rodless chamber of the horizontal leg cylinder 30, and the rod chamber of the horizontal leg cylinder 30 can communicate with the oil tank 60 through the oil outlet C2 of the back pressure valve 51, the oil inlet C1, and the operating oil port D1 of the first joint reversing valve 21 in this order. Therefore, the piston of the horizontal leg cylinder 30 can move back and forth relative to the cylinder at this time, and is in a floating state, so that the horizontal leg is in a floating state. When the crane is in lifting operation, the horizontal supporting leg can bear certain bending moment, and the horizontal supporting leg is in a floating state at the moment and can move correspondingly according to the borne load, so that the horizontal supporting leg can be protected.
In the present disclosure, there is no limitation on how the back pressure valve 51 is activated to switch the operating position, and in one embodiment, the back pressure valve 51 is a pilot operated valve. And a hydraulic control port X1 of the hydraulic control valve is communicated with an oil inlet P1 of the first joint reversing valve 21. When pilot port X1 reaches cracking pressure, the pilot operated valve is in the first operating position 511.
As described above, as shown in fig. 2, when the crane performs a lifting operation, the hydraulic pump 10 is started to allow hydraulic oil to flow into the pilot port X1 of the pilot valve and reach the cracking pressure, so that the pilot valve is switched to the first operating position 511. At this time, no hydraulic oil enters or flows out of the rodless chamber of the horizontal leg cylinder 30, and the rod chamber of the horizontal leg cylinder 30 can communicate with the oil tank 60, so that the horizontal leg is in a floating state. The first working position 511 and the second working position 512 are switched by arranging the hydraulic control valve, the hydraulic control valve is automatically started after the hydraulic pump 10 is started, the switching is timely, an additional switching device is not needed, and the structure is simple.
In other embodiments, the electrically controlled back pressure valve 51 may be used, and when the crane performs a hoisting operation, the electrically controlled back pressure valve 51 is controlled by the controller to be powered on or powered off, so that the electrically controlled back pressure valve 51 is in the first operating position 511.
Further, the opening pressure of the hydraulic control valve is 3-5 bar, preferably 5 bar. The opening pressure of the hydraulic control valve is small, so that when the crane just starts to lift and do work, and the hydraulic pump 10 just starts, the hydraulic control valve can be switched to the first working position 511, so that the horizontal support oil cylinder 30 is quickly in a floating state, and is protected as soon as possible.
In one embodiment of the present disclosure, as shown in fig. 1, the control valve assembly 50 further includes a check valve 513 and a orifice 514. A forward end of the check valve 513 is communicated with the hydraulic pump 10, a reverse end of the check valve 513 is communicated with the pilot port X1, and the orifice 514 is connected in parallel between the forward end and the reverse end of the check valve 513.
By providing the orifice 514 and the check valve 513 communicating with the pilot port X1, the hydraulic pump 10 stops supplying the oil when the leg hydraulic control system 100 needs to be switched back to the non-activated state from the leg retracting state or the lifting state. The hydraulic oil at the hydraulic control port X1 slowly flows back through the throttle member 514, and due to the damping effect generated by the throttle member 514, the hydraulic valve is slowly switched from the first working position 511 (the oil inlet C1 is communicated with the oil outlet C2) to the second working position 512 (the direction of the oil outlet C2 flowing to the oil inlet C1 is cut off). In the switching process, hydraulic oil in a rod cavity of the horizontal supporting leg oil cylinder 30 and a pipeline communicated with the rod cavity can flow away through the oil inlet C1 and the oil outlet C2, so that back pressure generated in the horizontal supporting leg oil cylinder 30 can be larger, further holding force for the horizontal supporting leg can be larger, and further the horizontal supporting leg can not be thrown out of the horizontal supporting leg oil cylinder 30 when the crane turns.
When the leg hydraulic control system 100 needs to be switched from the non-activated state to the leg retracting state or the lifting state, the hydraulic oil in the hydraulic pump 10 can rapidly flow from the forward end to the reverse end of the check valve 513 to provide the hydraulic oil to the hydraulic control port X1, and the hydraulic control valve is rapidly activated to be located at the first working position 511, so that the hydraulic oil in the horizontal leg cylinder 30 and the vertical leg cylinder 40 can be discharged into the oil tank 60, the horizontal leg cylinder 30 can be in the floating state in time, or the horizontal leg cylinder 30 and the vertical leg cylinder 40 can be rapidly extended or retracted.
The structure of the orifice 514 in the present disclosure is not limited as long as the orifice function can be achieved. In one embodiment, the orifice 514 is a throttle valve, or the orifice 514 is an orifice disposed in a conduit in parallel between the forward and reverse ends of the check valve 513. Further, the diameter of the orifice may be about 0.5 mm. In other embodiments, the throttling element 514 may be a regulating valve or other valve with flow regulating function.
To prevent the vertical leg from being forced downward after being extended, the leg hydraulic control system 100 further includes a bi-directional hydraulic lock 70. The two-way hydraulic lock 70 is connected to the pipelines between the working oil port B1, the oil outlet C2 and the rod chamber and the rodless chamber of the vertical leg cylinder 40.
Through the bidirectional hydraulic lock 70, when the crane is in a lifting state, hydraulic oil in a rod cavity and a rodless cavity of the vertical support oil cylinder 40 can be kept in the vertical support oil cylinder 40, so that the position of the vertical support oil cylinder 40 can be locked, and the vertical support is prevented from sinking when the crane is lifted.
The specific structure of the back pressure valve 51 is not limited in this disclosure as long as it can have the first and second operating positions 511 and 512 described above. In one embodiment, as shown in fig. 1 and 2, the back pressure valve 51 is a two-position, two-way directional valve. The two-position two-way reversing valve is in a first working position 511, an oil inlet C1 and an oil outlet C2 are communicated, and in a second working position 512, the direction of the oil outlet C2 flowing to an oil inlet C1 is blocked in a one-way mode.
In other embodiments, the back pressure valve 51 may also be a multi-position, multi-way reversing valve, as long as the reversing valve is capable of having the first operating position 511 and the second operating position 512 described above. For example, the back pressure valve 51 may be a three-position two-way, three-position three-way reversing valve, or a four-position two-way reversing valve, and the valve core is switched between a first operating position 511 where the oil inlet and the oil outlet are communicated and a second operating position 512 where only the oil inlet is allowed to be communicated to the oil outlet in one direction.
In order to prevent the back pressure valve 51 in the second operating position 512 from leaking the hydraulic oil in the horizontal leg cylinder 30 as much as possible, the back pressure valve 51 is a zero-leakage switching valve. This makes it possible to prevent the hydraulic oil in the rod chamber of the horizontal leg cylinder 30 from leaking through the back pressure valve 51 at all in the non-activated state, so that the generated back pressure can be maintained for a long time.
In one embodiment of the present disclosure, as shown in fig. 1 and 2, in order to control the different legs of the crane, a single horizontal leg cylinder 30, a single vertical leg cylinder 40, and a single second joint change valve 22 are a set of leg cylinder groups, and the number of leg cylinder groups is plural and they are arranged in parallel with each other. An oil inlet of the second combined reversing valve 22 in each supporting leg oil cylinder group is communicated with a working oil port D2, and a rod cavity of the horizontal supporting leg oil cylinder 30 and a rod cavity of the vertical supporting leg oil cylinder 40 in each supporting leg oil cylinder group are communicated with an oil outlet C2. The oil return port T2 of each second gang switching valve 22 is communicated with the oil tank 60 respectively.
The extending or retracting action of each oil cylinder in each support oil cylinder can be kept consistent in height by connecting the support oil cylinder groups in parallel. Moreover, the control valve assembly 50 can control the oil cylinders in each leg oil cylinder group, so that each horizontal leg oil cylinder 30 can generate enough back pressure in an un-started state, and the leg is prevented from being thrown out; the horizontal support oil cylinder 30 can be in a floating state in a hoisting state, and the horizontal support oil cylinder 30 is prevented from being damaged by stress in the hoisting process.
The specific arrangement of the reversing valves in fig. 1 and 2 is taken as an example to illustrate the working positions of the respective valves in various different states of the leg hydraulic control system. The back pressure valve 51 is a two-position two-way change valve, the first linkage change valve 21 is a three-position six-way change valve, and the second linkage change valve 22 is a three-position four-way change valve. It will be appreciated that the back pressure valve 51, the first gang direction valve 21, and the second gang direction valve 22 may be other types of valves in other embodiments.
When the leg hydraulic control system 100 is in the inactive state, the backpressure valve 51 is in the second operating position 512, and the first and second directional valves 21, 22 are in the neutral position.
When the support leg hydraulic control system 100 is in a hoisting state, the backpressure valve 51 is in the first working position 511, and the first linkage direction changing valve 21 and the second linkage direction changing valve 22 are in a middle position.
When the leg hydraulic control system 100 is in a leg retracting state, the back pressure valve 51 is in the first working position 511 during the extension and retraction of the leg cylinder. When the horizontal support oil cylinder 30 extends out, the first joint reversing valve 21 is positioned at the lower position, and each second joint reversing valve 22 is positioned at the upper position; when the horizontal support oil cylinder 30 retracts, the first linkage reversing valve 21 is in an upper position, and each second linkage reversing valve 22 is in an upper position; when the vertical support oil cylinder extends out, the first linkage reversing valve 21 is in the lower position, and each second linkage reversing valve 22 is in the lower position; when the vertical support leg oil cylinder retracts, the first linkage direction-changing valve 21 is in an upper position, and each second linkage direction-changing valve 22 is in a lower position.
According to another aspect of the present disclosure, there is also provided a crane including the leg hydraulic control system 100 described above.
Due to the adoption of the support leg hydraulic control system 100, the crane can not only maintain the pressure of the horizontal oil cylinder when the crane travels and prevent the horizontal support leg from being thrown out, but also enable the horizontal oil cylinder to be in a floating state when the crane lifts, so that the horizontal oil cylinder and the horizontal support leg are protected and prevented from being damaged by pressure.
The preferred embodiments of the present disclosure are described in detail with reference to the accompanying drawings, however, the present disclosure is not limited to the specific details of the above embodiments, and various simple modifications may be made to the technical solution of the present disclosure within the technical idea of the present disclosure, and these simple modifications all belong to the protection scope of the present disclosure.
It should be noted that, in the foregoing embodiments, various features described in the above embodiments may be combined in any suitable manner, and in order to avoid unnecessary repetition, various combinations that are possible in the present disclosure are not described again.
In addition, any combination of various embodiments of the present disclosure may be made, and the same should be considered as the disclosure of the present disclosure, as long as it does not depart from the spirit of the present disclosure.
Claims (10)
1. A hydraulic leg control system, characterized by comprising a hydraulic pump (10), a multi-way valve (20), a horizontal leg cylinder (30), a vertical leg cylinder (40), a control valve assembly (50) and an oil tank (60), wherein the multi-way valve (20) comprises a first joint directional valve (21) and a second joint directional valve (22), the control valve assembly (50) comprises a back pressure valve (51), the back pressure valve (51) at least comprises an oil inlet C1 and an oil outlet C2, and has a first working position (511) for conducting the oil inlet C1 and the oil outlet C2 and a second working position (512) for only allowing the oil inlet C1 to flow to the oil outlet C2 in one-way conduction, the oil outlet C2 is respectively communicated with a rod cavity of the horizontal leg cylinder (30) and a rod cavity of the vertical leg cylinder (40), and an oil inlet P1 of the first joint directional valve (21) is communicated with the hydraulic pump (10), two working oil ports D1, D2 of the first joint reversing valve (21) are respectively communicated with the oil inlet C1 and the oil inlet P2 of the second joint reversing valve (22), the second joint reversing valve (22) comprises two working oil ports A1, B1, the working oil ports A1, B1 are respectively communicated with a rodless cavity of the horizontal supporting leg oil cylinder (30) and a rodless cavity of the vertical supporting leg oil cylinder (40), the first joint reversing valve (21) is configured to be used when the working oil ports D1, D2 are not supplied with oil, and the working oil port D1 can be communicated with the oil tank (60).
2. The hydraulic leg control system of claim 1, wherein the backpressure valve (51) is a pilot operated valve, a pilot port X1 of the pilot operated valve is communicated with the oil inlet P1 of the first joint change valve, and the pilot operated valve is located at the first working position (511) when the pilot port X1 reaches a cracking pressure.
3. The hydraulic leg control system as claimed in claim 2, wherein the pilot operated valve has an opening pressure of 3 to 5 bar.
4. The leg hydraulic control system according to claim 2, wherein the control valve assembly (50) further comprises a check valve (513) and a throttling member (514), a forward end of the check valve (513) is communicated with the oil inlet P1 of the first joint reversing valve (21), a reverse end of the check valve (513) is communicated with the pilot port X1, and the throttling member (514) is connected in parallel between the forward end and the reverse end of the check valve (513).
5. The leg hydraulic control system according to claim 4, characterized in that the throttle member (514) is a throttle valve, or that the throttle member (514) is an orifice provided in a conduit in parallel between the forward and reverse ends of the check valve (513).
6. The leg hydraulic control system according to any one of claims 1-5, further comprising a bi-directional hydraulic lock (70), the bi-directional hydraulic lock (70) being connected on a pipeline between the working oil port B1, the oil outlet C2 and the rod and rodless chambers of the vertical leg cylinder (40).
7. The leg hydraulic control system according to any one of claims 1-5, characterized in that the back pressure valve (51) is a two-position, two-way directional valve.
8. The leg hydraulic control system according to any one of claims 1-5, characterized in that the back pressure valve (51) is a zero leakage reversing valve.
9. The support leg hydraulic control system according to any one of claims 1-5, characterized in that the single horizontal support leg cylinder (30), the single vertical support leg cylinder (40) and the single second combination directional control valve (22) are a group of support leg cylinder groups, the number of the support leg cylinder groups is multiple, and the support leg cylinder groups are arranged in parallel, the oil inlets of the second combination directional control valves (22) in each support leg cylinder group are communicated with the working oil port D2, and the rod cavities of the horizontal support leg cylinder (30) and the vertical support leg cylinder (40) in each support leg cylinder group are communicated with the oil outlet C2.
10. A crane, characterized by comprising a leg hydraulic control system (100) according to any one of claims 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911183918.3A CN112855650B (en) | 2019-11-27 | 2019-11-27 | Landing leg hydraulic control system and crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911183918.3A CN112855650B (en) | 2019-11-27 | 2019-11-27 | Landing leg hydraulic control system and crane |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112855650A true CN112855650A (en) | 2021-05-28 |
| CN112855650B CN112855650B (en) | 2023-01-17 |
Family
ID=75985762
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911183918.3A Active CN112855650B (en) | 2019-11-27 | 2019-11-27 | Landing leg hydraulic control system and crane |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112855650B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116906386A (en) * | 2023-09-12 | 2023-10-20 | 临工重机股份有限公司 | Engineering machinery control system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52108712U (en) * | 1976-02-13 | 1977-08-18 | ||
| JPS61153659U (en) * | 1985-03-15 | 1986-09-24 | ||
| CN203513142U (en) * | 2013-10-22 | 2014-04-02 | 中联重科股份有限公司 | Automobile crane and support leg control system thereof |
| CN103836015A (en) * | 2014-03-26 | 2014-06-04 | 徐州重型机械有限公司 | Elevating platform fire truck and control system of landing leg vertical oil cylinder of elevating platform fire truck |
| CN203835850U (en) * | 2014-05-12 | 2014-09-17 | 上海海鹏特种车辆有限公司 | Lifting balance pile-up valve for hydraulic molten metal trolley |
| CN104832469A (en) * | 2014-05-20 | 2015-08-12 | 北汽福田汽车股份有限公司 | Stroke control system for supporting leg oil cylinder and automobile crane with stroke control system |
| CN107859664A (en) * | 2017-11-10 | 2018-03-30 | 刘剑 | Walking and support oil cylinder linkage |
-
2019
- 2019-11-27 CN CN201911183918.3A patent/CN112855650B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52108712U (en) * | 1976-02-13 | 1977-08-18 | ||
| JPS61153659U (en) * | 1985-03-15 | 1986-09-24 | ||
| CN203513142U (en) * | 2013-10-22 | 2014-04-02 | 中联重科股份有限公司 | Automobile crane and support leg control system thereof |
| CN103836015A (en) * | 2014-03-26 | 2014-06-04 | 徐州重型机械有限公司 | Elevating platform fire truck and control system of landing leg vertical oil cylinder of elevating platform fire truck |
| CN203835850U (en) * | 2014-05-12 | 2014-09-17 | 上海海鹏特种车辆有限公司 | Lifting balance pile-up valve for hydraulic molten metal trolley |
| CN104832469A (en) * | 2014-05-20 | 2015-08-12 | 北汽福田汽车股份有限公司 | Stroke control system for supporting leg oil cylinder and automobile crane with stroke control system |
| CN107859664A (en) * | 2017-11-10 | 2018-03-30 | 刘剑 | Walking and support oil cylinder linkage |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116906386A (en) * | 2023-09-12 | 2023-10-20 | 临工重机股份有限公司 | Engineering machinery control system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112855650B (en) | 2023-01-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO2005031172A1 (en) | Hydraulic control device of industrial machinery | |
| US3760689A (en) | Control system for automatically sequencing operation of a plurality of hydraulic pumps for supplying a plurality of hydraulic actuators | |
| JP2007239992A (en) | Hydraulic system including plurality of pressure relief level | |
| KR20140050005A (en) | Flow control valve for construction machinery | |
| WO2012129042A1 (en) | Regeneration circuit | |
| CN112855650B (en) | Landing leg hydraulic control system and crane | |
| CN102303813A (en) | Crane support leg, support leg hydraulic system and crane | |
| CN110925252A (en) | Integrated multi-way valve, lifting hydraulic control system and crane | |
| JP6049386B2 (en) | Crane hydraulic circuit | |
| CN112173994B (en) | Control valve unit, hydraulic control loop and engineering equipment with telescopic crane boom | |
| CN211039191U (en) | Hydraulic drive system | |
| CN110566527A (en) | hydraulic drive system | |
| CN112032133B (en) | Hydraulic control system and work vehicle | |
| US8806862B2 (en) | Smart flow sharing system | |
| CN211039198U (en) | Hydraulic drive system | |
| US20120205563A1 (en) | Valve arrangement for actuating a load | |
| CN112797042A (en) | Integrated main control valve, hydraulic system and crane | |
| KR102500484B1 (en) | directional seated valve | |
| CN216764131U (en) | Landing leg control system and operating machine | |
| CN111677704B (en) | Hydraulic system and engineering machinery | |
| KR100621977B1 (en) | hydraulic circuit of having float function | |
| CN110552926A (en) | hydraulic drive system | |
| CN218968690U (en) | Converging multi-way valve and double-pump hydraulic system | |
| CN220283378U (en) | Counterweight control system and crane | |
| CN211545753U (en) | Multi-way reversing valve group for extension and protection of supporting leg |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |