CN202379608U - Boarding rotating hydraulic control system and crane provided with same - Google Patents
Boarding rotating hydraulic control system and crane provided with same Download PDFInfo
- Publication number
- CN202379608U CN202379608U CN2011205634908U CN201120563490U CN202379608U CN 202379608 U CN202379608 U CN 202379608U CN 2011205634908 U CN2011205634908 U CN 2011205634908U CN 201120563490 U CN201120563490 U CN 201120563490U CN 202379608 U CN202379608 U CN 202379608U
- Authority
- CN
- China
- Prior art keywords
- hydraulic fluid
- valve
- fluid port
- oil
- getting
- 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 - Lifetime
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
The utility model discloses a boarding rotating hydraulic control system, comprising a first direction control valve arranged among a rotating motor, a system pressure oil path and an oil-returning oil path, and further comprising a variable back pressure element which is arranged between an oil-returning opening of the first direction control valve and the system oil-returning oil path; and the first direction control valve is conducted with the variable back pressure element in a unidirectional manner. Compared with the prior art, the variable back pressure element is adjusted to increase an oil-returning pressure under the work conditions of starting to rotate or stopping rotating when a resistance moment change rate is greater, so that the system rigidity is correspondingly enhanced to overcome pressure impact under the work conditions of starting to rotate or stopping rotating, and reliable guarantees for improving the rotating performance and the stability of a whole vehicle are provided. Meanwhile, the system oil-returning oil path has a fixed back pressure all the time, so that the system rigidity is correspondingly enhanced and a boarding rotating process has a better anti-impact capability. On the basis, the utility model further provides a crane provided with the boarding rotating hydraulic control system.
Description
Technical field
The utility model relates to a kind of construction machinery and equipment technology, is specifically related to a kind of hoisting crane of getting on the bus and turning round hydraulic control system and having this hydraulic control system.
Background technology
For the construction machinery and equipment that the relative chassis of getting on the bus rotates, swing type mechanism to open the braking stationarity be one of important indicator of complete machine performance, therefore, optimal design avoids swing type mechanism to open that the influence of inertia impact is the research and development focus of industry in the braking procedure.Such as: the revolution hydraulic control system of getting on the bus of hoisting crane.
At present, along with developing rapidly of economic construction, Infrastructure scales such as arteries of communication, airport, harbour, water conservancy and hydropower, urban construction are also increasing, and the demand of market elevator machinery also increases thereupon.As everyone knows, in the crane job process, these move the spatial alternation of realizing the lift heavy thing revolution of the hoisting of flexible, the suspension hook of luffing that need be through derricking cylinder, arm, turntable.The working stability of crane rotation operating system directly influences the safe reliability of complete machine.
See also Fig. 1, this figure is the fundamental diagram of a kind of revolution hydraulic control system of getting on the bus in the prior art.
Pressure oil liquid inputs to the epitrochoidal chamber of rotary motor 20 from the P mouth via slewing directional control valve 10, and the forward and backward through rotary motor 20 drives to get on the bus turns round.In this hydraulic control system, adopt the safety valve of main by pass valve 30, utilize the pilot pressure of the main by pass valve of precursor overflow valve 40 controls as rotary system; And obtain guide's oil sources of revolution switching-over through pressure oil circuit P, control slewing directional control valve 10 main valve plugs through electric proportional pressure-reducing valve 50 decompression backs and commutate.In the manipulation of physical process,, regulate the different pilot pressure oil of electric proportional pressure-reducing valve 50 outputs, thereby control rotating switching-over and obtain different speed of revolutionss through electric ratio handle output Different control signal.
Wherein, Rotary buffering valve 60 is made up of four check valves (6a, 6b, 6c, 6d) and an overload protection by pass valve 61; Obtain guide oil to overload protection by pass valve 61 pilot port from the load feedback mouth XL mouth of slewing directional control valve 10, can in the forward and backward motion process, play the function of buffering and repairing.When rotary motor moves right in the process, carry factor such as non-constant and cause the resisting moment of gyroscopic movement to increase suddenly if support ground injustice and wind, then the pressure on rotary motor right side is because the inertia of gyroscopic movement parts and raising suddenly; Under this state; When pressure surpasses overload protection by pass valve 61 settling pressures and the coefficient pressure of by pass valve pilot pressure XL; Overload protection by pass valve 61 is opened; Rotary motor 20 right atrial pressures oil, is realized cushioning in the motion process to slow down the compression shock in the pipeline through check valve 6d and 61 overflows of overload protection by pass valve; Simultaneously, through check valve 6a to rotary motor 20 left side repairings.Otherwise still.
Yet; In the startup of gyroscopic movement and the process that stops; Because system exists gap and arm and turntable for being rigidly connected by static the engagement to motion or, rotary reducer static by moving to and revolution Support Gear; And weight and arm through steel rope for flexibly connecting, just as single pendulum, thus revolution start with stopped process in the resisting moment rate of change greatly, the impact of system is bigger.That is to say that this revolution hydraulic control system of getting on the bus can't avoid turning round the impact in startup and the stopped process; Particularly, during handling large-tonnage weight, even more serious at the moment impact that starts and stop; Very easily cause the hydraulic efficiency impact in the conduit under fluid pressure; Reduce the service life of each relevant Hydraulic Elements, or even the car load that causes owing to rotary system shake rocks, thereby influence the car load stationarity.
In view of this, demanding urgently looking for another way is optimized design to the existing revolution hydraulic control system of getting on the bus, and system shock occurs effectively to avoid revolution to start glancing impact.
The utility model content
To above-mentioned defective, the technical matters that the utility model solves is, a kind of revolution hydraulic control system of getting on the bus is provided, with the balance of each operating mode turning down operation of effective raising.On this basis, the utility model also provides a kind of hoisting crane with this revolution hydraulic control system of getting on the bus.
The revolution hydraulic control system of getting on the bus that the utility model provides; Comprise the first direction control cock that is arranged between rotary motor and system pressure oil circuit and the oil return circuit; Also comprise the return opening that is arranged on said first direction control cock and the variable back pressure element between the system oil return oil circuit, and unidirectional conducting between said first direction control cock to the said variable back pressure element.
Preferably, said variable back pressure element is specially automatically controlled proportional pressure control valve, pilot relief valve or automatically controlled flow regulating valve, is provided with check valve between the return opening of said first direction control cock to the said variable back pressure element.
Preferably, be provided with two reverse overload protection by pass valves that are provided with between two hydraulic fluid ports of said rotary motor, and be respectively arranged with check valve between the downstream of said variable back pressure element to two hydraulic fluid ports of said rotary motor.
Preferably; Said first direction control cock is specially 3 position-5 way valve, and its first hydraulic fluid port is communicated with the system pressure oil circuit, second hydraulic fluid port and the 3rd hydraulic fluid port all is communicated with the system oil return oil circuit, the 4th hydraulic fluid port and the 5th hydraulic fluid port are communicated with two hydraulic fluid ports of said rotary motor respectively; At first control position, its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting, second hydraulic fluid port are non-conduction; At second control position, its first hydraulic fluid port and the 5th hydraulic fluid port conducting, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 3rd hydraulic fluid port are non-conduction; At the 3rd control position, its first hydraulic fluid port is non-conduction, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting.
Preferably, said first direction control cock is specially two-way hydraulic control apportioning valve; Stablize at two hydraulic control hydraulic fluid ports of said first direction control cock and system pressure and to be respectively arranged with second direction control cock and third direction control cock between oil circuit and the oil return circuit.
Preferably, said second direction control cock and third direction control cock are specially electronically controlled proportional valve.
Preferably, said rotary motor has normally closed rotary braking oil cylinder, and the working oil chamber of said rotary braking oil cylinder and system pressure are stablized between oil circuit and the oil return circuit and be provided with switch valve.
Preferably, said switch valve is specially the electric-controlled switch valve.
Preferably, also comprise the main by pass valve that is arranged between system pressure oil circuit and the oil return circuit, and the precursor overflow valve of the pilot pressure of the main by pass valve of control; And, being provided with shuttle valve between two hydraulic fluid ports of said rotary motor, the oil outlet of said shuttle valve is communicated with the guide's hydraulic fluid port of said main by pass valve and the oil inlet of said precursor overflow valve.
The hoisting crane that the utility model provides, comprise the chassis with can be with respect to the turntable of getting on the bus of chassis gyroscopic movement; Also comprise the foregoing revolution liquid control system of getting on the bus, the rotary motor output rotary motive power of the said revolution hydraulic control system of getting on the bus is to the turntable of getting on the bus.
Than prior art, the said revolution hydraulic control system of getting on the bus of the utility model is primarily aimed at rotary stability and has carried out optimizing improvement.This scheme adopts two hydraulic fluid ports of first direction control cock control rotary motor to be communicated with system pressure oil circuit or oil return circuit, to realize that rotary motor positive and negative two is to rotation; Wherein, Be provided with variable back pressure element between the return opening of first direction control cock and the system oil return oil circuit, so be provided with, start and stop under the operating mode in revolution; When resisting moment rate of change in the process is big; Can regulate this variable back pressure element according to the principle of hydraulic pressure power consumption has increased its spill pressure, thereby corresponding enhanced system rigidity starts and stop the compression shock under the operating mode to overcome, for the stationarity that improves turnability and car load provides reliable guarantee.Simultaneously; Unidirectional conducting between this first direction control cock to the variable back pressure element; Thereby on the oil return circuit of system, has a fixing back pressure all the time; And the corresponding system stiffness that increased, all have impact resistance preferably in the feasible revolution whole process of getting on the bus, further increased the stationarity of rotary system.
In the preferred version of the utility model, between two hydraulic fluid ports of rotary motor, be provided with two reverse overload protection by pass valves that are provided with.Like this; When the resisting moment that moves right when rotary motor increased suddenly, then the pressure on rotary motor right side was because the inertia of gyroscopic movement parts and raising suddenly, under this state; When if right atrial pressure surpasses the settling pressure of overload protection by pass valve; Then by pass valve is opened, and to slow down the compression shock in the pipeline, realizes cushioning in the motion process; Meanwhile, rotary motor right atrial pressure fluid carries out effective repairing on the left of flowing to rotary motor.And, downstream to rotary motor that can also be through variable back pressure element move right the further repairing of check valve between the return opening.Otherwise still.
In another preferred version of the utility model; Between two hydraulic fluid ports of rotary motor, be provided with shuttle valve; The oil outlet of this shuttle valve feeds back to main by pass valve and precursor overflow valve with the operation pressure of rotary motor; So that when the resisting moment of rotary motor motion increases suddenly, increase the response pressure of main by pass valve, thereby further improve system rigidity and stationarity.
The revolution hydraulic control system of getting on the bus that the utility model provides is specially adapted to self-propelled crane applicable to any type of hoisting crane.
Description of drawings
Fig. 1 is the get on the bus fundamental diagram of revolution hydraulic control system of existing a kind of typical case;
Fig. 2 is the integral structure scheme drawing of wheel crane described in the specific embodiment;
Get on the bus described in Fig. 3 specific embodiment and turn round the fundamental diagram of hydraulic control system.
Among Fig. 3:
Rotary motor 1, rotary braking oil cylinder 11, first direction control cock 2, automatically controlled proportional pressure control valve 3, first check valve 41, second check valve 42, the first overload protection by pass valve 51, the second overload protection by pass valve 52, the 3rd check valve 53, the 4th check valve 54, second direction control cock 61, third direction control cock 62, switch valve 7, main by pass valve 81, precursor overflow valve 82, shuttle valve 9.
The specific embodiment
The core of the utility model is to provide a kind of revolution hydraulic control system of getting on the bus, and has carried out optimize improving based on the gyroscopic movement stability requirement, the revolution impact phenomenon to occur in the turning course of avoiding getting on the bus.Specify this embodiment below in conjunction with Figure of description.
Be without loss of generality, this embodiment specifies as main body with wheel crane.
See also Fig. 2, this figure is the integral structure scheme drawing of the said wheel crane of this embodiment.
As shown in the figure, this hoisting crane comprise wheel undercarriage, can be with respect to the turntable of getting on the bus of chassis gyroscopic movement, be articulated in the anterior Lifting device of turntable, the main function components such as winding plant of weight up-down propulsive effort be provided.Identical with prior art, get on the bus to be provided with between turntable and the chassis and realize that both turn round seat ring in relative rotation, and get on the bus turntable positive and negative two to motion through the rotary motor driving.
Need to prove that the said aforementioned functional parts of this embodiment can adopt existing techniques in realizing, so this paper repeats no more.For specifying the application's inventive point, please further referring to the fundamental diagram of the revolution hydraulic control system of getting on the bus shown in Figure 3, this hydraulic control system is used to control the rotation direction of rotary motor, the adjustment of speed.
This revolution hydraulic control system of getting on the bus comprises the first direction control cock 2 that is arranged between rotary motor 1 and system pressure oil circuit P and the oil return circuit T, realizes that with the switching-over through first direction control cock 2 rotary motor 1 positive and negative two is to rotation.And; Between the return opening of first direction control cock 2 and system oil return oil circuit T, be provided with variable back pressure element, so be provided with, start and stop under the operating mode in revolution; When resisting moment rate of change in the process is big; Can regulate this variable back pressure element according to the principle of hydraulic pressure power consumption increases its spill pressure, thereby corresponding enhanced system rigidity starts and stop the compression shock under the operating mode to overcome, for the stationarity that improves turnability and car load provides reliable guarantee.
Shown in the figure, this variable back pressure element adopts automatically controlled proportional pressure control valve 3, during practical operation, in revolution startup and stop motion process, can regulate variable back pressure through bar handle.The descending variation of resisting moment in the revolution start-up course, and rate of change is bigger; Under this state; Can change from small to big and rate of change through the electric current that changes the automatically controlled proportional pressure control valve 3 of series connection; So that its oil return line back pressure is changed from small to big; Overcoming the load variations rate that reduces system when resisting moment changes, impact phenomenon can not appear turning round, make in the revolution start-up course more steady.In like manner; The ascending variation of resisting moment in the revolution stopped process; Electric current that can be through changing the automatically controlled proportional pressure control valve 3 of series connection from large to small and rate of change; So that its oil return line back pressure is from large to small, in the variation that overcomes resisting moment, reduce the load variations rate of system, so that more steadily reliable in the feasible revolution stopped process.Should be understood that based on aforementioned control principle, this variable back pressure element also can adopt pilot relief valve or automatically controlled flow regulating valve, as long as satisfy the use needs all in the scope that the application asks for protection.
Simultaneously, unidirectional conducting between this first direction control cock 2 to the automatically controlled proportional pressure control valve 3 specifically is provided with check valve between return opening to the automatically controlled proportional pressure control valve 3 of first direction control cock 2; Thus, on the oil return circuit of rotary system, have a fixing back pressure all the time, and the rigidity of corresponding increase system, making gets on the bus all has impact resistance preferably in the revolution whole process.Certainly, can adopt the first direction control cock 2 of different control modes, different structure form as required, for example the 3 position-5 way valve shown in the figure.First hydraulic fluid port of this valve is communicated with system pressure oil circuit P; Its second hydraulic fluid port and the 3rd hydraulic fluid port pass through first check valve 41 and second check valve 42 and automatically controlled proportional pressure control valve 3 respectively and are communicated with system oil return oil circuit T, and its 4th hydraulic fluid port and the 5th hydraulic fluid port are communicated with two hydraulic fluid ports of rotary motor 1 respectively.At first control position (right position), its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting, second hydraulic fluid port are non-conduction, this state turning down motor 1 turning clockwise; On second control position (left side position), its first hydraulic fluid port and the 5th hydraulic fluid port conducting, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 3rd hydraulic fluid port are non-conduction, and this state turning down motor 1 turns left; At the 3rd control position (meta), its first hydraulic fluid port is non-conduction, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting.
In addition,, be provided with two reverse overload protection by pass valves that are provided with between two hydraulic fluid ports of rotary motor 1, be specially the first overload protection by pass valve 51 and the second overload protection by pass valve 52 in order further to improve the impact resistance in the gyroscopic movement process; And be respectively arranged with check valve between two hydraulic fluid ports of the downstream of automatically controlled proportional pressure control valve 3 to rotary motor 10, be specially the 3rd check valve 53 and the 4th check valve 54.When the resisting moment that moves right when rotary motor 10 increases suddenly; Then the pressure on rotary motor right side raises suddenly owing to the inertia of gyroscopic movement parts; Under this state, when surpassing the settling pressure of the first overload protection by pass valve 51 as if right atrial pressure, then by pass valve is opened; To slow down the compression shock in the pipeline, realize cushioning in the motion process; Meanwhile, rotary motor right atrial pressure fluid flows to rotary motor 10 left sides and carries out effective repairing.And, downstream to rotary motor 1 that can also be through automatically controlled proportional pressure control valve 3 move right the 4th check valve 54 further repairings between the return opening.Otherwise still.In fact, be equivalent to can shock proof cushion valve for the combination function of the first overload protection by pass valve 51, the second overload protection by pass valve 52, the 3rd check valve 53 and the 4th check valve 54.
For further improving the controller performance of total system; The first direction control cock 2 of 3 position-5 way described in this programme is specially two-way hydraulic control apportioning valve; As shown in the figure, two hydraulic control hydraulic fluid ports of this first direction control cock 2 and system pressure are stablized and are respectively arranged with second direction control cock 61 and third direction control cock 62 between oil circuit X and the oil return circuit T; Preferably; Second direction control cock 61 is specially electronically controlled proportional valve with third direction control cock 62; Stablize oil circuit X according to the electric signal switch pressure of steering command output or oil return circuit T is communicated with the corresponding hydraulic control hydraulic fluid port of first direction control cock 2, and then realization is to the reliable control of the turning to of rotary motor 1, rotating speed.
For rotary motor 1 with normally closed rotary braking oil cylinder 11; The working oil chamber of rotary braking oil cylinder 11 and system pressure are stablized between oil circuit X and the oil return circuit T and are provided with switch valve 7; This switch valve 7 can adopt automatically controlled two position three-way valve, and the epitrochoidal chamber of control rotary braking oil cylinder 11 is communicated with pressure stability oil circuit X or oil return circuit T.That is to say that the epitrochoidal chamber of normality turning down brake cylinder 11 is communicated with oil return circuit T, and when needs are got on the bus revolution; Then export these switch valve 7 switching-overs of control signal control; Control rotary braking oil cylinder 11 is communicated with pressure stability oil circuit X, removes rotary braking, promptly is equivalent to the electric-controlled switch valve.In fact, pressure stability oil circuit X can provide for independent oil sources, also can come from system pressure oil circuit P, controls it and is in the constant pressure state and gets final product.
Based on the system safety requirement, the revolution hydraulic control system of getting on the bus that this programme provides adopts by pass valve to provide safeguard equally.As shown in the figure, main by pass valve 81 is arranged between system pressure oil circuit P and the oil return circuit T, and adopts the pilot pressure of the main by pass valve 81 of precursor overflow valve 82 controls, realizes earial drainage when guaranteeing the rotary system hypertonia.Simultaneously; This programme further effectively utilizes the load feedback signal of rotary motor 1; As shown in the figure; Be provided with shuttle valve 9 between two hydraulic fluid ports of rotary motor 1, two oil inlets of shuttle valve 9 are communicated with two hydraulic fluid ports of rotary motor 1 respectively, and its oil outlet is communicated with the guide's hydraulic fluid port of main by pass valve 81 and the oil inlet of precursor overflow valve 82; Thus, the operation pressure of rotary motor 1 is fed back to main by pass valve 81 and precursor overflow valve 82 in real time,, thereby further improve system rigidity and stationarity so that when the resisting moment of rotary motor 1 motion increases suddenly, increase the response pressure of main by pass valve 81.
Certainly, based on the principle of work of shuttle valve, this shuttle valve 9 also can adopt two check valves that are oppositely arranged to realize its function needs, all can as long as satisfy the use needs.
The principle of work that the minimizing revolution of following brief description this programme is impacted.
The left side A pressure of rotary motor 1 is Pa, and its right side B links to each other with system oil return oil circuit (fuel tank) through first direction control cock 2, first check valve 41 and automatically controlled proportional pressure control valve 3, and pressure is Pb; Then, rotary motor 1 oil inlet and oil return mouth pressure reduction is: Δ P=Pa-Pb.
Motor torsional moment formula: in
formula:
V
gThe discharge capacity of-rotary motor, constant;
η
mThe mechanical efficiency of-rotary motor, constant;
Δ P-is the pressure reduction of rotary motor oil inlet and oil return mouth.
Moment of torsion formula by rotary motor 1 can be known: the moment of torsion of rotary motor 1 output that is used for balance rotary system resisting moment is only relevant with the pressure reduction of its oil inlet and oil return mouth.
One, starts operating mode
1.1 revolution starts when moving right; In order to make rotary motor entrance pressure Pa constant, may command is changed from small to big the control current of the automatically controlled proportional pressure control valve 3 in its oil return line, changes from small to big thereby control the pressure of opening automatically controlled proportional pressure control valve 3; And then and control spill pressure Pb changes from small to big; Finally reach the trend that oil inlet and oil return pressure differential deltap P is from large to small and change, with the output torque of realizing rotary motor 1 then from large to small, satisfy in the process that revolution starts to the right; To motion, the resistance distance is descending and rate of change is big by static.
1.2 revolution starts when left movement; In order to make rotary motor 1 entrance pressure Pb constant, through control the control current of automatically controlled proportional pressure control valve 3 in the oil return line is changed from small to big, change from small to big thereby control the pressure of opening automatically controlled proportional pressure control valve 3; And then control spill pressure Pa changes from small to big; Finally reach the trend that oil inlet and oil return pressure differential deltap P is from large to small and change, with the output torque of realizing rotary motor 1 from large to small, satisfy in the process that revolution starts left; To motion, the resistance distance is descending and rate of change is big by static.
Therefore, significantly reduced and start to have impacted, system can make in the start-up course of gyroscopic movement comparatively steadily reliable.
Two, stop operating mode
In the stopped process of gyroscopic movement, rotary motor 1 is static by moving to the right or left, and the resistance distance is all ascending and rate of change is big; First direction control cock 2 is in meta.The left and right sides of rotary motor 1 links to each other with system oil return oil circuit (fuel tank) with second check valve 42, automatically controlled proportional pressure control valve 3 through first direction control cock 2, first check valve 41.When rotary motor 1 moves right in the process that stops; Rotary motor 1 right side is a return opening, the control current that makes automatically controlled proportional pressure control valve 3 in the oil return line through control from large to small, thereby the pressure that automatically controlled proportional pressure control valve 3 is opened in control from large to small; And then control spill pressure Pa from large to small; Finally reach oil inlet and oil return pressure differential deltap P and be the trend variation of changing from small to big, change from small to big, satisfy resistance apart from the requirement that changes with the output torque of realizing rotary motor 1; Meanwhile, rotary motor 1 passes on left 54 repairings of second check valve.Vice versa.
Therefore, significantly reduced and stop to impact, system can make in the stopped process of gyroscopic movement comparatively steadily reliable.
Three, normally turn round operating mode
Owing to be respectively arranged with first check valve 41 and second check valve 42 between two return openings of first direction control cock 2 to the automatically controlled proportional pressure control valve 3; All the time has a fixing back pressure on the oil return circuit of rotary system; The corresponding rigidity that increases system all has impact resistance preferably in the feasible revolution whole process of getting on the bus
Special version be; First direction control cock 2 in this programme, the first overload protection by pass valve 51, the second overload protection by pass valve 52, the 3rd check valve 53, the 4th check valve 54 and switch valve 7 can adopt independent component; Also can be integrated into the valve group; Corresponding oil sources is taken at valve inner, and the system stringing of making is compact more; In addition, so setting has assembly process process preferably, is convenient to carry out the assembly operation of complete machine.
The above only is the preferred implementation of the utility model; Should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the utility model principle; Can also make some improvement and retouching, these improvement and retouching also should be regarded as the protection domain of the utility model.
Claims (10)
1. the revolution hydraulic control system of getting on the bus; Comprise the first direction control cock that is arranged between rotary motor and system pressure oil circuit and the oil return circuit; It is characterized in that; Also comprise the return opening that is arranged on said first direction control cock and the variable back pressure element between the system oil return oil circuit, and unidirectional conducting between said first direction control cock to the said variable back pressure element.
2. the revolution hydraulic control system of getting on the bus according to claim 1; It is characterized in that; Said variable back pressure element is specially automatically controlled proportional pressure control valve, pilot relief valve or automatically controlled flow regulating valve, is provided with check valve between the return opening of said first direction control cock to the said variable back pressure element.
3. the revolution hydraulic control system of getting on the bus according to claim 2; It is characterized in that; Be provided with two reverse overload protection by pass valves that are provided with between two hydraulic fluid ports of said rotary motor, and be respectively arranged with check valve between the downstream of said variable back pressure element to two hydraulic fluid ports of said rotary motor.
4. according to each described revolution hydraulic control system of getting on the bus in the claim 1 to 3; It is characterized in that; Said first direction control cock is specially 3 position-5 way valve, and its first hydraulic fluid port is communicated with the system pressure oil circuit, second hydraulic fluid port and the 3rd hydraulic fluid port all is communicated with the system oil return oil circuit, the 4th hydraulic fluid port and the 5th hydraulic fluid port are communicated with two hydraulic fluid ports of said rotary motor respectively; At first control position, its first hydraulic fluid port and the 4th hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting, second hydraulic fluid port are non-conduction; At second control position, its first hydraulic fluid port and the 5th hydraulic fluid port conducting, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 3rd hydraulic fluid port are non-conduction; At the 3rd control position, its first hydraulic fluid port is non-conduction, the 4th hydraulic fluid port and the second hydraulic fluid port conducting, the 5th hydraulic fluid port and the 3rd hydraulic fluid port conducting.
5. the revolution hydraulic control system of getting on the bus according to claim 4 is characterized in that said first direction control cock is specially two-way hydraulic control apportioning valve; Stablize at two hydraulic control hydraulic fluid ports of said first direction control cock and system pressure and to be respectively arranged with second direction control cock and third direction control cock between oil circuit and the oil return circuit.
6. the revolution hydraulic control system of getting on the bus according to claim 5 is characterized in that said second direction control cock and third direction control cock are specially electronically controlled proportional valve.
7. the revolution hydraulic control system of getting on the bus according to claim 4 is characterized in that said rotary motor has normally closed rotary braking oil cylinder, and the working oil chamber of said rotary braking oil cylinder and system pressure are stablized between oil circuit and the oil return circuit and be provided with switch valve.
8. the revolution hydraulic control system of getting on the bus according to claim 7 is characterized in that said switch valve is specially the electric-controlled switch valve.
9. the revolution hydraulic control system of getting on the bus according to claim 4 is characterized in that, also comprises the main by pass valve that is arranged between system pressure oil circuit and the oil return circuit, and the precursor overflow valve of the pilot pressure of the main by pass valve of control; And, being provided with shuttle valve between two hydraulic fluid ports of said rotary motor, the oil outlet of said shuttle valve is communicated with the guide's hydraulic fluid port of said main by pass valve and the oil inlet of said precursor overflow valve.
10. hoisting crane, comprise the chassis with can be with respect to the turntable of getting on the bus of chassis gyroscopic movement; It is characterized in that, also comprise that the rotary motor output rotary motive power of the said revolution hydraulic control system of getting on the bus is to the turntable of getting on the bus like each described revolution liquid control system of getting on the bus in the claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205634908U CN202379608U (en) | 2011-12-29 | 2011-12-29 | Boarding rotating hydraulic control system and crane provided with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011205634908U CN202379608U (en) | 2011-12-29 | 2011-12-29 | Boarding rotating hydraulic control system and crane provided with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202379608U true CN202379608U (en) | 2012-08-15 |
Family
ID=46628126
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011205634908U Expired - Lifetime CN202379608U (en) | 2011-12-29 | 2011-12-29 | Boarding rotating hydraulic control system and crane provided with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202379608U (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102515025A (en) * | 2011-12-29 | 2012-06-27 | 徐州重型机械有限公司 | Superstructure rotary hydraulic control system and crane with same |
| CN103541944A (en) * | 2013-11-06 | 2014-01-29 | 徐州重型机械有限公司 | Rotation buffer valve, rotation buffer control device and crane rotation hydraulic system |
| CN103641023A (en) * | 2013-12-17 | 2014-03-19 | 徐州重型机械有限公司 | Control valve, hydraulic control system of winch brake and crane |
| CN103663196A (en) * | 2013-12-24 | 2014-03-26 | 徐州重型机械有限公司 | Crane and super-hoisting winching component hydraulic system |
| CN103912531A (en) * | 2013-01-07 | 2014-07-09 | 广西柳工机械股份有限公司 | Load sensing distribution valve for loader |
| CN107524661A (en) * | 2017-08-25 | 2017-12-29 | 武汉船用机械有限责任公司 | A kind of hydraulic system of rack-and-pinion lowering or hoisting gear |
| CN110294428A (en) * | 2019-07-04 | 2019-10-01 | 江苏徐工工程机械研究院有限公司 | A kind of closed rotary control system and crane |
| CN111439691A (en) * | 2020-04-17 | 2020-07-24 | 浙江三一装备有限公司 | Slewing device hydraulic control system and engineering machinery |
| CN113697696A (en) * | 2021-08-27 | 2021-11-26 | 浙江三一装备有限公司 | Crane rotation control method and system and crane |
-
2011
- 2011-12-29 CN CN2011205634908U patent/CN202379608U/en not_active Expired - Lifetime
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102515025A (en) * | 2011-12-29 | 2012-06-27 | 徐州重型机械有限公司 | Superstructure rotary hydraulic control system and crane with same |
| CN102515025B (en) * | 2011-12-29 | 2014-09-17 | 徐州重型机械有限公司 | Superstructure rotary hydraulic control system and crane with same |
| CN103912531A (en) * | 2013-01-07 | 2014-07-09 | 广西柳工机械股份有限公司 | Load sensing distribution valve for loader |
| CN103912531B (en) * | 2013-01-07 | 2016-03-16 | 广西柳工机械股份有限公司 | Loader load sensing distributing valve |
| CN103541944A (en) * | 2013-11-06 | 2014-01-29 | 徐州重型机械有限公司 | Rotation buffer valve, rotation buffer control device and crane rotation hydraulic system |
| CN103641023B (en) * | 2013-12-17 | 2016-04-27 | 徐州重型机械有限公司 | The hydraulic control system of control cock and hoist brake, hoisting crane |
| CN103641023A (en) * | 2013-12-17 | 2014-03-19 | 徐州重型机械有限公司 | Control valve, hydraulic control system of winch brake and crane |
| CN103663196A (en) * | 2013-12-24 | 2014-03-26 | 徐州重型机械有限公司 | Crane and super-hoisting winching component hydraulic system |
| CN103663196B (en) * | 2013-12-24 | 2016-06-29 | 徐州重型机械有限公司 | Crane and setting-up hoisting hydraulic system thereof |
| CN107524661A (en) * | 2017-08-25 | 2017-12-29 | 武汉船用机械有限责任公司 | A kind of hydraulic system of rack-and-pinion lowering or hoisting gear |
| CN110294428A (en) * | 2019-07-04 | 2019-10-01 | 江苏徐工工程机械研究院有限公司 | A kind of closed rotary control system and crane |
| CN111439691A (en) * | 2020-04-17 | 2020-07-24 | 浙江三一装备有限公司 | Slewing device hydraulic control system and engineering machinery |
| CN113697696A (en) * | 2021-08-27 | 2021-11-26 | 浙江三一装备有限公司 | Crane rotation control method and system and crane |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202379608U (en) | Boarding rotating hydraulic control system and crane provided with same | |
| CN201729610U (en) | Rotary hydraulic system of crane and crane | |
| CN102336370B (en) | Rotating hydraulic system of crane and control method thereof | |
| CN102588357B (en) | Load sensitive hydraulic system and crane with hydraulic system | |
| CN202612232U (en) | Hydraulic motor driving device and long spiral drilling machine main winch adopting same | |
| CN102887435B (en) | Hydraulic system for controlling amplitude variation of crane boom, control method and crane | |
| CN103244496B (en) | Rotary control valve group, revolution hydraulic control system and hoist | |
| CN102515025B (en) | Superstructure rotary hydraulic control system and crane with same | |
| CN102788055B (en) | Hydraulic system of wrecker | |
| CN103470565A (en) | Rotary cushion valve and rotary system for crane | |
| CN103613021B (en) | A kind of winding hydraulic control system and engineering machinery | |
| CN102491173B (en) | Crane and closed type hoisting negative power control system for crane | |
| CN104477800B (en) | Buffer control system of swing mechanism, buffer control method and crane | |
| CN202988618U (en) | Closed hydraulic circuit for controlling cantilever crane to rotate, and crane | |
| CN103922250B (en) | Working bucket leveling system and folding arm high-altitude operation vehicle | |
| CN202829340U (en) | Hydraulic system controlling boom to vary amplitude and crane | |
| CN106517019B (en) | Winch hydraulic control system | |
| CN103641023B (en) | The hydraulic control system of control cock and hoist brake, hoisting crane | |
| CN102431899B (en) | Super-lift winch control system and crane using the same | |
| CN201382036Y (en) | Multilevel speed control valve bank and crane applying same | |
| CN102465935B (en) | Pressure-compensated valve, load-sensitive hydraulic system and crane applying same | |
| CN113511601B (en) | Rotary hydraulic system, engineering machine and rotary control method | |
| CN104192739B (en) | Rotary system and hoisting crane | |
| CN202381430U (en) | Load-sensitive hydraulic system and crane with same | |
| CN101863421A (en) | Hydraulic operation triple pump hydraulic system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20120815 Effective date of abandoning: 20140917 |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20120815 Effective date of abandoning: 20140917 |
|
| RGAV | Abandon patent right to avoid regrant |