CN203532381U - Rotary cushion valve and rotary system of crane - Google Patents
Rotary cushion valve and rotary system of crane Download PDFInfo
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- CN203532381U CN203532381U CN201320602014.1U CN201320602014U CN203532381U CN 203532381 U CN203532381 U CN 203532381U CN 201320602014 U CN201320602014 U CN 201320602014U CN 203532381 U CN203532381 U CN 203532381U
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Abstract
The utility model discloses a rotary cushion valve and a rotary system of a crane, and relates to the technical field of engineering machines. The technical problems that in the prior art, a rotary mechanism can not operate when instantaneous pressure in the rotary system exceeds the set value of an overflow valve, so that a dynamic handle can not move after throttling up of the crane are solved. The rotary cushion valve comprises an oil inlet opening, an oil return opening, an oil circuit reversing valve, a first overflow valve, a second overflow valve, a first oil connecting opening and a second oil connecting opening. The oil circuit reversing valve is connected among the oil inlet opening, the oil return opening, the first oil connecting opening and the second oil connecting opening. An oil inlet port of the first overflow valve is connected to an oil circuit between the oil circuit reversing valve and the first oil connecting opening, and an oil outlet port of the first overflow valve and an oil outlet port of the second overflow valve are both communicated with the oil return opening. The rotary system of the crane comprises the rotary cushion valve. The rotary cushion valve and the rotary system of the crane are used for improving the rotary cushioning performance of the rotary system of the crane.
Description
Technical field
The utility model relates to technical field of engineering machinery, the rotary system that relates in particular to a kind of rotary buffering valve and the hoist of this rotary buffering valve is set.
Background technique
Wheeled crane be a kind of operational site unrestricted, can band carry or no-load condition under do not need trapped orbit and work, and rely on stress balance to keep stable jib-type crane.
Operation fine motion and revolution resiliency are the important technology performances of wheeled crane.Operation fine motion refers in crane operation process, is used for weighing the trickle degree that in the situation of the little opening of hydrovalve, operation can reach.Revolution resiliency refers to that handle returns meta, main valve turn-off transient, is used in the performance of of short duration release load and swirl gear inertia.
At present, crane rotation system mainly adopts following two kinds of methods:
1, adopt closed model pump control system, system fine motion and travelling comfort are good, and control accuracy is high, but cost is high;
2, adopt common gear pump to add slewing directional control valve and trimmer valve, on little tonnage hoist, use extensively, respond well.
Along with user requires the increasing of the weight of lifting and lifting altitude, more than large-tonnage 90t product arm is long, weight is large, during revolution, turn round moment of inertia large, therefore, those skilled in the art have adopted the first controlling method-closed model pump control system, system fine motion and travelling comfort are good, and control accuracy is high, but cost is high; 70 tons of following product revolution moment of inertia of little tonnage are less, by common gear pump, add the gentle valve that rushes of rotary valve and just can solve revolution fine motion, but current existing rotary buffering valve exists, and weight is heavier, after junction plane easy oil leakage and first open out, the problems such as active handle revolution attonity.
In order to improve operation fine motion and the revolution resiliency of wheeled crane, in prior art, provide following two kinds of technological schemes as depicted in figs. 1 and 2:
Technological scheme 1:
As shown in Figure 1, the hydraulic oil of gear pump output enters into rotary motor through slewing directional control valve, and high pressure liquid force feed drives rotary motor to rotate to drive swirl gear to carry out work.When rotary system instantaneous pressure is too high and reach relief valve setting value, rotary motor filler opening, return opening communicate, and play the effect of revolution buffering; When rotary motor is driven by external force, one-way valve can form oil supply loop and carry out repairing, avoids motor to occur that negative pressure produces cavitation phenomenon.
Technological scheme 2:
As shown in Figure 2, pressure oil, from oil inlet P oil-feed, then enters into rotary motor through slewing directional control valve, drives swirl gear to carry out work, and wherein main relief valve 4 plays safety valve effect in rotary system, and precursor overflow valve 5 is controlled the pilot pressure of main relief valve; From pressure oil circuit, get pilot control, after electric proportional pressure-reducing valve 2 decompressions, control the commutation of slewing directional control valve main valve plug 3; By control cab electricity ratio handle, export different control signals, control the different pilot pressure oil of electric proportional pressure-reducing valve 2 outputs, thereby control rotating commutation and obtain different rotating speed.Rotary buffering valve 1 is comprised of four one-way valves and a pilot operated compound relief valve, from the load feedback mouth XL mouth of slewing directional control valve, get guide oil and carry out controlling water kick valve pilot port, when rotary system instantaneous pressure is too high and reach relief valve setting value, rotary motor filler opening, return opening communicate, and play the effect of revolution buffering.
In prior art at least there is following technical problem in technological scheme 1:
1., in the ban after open out, during active handle, moment system pressure too high and reach relief valve setting value, now rotary motor filler opening, recycle muzzle pressure equate, there will be the fault that turns motionless;
2., rotary buffering valve is comprised of main valve body and former and later two transition plates, because main valve body and transition plate are cast member, so easily there is oil leakage fault in the junction plane between transition plate and main valve body, and weight is heavier;
In prior art at least there is following technical problem in technological scheme 2:
1., a whole set of rotary system cost is higher, on medium and small tonnage hoist, has cost inferior position;
2., swirl gear must have mechanical braking, if machinery-free braking, the trend that rotary motor remains in operation because inertia has when handle returns meta.
Model utility content
The purpose of this utility model is the rotary system that proposes a kind of rotary buffering valve and the hoist of this rotary buffering valve is set, when having solved prior art and existing instantaneous pressure in rotary system to surpass the setting value of relief valve, swirl gear cannot turn round, cause hoist to exist after first open out, the technical problem of active handle attonity.The utility model optimal technical scheme has also at least solved prior art and has had that weight is heavier, junction plane is prone to the technical problems such as leakage of oil.
For achieving the above object, the utility model provides following technological scheme:
The rotary buffering valve that the utility model embodiment provides, comprises filler opening, return opening, oil circuit selector valve, the first relief valve, the second relief valve, the first logical hydraulic fluid port and the second logical hydraulic fluid port, wherein:
Described oil circuit selector valve is connected between described filler opening, described return opening, the described first logical hydraulic fluid port and the described second logical hydraulic fluid port;
Described oil circuit selector valve is when the first state, and described filler opening is connected with the described first logical hydraulic fluid port by described oil circuit selector valve, and described return opening is connected with the described second logical hydraulic fluid port by described oil circuit selector valve;
Described oil circuit selector valve is when the second state, and described filler opening is connected with the described second logical hydraulic fluid port by described oil circuit selector valve, and described return opening is connected with the described first logical hydraulic fluid port by described oil circuit selector valve;
Described oil circuit selector valve is when the third state, and described oil circuit selector valve ends;
The oil-feed port of described the first relief valve is connected on the oil circuit between described oil circuit selector valve and the described first logical hydraulic fluid port, the oil-feed port of described the second relief valve is connected on the oil circuit between described oil circuit selector valve and the described second logical hydraulic fluid port, and the fuel-displaced port of described the first relief valve is all connected with described return opening with the fuel-displaced port of described the second relief valve.
At one preferably or alternatively in embodiment, after the fuel-displaced port parallel connection of the fuel-displaced port of described the first relief valve and described the second relief valve, by double linked one-way valve, be connected with described return opening.
At one, preferably or alternatively in embodiment, described rotary buffering valve also comprises the first one-way valve and the second one-way valve, wherein:
The fuel-displaced port of described the first one-way valve is connected on the oil circuit between described oil circuit selector valve and the described first logical hydraulic fluid port, and the oil-feed port of described the first one-way valve is connected in the fuel-displaced port of described double linked one-way valve and described the first relief valve, on the oil circuit between the fuel-displaced port of described the second relief valve;
The fuel-displaced port of described the second one-way valve is connected on the oil circuit between described oil circuit selector valve and the described second logical hydraulic fluid port, and the oil-feed port of described the second one-way valve is connected in the fuel-displaced port of described double linked one-way valve and described the first relief valve, on the oil circuit between the fuel-displaced port of described the second relief valve.
At one, preferably or alternatively in embodiment, described the first relief valve and the second relief valve are bypass type relief valve, and described rotary buffering valve also comprises bypass selector valve, wherein:
Described the first relief valve and described the second relief valve draining port separately are all connected with fuel tank;
After the bypass hydraulic fluid port of described the first relief valve is in parallel with the bypass hydraulic fluid port of described the second relief valve, be connected with the oil inlet end of described bypass selector valve;
Both are connected the oil-feed port of described the first one-way valve and the oil-feed port of described the second one-way valve with the oil outlet end of described filler opening, described bypass selector valve with the oil circuit between described double linked one-way valve;
Described bypass selector valve when the first state, the oil circuit conducting between the oil inlet end of described bypass selector valve and its oil outlet end, described bypass selector valve when the second state, the cut-off of oil circuit between the oil inlet end of described bypass selector valve and its oil outlet end.
At one, preferably or alternatively in embodiment, described the first relief valve and described the second relief valve bypass hydraulic fluid port are separately connected with the oil inlet end of described bypass selector valve by different bypass one-way valves respectively; Or the bypass hydraulic fluid port of described the first relief valve and the bypass hydraulic fluid port of described the second relief valve are connected with two oil-feed ports of shuttle valve respectively, the fuel-displaced port of described shuttle valve is connected with the oil inlet end of described bypass selector valve.
At one, preferably or alternatively in embodiment, both are connected the oil-feed port of described the first one-way valve and the oil-feed port of described the second one-way valve by bypass relief valve with described bypass selector valve with the oil circuit between described double linked one-way valve.
At one, preferably or alternatively in embodiment, described bypass selector valve is solenoid directional control valve, and described bypass relief valve is plug-in overflow valve.
At one, preferably or alternatively in embodiment, described oil circuit selector valve is pilot operated directional control valve or solenoid directional control valve.
At one, preferably or alternatively in embodiment, described rotary buffering valve comprises front transition plate, rear transition plate and main valve body, wherein:
Described filler opening and described return opening are all arranged on described front transition plate, and the described first logical hydraulic fluid port and the described second logical hydraulic fluid port are all arranged on described main valve body;
Described front transition plate, described rear transition plate and described main valve body are integral type structure.
The rotary system of the hoist that the utility model embodiment provides, comprises the rotary buffering valve that the arbitrary technological scheme of rotary motor and the utility model provides, wherein:
One of them is connected the filler opening of described rotary motor and the oil outlet of described rotary motor with the described first logical hydraulic fluid port, and wherein another is connected with the described second logical hydraulic fluid port the filler opening of described rotary motor with the oil outlet of described rotary motor.
Based on technique scheme, the utility model embodiment at least can produce following technique effect:
When the rotary buffering valve providing as the utility model embodiment is applied to the rotary system of hoist, make the first logical hydraulic fluid port of rotary buffering valve, the second logical hydraulic fluid port is all connected with rotary motor, rotary system moment system pressure is too high and reach the first relief valve, during the setting value of the second relief valve, hydraulic oil is through the first relief valve, after the second relief valve, flow back into fuel tank, rather than rotary motor filler opening as prior art, return opening communicates, so swirl gear cannot turn round when having solved prior art and existing instantaneous pressure in rotary system to surpass the setting value of relief valve, cause hoist to exist after first open out, the technical problem of active handle attonity.
In addition, the optimal technical scheme that the utility model provides compared with prior art at least can produce following technique effect:
1, in the utility model the front transition plate of rotary buffering valve, rear transition plate and main valve body for casting or the integrated type that is stamped to form (or claim: integral type) structure, valve body structure is compact, weight is lighter;
2, a whole set of rotary system cost is lower, on medium and small tonnage hoist, has price advantage;
3, subelement adopt plug-in type (for example: plug-in overflow valve), rotary buffering valve function admirable.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide further understanding of the present utility model, forms the application's a part, and schematic description and description of the present utility model is used for explaining the utility model, does not form improper restriction of the present utility model.In the accompanying drawings:
The oil circuit schematic diagram of the technological scheme 1 that Fig. 1 provides for prior art;
The oil circuit schematic diagram of the technological scheme 2 that Fig. 2 provides for prior art;
The schematic diagram of annexation between the rotary buffering valve that a kind of mode of execution that Fig. 3 is the utility model embodiment provides and rotary motor;
The schematic diagram of annexation between the rotary buffering valve that the another kind of mode of execution that Fig. 4 is the utility model embodiment provides and rotary motor;
The schematic diagram of annexation between the rotary buffering valve that another mode of execution that Fig. 5 is the utility model embodiment provides and rotary motor;
Reference character: 1, rotary buffering valve; 2, reduction valve; 3, main valve plug; 4, main relief valve; 5, precursor overflow valve; 60, bypass one-way valve; 61, rotary motor; 62, bypass selector valve; 63, oil circuit selector valve; 64, bypass relief valve; 651, the first relief valve; 652, the second relief valve; 661, the first one-way valve; 662, the second one-way valve; 67, double linked one-way valve; 68, fuel tank; 69, shuttle valve; P, filler opening; T, return opening; A, the first logical hydraulic fluid port; B, the second logical hydraulic fluid port; A, control mouthful; B, control mouthful.
Embodiment
Can understand the distinctive points between content of the present utility model and the utility model and prior art with reference to accompanying drawing Fig. 1～Fig. 5 and word content below.Below, by accompanying drawing and the mode of enumerating optional embodiments more of the present utility model, the technical solution of the utility model (comprising optimal technical scheme) is described in further detail.It should be noted that: any technical characteristics in the present embodiment, any technological scheme is all the technical characteristics of plurality of optional or one or more in optional technological scheme, cannot exhaustive all alternative technical characteristicss of the present utility model and alternative technological scheme in order to describe succinct need in presents, also the mode of execution that is not easy to each technical characteristics all emphasizes that it is one of optional numerous embodiments, so those skilled in the art should know: arbitrary technological means that the utility model can be provided is replaced or any two or more technological means or technical characteristics that the utility model is provided combine mutually and obtain new technological scheme.Any technical characteristics in the present embodiment and any technological scheme all do not limit protection domain of the present utility model, protection domain of the present utility model should comprise those skilled in the art do not pay creative work thinkable any alternate embodiments and those skilled in the art any two or more technological means that the utility model is provided or technical characteristics combine mutually and the new technological scheme that obtains.
When the utility model embodiment provides the setting value that instantaneous pressure in a kind of oil-way system surpasses relief valve, the rotary buffering valve that swirl gear can turn round and the rotary system that the hoist of this rotary buffering valve is set.
Technological scheme the utility model being provided below in conjunction with Fig. 3～Fig. 5 is carried out more detailed elaboration.
As shown in Fig. 3～Fig. 5, the rotary buffering valve that the utility model embodiment provides, comprise that oil inlet P, oil return inlet T, oil circuit selector valve (being preferably pilot operated directional control valve) 63, the first relief valve 651, second relief valve 652(the first relief valve 651, the second relief valve 652 are all preferably bypass type relief valve), the first logical hydraulic fluid port A and the second logical hydraulic fluid port B, wherein:
Oil circuit selector valve 63 is connected between oil inlet P, oil return inlet T, the first logical hydraulic fluid port A and the second logical hydraulic fluid port B.Oil circuit selector valve 63 in the first state (for example: in the time of left position in Fig. 3), oil inlet P is connected with the first logical hydraulic fluid port A by oil circuit selector valve 63, and oil return inlet T is connected with the second logical hydraulic fluid port B by oil circuit selector valve 63.
Oil circuit selector valve 63 in the second state (for example: in the time of right position in Fig. 3), oil inlet P is connected with the second logical hydraulic fluid port B by oil circuit selector valve 63, and oil return inlet T is connected with the first logical hydraulic fluid port A by oil circuit selector valve 63.
Oil circuit selector valve 63 in the third state (for example: in the time of meta in Fig. 3), oil circuit selector valve 63 ends.
The oil-feed port of the first relief valve 651 is connected on the oil circuit between oil circuit selector valve 63 and the first logical hydraulic fluid port A, the oil-feed port of the second relief valve 652 is connected on the oil circuit between oil circuit selector valve 63 and the second logical hydraulic fluid port B, and the fuel-displaced port of the first relief valve 651 is all connected with oil return inlet T with the fuel-displaced port of the second relief valve 652.
When the pressure of the hydraulic oil of oil inlet P input surpasses the setting value of the first relief valve 651 or the second relief valve 652, hydraulic oil can flow out to reach the object of off-load through the first relief valve 651 or the second relief valve 652 from oil return inlet T.
In Fig. 3, K mouth is that technique is stifled, does not carry out any pipeline connection.
As preferably a kind of or mode of execution alternatively, after the fuel-displaced port parallel connection of the fuel-displaced port of the first relief valve 651 and the second relief valve 652, by double linked one-way valve 67, be connected with oil return inlet T.
Double linked one-way valve 67 can produce certain back pressure value in the return line of rotary system that this rotary buffering valve is set, and prevents that in turning course, jitter phenomenon produces, thereby guarantees the stationarity of revolution operation.
As preferably a kind of or mode of execution alternatively, rotary buffering valve also comprises the first one-way valve 661 and the second one-way valve 662, wherein:
The fuel-displaced port of the first one-way valve 661 is connected on the oil circuit between oil circuit selector valve 63 and the first logical hydraulic fluid port A, and the oil-feed port of the first one-way valve 661 is connected in the fuel-displaced port of double linked one-way valve 67 and the first relief valve 651, on the oil circuit between the fuel-displaced port of the second relief valve 652.
The fuel-displaced port of the second one-way valve 662 is connected on the oil circuit between oil circuit selector valve 63 and the second logical hydraulic fluid port B, and the oil-feed port of the second one-way valve 662 is connected in the fuel-displaced port of double linked one-way valve 67 and the first relief valve 651, on the oil circuit between the fuel-displaced port of the second relief valve 652.
When rotary motor 61 is driven by external force, the first one-way valve 661 or the second one-way valve 662 can form oil supply loop to rotary motor 61 fuel feeding, avoid rotary motor 61 to produce cavitation erosion.
As preferably a kind of or mode of execution alternatively, the first relief valve 651 and the second relief valve 652 are all preferably bypass type relief valve, and rotary buffering valve also comprises bypass selector valve 62, wherein:
The first relief valve 651 and the second relief valve 652 draining port separately are all connected with fuel tank 68, are preferably: after both parallel connections of the draining port of the draining port of the first relief valve 651 and the second relief valve 652, be connected with fuel tank 68.
The first relief valve 651 and the second relief valve 652 bypass hydraulic fluid port separately are all connected with the oil inlet end of bypass selector valve 62.Be preferably: after both parallel connections of the bypass hydraulic fluid port of the bypass hydraulic fluid port of the first relief valve 651 and the second relief valve 652, be connected with the oil inlet end of bypass selector valve 62.
Both are connected the oil-feed port of the oil-feed port of the first one-way valve 661 and the second one-way valve 662 with the oil outlet end of oil inlet P, bypass selector valve 62 with the oil circuit between double linked one-way valve 67.
For there being the electric situation that obtains of an independent fingertip control bypass selector valve 62 on the Joystick of pilot oil way reversing valve 63 working staties, when weight is during in oblique pull state, this bypass selector valve 62 needs to such an extent that conduct and switch to left position state from the state of right position shown in Fig. 3, rotary system, in freely transferring state, is realized aligning of weight.
As preferably a kind of or mode of execution alternatively, the bypass hydraulic fluid port of the bypass hydraulic fluid port of the first relief valve 651 and the second relief valve 652 is connected with the oil inlet end of bypass selector valve 62 by different bypass one-way valves 60 respectively as shown in Figure 3 and Figure 4.
Certainly, the replacement scheme of above-mentioned mode of execution, the first relief valve 651 and the second relief valve 652 bypass hydraulic fluid port separately also can be connected with two oil-feed ports of shuttle valve 69 respectively as shown in Figure 5, and the fuel-displaced port of shuttle valve 69 is connected with the oil inlet end of bypass selector valve 62.
Two bypass one-way valves 60 are identical with the effect of shuttle valve 69, all play the effect of conducting oil circuit, damping hole below can increase the resistance of the hydraulic oil of the first relief valve 651 and the bypass hydraulic fluid port output separately of the second relief valve 652, plays the effect of buffering, voltage stabilizing.。
As preferably a kind of or mode of execution alternatively, bypass selector valve 62 is connected with the oil circuit between double linked one-way valve 67 with the oil-feed port of oil inlet P, the first one-way valve 661 and the oil-feed port of the second one-way valve 662 by bypass relief valve 64.
During 62 conducting of bypass selector valve, the hydraulic oil of bypass hydraulic fluid port separately of the first relief valve 651 and the second relief valve 652 output can flow into fuel tanks through double linked one-way valve 67 while surpassing the scheduled pressure value of bypass relief valve 64.Now, the load of hoist is in layback state, rotary motor 61 with and the swirl gear that driven can realize automatic alignment.
As preferably a kind of or mode of execution alternatively, bypass selector valve 62 is solenoid directional control valve, and bypass relief valve 64 is plug-in overflow valve.The non-one-way valve directly processing at valve inner of relief valve of the type, so just can avoid due to the fault of processing and assembly error causes spool clamping stagnation to bring.
As preferably a kind of or mode of execution alternatively, oil circuit selector valve 63 can be pilot operated directional control valve or as shown in Figure 4 solenoid directional control valve as shown in Figure 3.
The selector valve of above two types all can be realized the control to oil circuit between oil inlet P, oil return inlet T, the first logical hydraulic fluid port A and the second logical hydraulic fluid port B.Certainly, use other valves with the technological scheme that substitutes above-mentioned valve also within protection domain of the present utility model.
As preferably a kind of or mode of execution alternatively, rotary buffering valve comprises front transition plate, rear transition plate and main valve body, wherein:
Oil inlet P and oil return inlet T are all arranged on front transition plate, and the first logical hydraulic fluid port A and the second logical hydraulic fluid port B are all arranged on main valve body.
Front transition plate, rear transition plate and main valve body are integral type structure.
This structure has compact structure, the advantage that hydraulic oil seal is good.
As shown in Fig. 3～Fig. 5, the rotary system of the hoist that the utility model embodiment provides, comprises the rotary buffering valve that the arbitrary technological scheme of rotary motor 61 and the utility model provides, wherein:
This hoist is preferably wheeled crane.One of them is connected the first logical hydraulic fluid port A and the filler opening of rotary motor 61 and the oil outlet of rotary motor 61, and second leads to hydraulic fluid port B and the filler opening of rotary motor 61 and the oil outlet of rotary motor 61, and wherein another is connected.
When the first logical hydraulic fluid port of rotary buffering valve, the second logical hydraulic fluid port are all connected with rotary motor 61, rotary system moment system pressure is too high and while reaching relief valve setting value, hydraulic oil flow back into fuel tank through the first relief valve 651, the second relief valve 652, rather than the return opening of the filler opening of rotary motor 61, rotary motor 61 communicates, can avoid thus rotary motor 61 to rotate and cause the phenomenon of first open out, rear active handle attonity to occur.
As shown in Fig. 3～Fig. 5, concentrate the working procedure of the rotary system that the hoist that the utility model provides is described below:
1, when swirl gear does not carry out any action, now pilot operated directional control valve is in closed condition, and oil inlet P and oil return inlet T mouth communicate, and fluid is directly from the meta off-load of oil circuit selector valve 63 as shown in Figure 3;
2, when pulling Joystick, guide oil enters the control mouth a of oil circuit selector valve (being preferably pilot operated directional control valve) 63 or controls a mouthful b, drive oil circuit selector valve 63 to commutate, hydraulic oil enters into rotary motor 61 through oil circuit selector valve 63, drives swirl gear to carry out work; When instantaneous pressure is too high and reach relief valve setting value, fluid is directly laid down from oil return inlet T through the first relief valve 651, the second relief valve 652, plays the effect of revolution buffering;
3, when load is during in layback state, press bypass selector valve 62(and be preferably solenoid directional control valve) switch, make 62 conductings of bypass selector valve, swirl gear automatic alignment.On Joystick, have an independent fingertip control solenoid directional control valve electric situation, when weight is during in oblique pull state, this solenoid valve needs electricly, rotary system, in freely transferring state, is realized aligning of weight.
The load of hoist is when layback state, and because the break of rotary system is open type, rotary motor 61 is in passive stress; When solenoid directional control valve obtain electric after, rotary motor 61 high side pressure oil are by i.e. bypass selector valve 62 off-loads as shown in Figure 3 of solenoid directional control valve, the filler opening of rotary motor 61, oil outlet are in pressure balance; Arm center line place plane goes to weight center of gravity when top, in to positive status.
Above-mentioned arbitrary technological scheme disclosed in the utility model unless otherwise stated, if it discloses number range, so disclosed number range is preferred number range, any it should be appreciated by those skilled in the art: preferred number range is only the obvious or representative numerical value of technique effect in many enforceable numerical value.Because numerical value is more, cannot be exhaustive, so the utility model just discloses part numerical value to illustrate the technical solution of the utility model, and the above-mentioned numerical value of enumerating should not form the restriction of the utility model being created to protection domain.
If used the words such as " first ", " second " to limit component herein, those skilled in the art should know: the use of " first ", " second " is only used to be convenient to describe above component are distinguished as not having outside Stated otherwise, and above-mentioned word does not have special implication.
Simultaneously, if above-mentioned the utility model discloses or has related to component or the structural member of connection fastened to each other, so, unless otherwise stated, be fixedly connected with and can be understood as: can dismantle and be fixedly connected with (for example using bolt or screw to connect), also can be understood as: non-removable being fixedly connected with (for example rivet, weld), certainly, connection fastened to each other also can for example, be replaced (obviously cannot adopt except integrally formed technique) by integral type structure (use casting technique is integrally formed to be created).
In addition, in the disclosed arbitrary technological scheme of above-mentioned the utility model applied for the term that represents state relation or shape unless otherwise stated its implication comprise and its approximate, similar or approaching state or shape.Arbitrary parts that the utility model provides can be both to be assembled by a plurality of independent constituent elements, the produced separate part of the technique that also can be one of the forming.
Finally should be noted that: above embodiment is only in order to illustrate that the technical solution of the utility model is not intended to limit; Although the utility model is had been described in detail with reference to preferred embodiment, those of ordinary skill in the field are to be understood that: still can modify or part technical characteristics is equal to replacement embodiment of the present utility model; And not departing from the spirit of technical solutions of the utility model, it all should be encompassed in the middle of the technological scheme scope that the utility model asks for protection.
Claims (10)
1. a rotary buffering valve, is characterized in that, comprises filler opening, return opening, oil circuit selector valve, the first relief valve, the second relief valve, the first logical hydraulic fluid port and the second logical hydraulic fluid port, wherein:
Described oil circuit selector valve is connected between described filler opening, described return opening, the described first logical hydraulic fluid port and the described second logical hydraulic fluid port;
Described oil circuit selector valve is when the first state, and described filler opening is connected with the described first logical hydraulic fluid port by described oil circuit selector valve, and described return opening is connected with the described second logical hydraulic fluid port by described oil circuit selector valve;
Described oil circuit selector valve is when the second state, and described filler opening is connected with the described second logical hydraulic fluid port by described oil circuit selector valve, and described return opening is connected with the described first logical hydraulic fluid port by described oil circuit selector valve;
Described oil circuit selector valve is when the third state, and described oil circuit selector valve ends;
The oil-feed port of described the first relief valve is connected on the oil circuit between described oil circuit selector valve and the described first logical hydraulic fluid port, the oil-feed port of described the second relief valve is connected on the oil circuit between described oil circuit selector valve and the described second logical hydraulic fluid port, and the fuel-displaced port of described the first relief valve is all connected with described return opening with the fuel-displaced port of described the second relief valve.
2. rotary buffering valve according to claim 1, is characterized in that, after the fuel-displaced port parallel connection of the fuel-displaced port of described the first relief valve and described the second relief valve, by double linked one-way valve, is connected with described return opening.
3. rotary buffering valve according to claim 2, is characterized in that, described rotary buffering valve also comprises the first one-way valve and the second one-way valve, wherein:
The fuel-displaced port of described the first one-way valve is connected on the oil circuit between described oil circuit selector valve and the described first logical hydraulic fluid port, and the oil-feed port of described the first one-way valve is connected in the fuel-displaced port of described double linked one-way valve and described the first relief valve, on the oil circuit between the fuel-displaced port of described the second relief valve;
The fuel-displaced port of described the second one-way valve is connected on the oil circuit between described oil circuit selector valve and the described second logical hydraulic fluid port, and the oil-feed port of described the second one-way valve is connected in the fuel-displaced port of described double linked one-way valve and described the first relief valve, on the oil circuit between the fuel-displaced port of described the second relief valve.
4. rotary buffering valve according to claim 3, is characterized in that, described the first relief valve and the second relief valve are bypass type relief valve, and described rotary buffering valve also comprises bypass selector valve, wherein:
Described the first relief valve and described the second relief valve draining port separately are all connected with fuel tank;
After the bypass hydraulic fluid port of described the first relief valve is in parallel with the bypass hydraulic fluid port of described the second relief valve, be connected with the oil inlet end of described bypass selector valve;
Both are connected the oil-feed port of described the first one-way valve and the oil-feed port of described the second one-way valve with the oil outlet end of described filler opening, described bypass selector valve with the oil circuit between described double linked one-way valve;
Described bypass selector valve when the first state, the oil circuit conducting between the oil inlet end of described bypass selector valve and its oil outlet end, described bypass selector valve when the second state, the cut-off of oil circuit between the oil inlet end of described bypass selector valve and its oil outlet end.
5. rotary buffering valve according to claim 4, is characterized in that, described the first relief valve and described the second relief valve bypass hydraulic fluid port are separately connected with the oil inlet end of described bypass selector valve by different bypass one-way valves respectively; Or the bypass hydraulic fluid port of described the first relief valve and the bypass hydraulic fluid port of described the second relief valve are connected with two oil-feed ports of shuttle valve respectively, the fuel-displaced port of described shuttle valve is connected with the oil inlet end of described bypass selector valve.
6. rotary buffering valve according to claim 5, it is characterized in that, both are connected the oil-feed port of described the first one-way valve and the oil-feed port of described the second one-way valve by bypass relief valve with described bypass selector valve with the oil circuit between described double linked one-way valve.
7. rotary buffering valve according to claim 6, is characterized in that, described bypass selector valve is solenoid directional control valve, and described bypass relief valve is plug-in overflow valve.
8. according to the arbitrary described rotary buffering valve of claim 1-7, it is characterized in that, described oil circuit selector valve is pilot operated directional control valve or solenoid directional control valve.
9. according to the arbitrary described rotary buffering valve of claim 1-7, it is characterized in that, described rotary buffering valve comprises front transition plate, rear transition plate and main valve body, wherein:
Described filler opening and described return opening are all arranged on described front transition plate, and the described first logical hydraulic fluid port and the described second logical hydraulic fluid port are all arranged on described main valve body;
Described front transition plate, described rear transition plate and described main valve body are integral type structure.
10. a rotary system for hoist, is characterized in that, comprises the arbitrary described rotary buffering valve of rotary motor and claim 1-9, wherein:
One of them is connected the filler opening of described rotary motor and the oil outlet of described rotary motor with the described first logical hydraulic fluid port, and wherein another is connected with the described second logical hydraulic fluid port the filler opening of described rotary motor with the oil outlet of described rotary motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320602014.1U CN203532381U (en) | 2013-09-24 | 2013-09-24 | Rotary cushion valve and rotary system of crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320602014.1U CN203532381U (en) | 2013-09-24 | 2013-09-24 | Rotary cushion valve and rotary system of crane |
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| Publication Number | Publication Date |
|---|---|
| CN203532381U true CN203532381U (en) | 2014-04-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320602014.1U Withdrawn - After Issue CN203532381U (en) | 2013-09-24 | 2013-09-24 | Rotary cushion valve and rotary system of crane |
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| Country | Link |
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| CN (1) | CN203532381U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103470565A (en) * | 2013-09-24 | 2013-12-25 | 徐州重型机械有限公司 | Rotary cushion valve and rotary system for crane |
| CN108626193A (en) * | 2018-05-18 | 2018-10-09 | 宁波真格液压科技有限公司 | A kind of cartridge valve |
-
2013
- 2013-09-24 CN CN201320602014.1U patent/CN203532381U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103470565A (en) * | 2013-09-24 | 2013-12-25 | 徐州重型机械有限公司 | Rotary cushion valve and rotary system for crane |
| CN108626193A (en) * | 2018-05-18 | 2018-10-09 | 宁波真格液压科技有限公司 | A kind of cartridge valve |
| CN108626193B (en) * | 2018-05-18 | 2020-08-07 | 台州市路桥区嘉伟鞋帽厂 | Plug-in type valve |
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