CN102022516B - Wheeled crane and chassis hydraulic control system thereof - Google Patents
Wheeled crane and chassis hydraulic control system thereof Download PDFInfo
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- CN102022516B CN102022516B CN 201010591063 CN201010591063A CN102022516B CN 102022516 B CN102022516 B CN 102022516B CN 201010591063 CN201010591063 CN 201010591063 CN 201010591063 A CN201010591063 A CN 201010591063A CN 102022516 B CN102022516 B CN 102022516B
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Abstract
The invention discloses a chassis hydraulic control system which is used for controlling action of a first chassis actuating element. The system comprises a first directional control valve and an energy accumulator, wherein, the first directional control valve is used for controlling communication between an operating oil port of the first chassis actuating element and a pressure oil passage or a return oil passage of the system; and an operating oil port of the energy accumulator is communicated with an oil inlet of the first directional control valve. Preferably, the system further comprises a first pressure relay and a second pressure relay which are used for acquiring the pressure of the operating oil port of the energy accumulator, wherein, the pre-determined pressure of the first pressure relay is less than that of the second pressure relay. In the invention, by means of hydraulic control, the operating pressure which meets the need of a differential lock oil cylinder can be output; and owing to small compression ratio of hydraulic oil, the actuating element achieves timely and accurate action response without load influence during the operation process, thus ensuring timely and effective differential control. On the basis, the invention further provides a wheeled crane with the chassis hydraulic control system.
Description
Technical field
The present invention relates to technical field of engineering machinery, be specifically related to a kind of wheeled crane and chassis hydraulic control system thereof.
Background technique
The transmission principle of engineering machinery wheel undercarriage is roughly the same, driving source ultromotivity element output, through clutch to gearbox, after retarder exports ransaxle to; If drive form is a rear wheel drive, then export rear axle reductor to through transmission shaft.If the four-wheel drive form, then the gearbox in the Transmitted chains is set up two ransaxle power connections by taking off the bridge cylinder.
Under travelling state, do equidistantly not travel with the form of pure rolling as far as possible for the wheel of guaranteeing the vehicle bridge both sides, reduce the friction on tire and ground, for each ransaxle, require in theory in the time of the semiaxis transferring power of both sides, allow the both sides semiaxis with different rotating speed rotations.The available technology adopting differential mechanism has been realized above-mentioned function needs of taking turns a differential, and in the working procedure, by the stretching out or operate of control differential lock, the adjustment differential mechanism switches between differential state and non-differential state; That is to say, be in the differential state when differential lock is opened, be in non-differential state when differential lock is closed.
Particularly, the control mode of differential is mainly decided by the driving mode of axle-differential lock between wheel, the driving mode of existing axle-differential lock can be divided into Pneumatic-control type and electric-controlled type, and wherein, Pneumatic-control type is used comparatively general in existing engineering machinery wheel undercarriage control system.See also Fig. 1, this figure is the schematic diagram of Pneumatic-control type chassis control system.
As shown in Figure 1, this system has formed a simple commonly used atmospheric control as control unit, pneumatic differential lock 7a as executive component as Detecting element, solenoid directional control valve 6a as dynamical element, warning light switch 3a by gas cylinder 5a, is used for differential control between vehicle wheel.When opening discrepancy switch, solenoid directional control valve 6a gets TURP and changes to working position, and the pressurized air among the gas cylinder 5a enters pneumatic differential lock 7a by solenoid directional control valve and promotes the action of cylinder bar, and this moment, differential lock was opened; When closing discrepancy switch, solenoid directional control valve 6a dead electricity is returned to down working position, disconnects between gas cylinder 5a and the pneumatic differential lock 7, and the differential lock return is closed.In addition, elements such as the air compressor 1a of this system, air drier 2a, sequence valve 4a, gas cylinder 5a are formed an air compensating system, can manually carry out tonifying Qi to gas cylinder.Open air compressor 1a, pressurized air carries out tonifying Qi by air drier 2a, sequence valve 4a to gas cylinder 5a.After finishing, tonifying Qi closes air compressor.
Yet because air has compressibility, the action of pneumatic difference band lock is subject to the variation of load and changes; Therefore, be subjected to the restriction of himself working principle, this atmospheric control has the following disadvantages in the practical process of reality:
One moves inaccurate.When load was low, the action of pneumatic differential lock was more timely, and when load was higher, retardation phenomenon just can appear in the action of pneumatic differential lock, and differential control is untimely, has the inaccurate defective of action.
Its two, move not steady.Pneumatic differential lock is when low-speed motion, because frictional force accounts for the large percentage of thrust, the low-speed stability of pneumatic differential lock is lower.
Its three, pneumatic differential lock ouput force is little.
In addition, this atmospheric control does not possess pressure self compensation function, and newspaper indication warning lamp is bright in the time of the gas cylinder underpressure, and need manually-operable that gas cylinder is carried out tonifying Qi this moment, otherwise system can't proper functioning.Operate comparatively loaded down with trivial details.
For the wheel undercarriage control system of four-wheel drive form, it takes off bridge cylinder control gearbox by control and takes off bridge, makes vehicle switch between two-wheel drive and two kinds of drive forms of four-wheel drive.Specifically, when taking off the bridge cylinder and obtain hydrodynamic pressure and promote the action of cylinder bar, can make the disconnection that is in transmission connection of gearbox and bridge, thereby play the bridge effect of taking off; Hydrodynamic pressure recovers, and then takes off the bridge cylinder and resets and be in coupled condition.Take off the bridge driving mode in the prior art and also be Pneumatic-control type, exist the above-mentioned defective of differential lock pneumatic control system equally.
In view of this, demand urgently being optimized design, effectively to overcome the above-mentioned defective that prior art exists at existing chassis control system.
Summary of the invention
At above-mentioned defective, the technical problem that the present invention solves is, a kind of chassis hydraulic control system is provided, and on the basis of the action degree of accuracy that effectively improves corresponding controlling component, stationarity, has improved output action power greatly.On this basis, the present invention also provides a kind of wheeled crane with this chassis hydraulic control system.
Chassis provided by the invention hydraulic control system is used to control the action of the first chassis executive component; This system comprises first direction control valve and accumulator; Wherein, described first direction control valve is used to control the actuator port of the described first chassis executive component and being communicated with of system pressure oil circuit or oil return circuit; The actuator port of described accumulator is communicated with the filler opening of described first direction control valve.
Preferably, also comprise dynamical element and second direction control valve; Wherein, described dynamical element is used for delivery pressure fluid to the system pressure oil circuit, and described second direction control valve is used to control the oil outlet of described dynamical element and being communicated with of system pressure oil circuit or oil return circuit.
Preferably, also comprise and be used to control described second direction control valve to oil circuit conducting between the accumulator or non-conduction third direction control valve; And the path between described dynamical element and described second direction control valve has the bypath system interface.
Preferably, also comprise first reduction valve that is arranged on the path of described third direction control valve between the actuator port of described accumulator, and be arranged on the actuator port of described accumulator and first relief valve between the oil return circuit; And the set pressure of described first reduction valve is less than the set pressure of described first relief valve.
Preferably, also comprise first pressure relay and second pressure relay of the actuator port pressure that is used to gather described accumulator, and the predetermined pressure of described first pressure relay is less than the predetermined pressure of second pressure relay; The actuator port pressure of described accumulator is less than the predetermined pressure of first pressure relay, first pressure relay outputs control signals to described second direction control valve and described third direction control valve, the path between described dynamical element of conducting and the described accumulator; The actuator port pressure of described accumulator is greater than the predetermined pressure of described second pressure relay, second pressure relay outputs control signals to described second direction control valve and described third direction control valve, cuts off the path between described dynamical element and the described accumulator.
Preferably, the described first chassis executive component is specially the differential lock oil cylinder or takes off the bridge oil cylinder.
Preferably, what also comprise actuator port that the second chassis executive component and being used to controls the described second chassis executive component and system pressure oil circuit or oil return circuit is communicated with the four directions to control valve, and described four directions is communicated with the actuator port of described accumulator to the filler opening of control valve.
Preferably, the described first chassis executive component is specially the differential lock oil cylinder, and the described second chassis executive component is specially and takes off the bridge oil cylinder.
Preferably, described rated working pressure of taking off the rated working pressure of bridge oil cylinder less than described differential lock oil cylinder; And described control system also comprises the actuator port that is arranged on described accumulator to second reduction valve of described four directions on the path between the control valve, and is arranged on second relief valve on the path between second reduction valve and the oil return circuit; And the set pressure of described second reduction valve is less than the set pressure of second relief valve.
Wheeled crane provided by the invention comprises the wheel undercarriage with executive component, also comprises foregoing chassis hydraulic control system.
Compared with prior art, the present invention is used to control the control system employing hydraulic control of chassis executive component, the exportable working pressure that satisfies differential lock oil cylinder needs.With the differential lock oil cylinder is example, because the hydraulic oil pressure shrinkage is very little, thereby the action of differential lock oil cylinder is not subjected to load effect, and action response is timely in the working procedure, the degree of accuracy height, thus can guarantee that differential control is timely and effective.Simultaneously, differential lock oil cylinder telescopic displacement is not subjected to the influence of frictional force, moves that comparatively balance is reliable.
In preferred version of the present invention, also comprise first pressure relay and second pressure relay of the actuator port pressure that is used to gather described accumulator, make this system have energy storage pressure self compensation function.Because the predetermined pressure of first pressure relay is less than the predetermined pressure of second pressure relay, in the working procedure, when the working pressure of accumulator during less than the predetermined pressure of first pressure relay, then first pressure relay outputs control signals to second direction control valve and third direction control valve, the path between conducting dynamical element and the accumulator; That is to say, can carry out the topping up ftercompction to accumulator automatically.Otherwise when the working pressure of accumulator during greater than the predetermined pressure of second pressure relay, then second pressure relay outputs control signals to second direction control valve and third direction control valve, cuts off the path between dynamical element and the accumulator; That is to say that this preferred version can also be closed down the topping up ftercompction automatically.Compared with prior art, this programme has reliable pressure self compensation function, has effectively improved the operability of control system.
In another preferred version of the present invention, this control system can be controlled the operation of two executive components simultaneously, specifically can control the differential lock oil cylinder simultaneously and take off the bridge oil cylinder; So be provided with, not needing additionally to increase an oil hydraulic pump provides pressure oil, this system can also with the shared oil hydraulic pump of other hydraulic systems, promptly save cost and alleviate complete vehicle weight again.
Chassis provided by the invention hydraulic control system is applicable to any industrial wheeled equipment, is specially adapted to wheeled crane.
Description of drawings
Fig. 1 is the schematic diagram of a kind of Pneumatic-control type chassis control system in the prior art;
Fig. 2 is first embodiment's fundamental diagram of chassis hydraulic control system;
Fig. 3 is second embodiment's fundamental diagram of chassis hydraulic control system;
Fig. 4 is the overall structure schematic representation of wheeled crane described in the embodiment.
Among Fig. 2-Fig. 4:
Oil suction oil purifier 1, stop valve 2, dynamical element 3, second direction control valve 4, the first relief valve 5a, first pressure relay 6, second pressure relay 7, accumulator 8, the first reduction valve 9a, restriction 10, one-way valve 11, third direction control valve 12, first direction control valve 13a, four directions are to control valve 13b, the first chassis executive component 14a, the second chassis executive component 14b, oil return oil purifier 16, fuel tank 17.
Embodiment
Core of the present invention provides a kind of chassis hydraulic control system, on the basis of the action degree of accuracy that effectively improves corresponding controlling component, stationarity, has improved output action power greatly.Specify embodiment below in conjunction with Figure of description.
See also Fig. 2, this is illustrated as first embodiment's fundamental diagram of chassis hydraulic control system.
This system is used to control the action of the first chassis executive component 14a, and identical with existing gas control mode is to control its action by the pressure fluid that exports executive component to.This system controls the actuator port of the first chassis executive component 14a and being communicated with of system pressure oil circuit P or oil return circuit T by first direction control valve 13a; The actuator port of accumulator 8 is communicated with the filler opening of first direction control valve 13a, and the pressure oil liquid that accumulator 8 is laid in can satisfy the needs of first chassis executive component 14a action fully.Particularly, this first direction control valve 13a can be the two-position three way solenoid directional control valve, and its oil outlet is communicated with the actuator port of the first chassis executive component 14a, its filler opening is communicated with the pressure oil circuit, its return opening is communicated with oil return circuit; In the working procedure, first direction control valve 13a can switch between two working positions, realizes that the working oil chamber of the first chassis executive component 14a is communicated with the pressure oil circuit or is communicated with oil return circuit.
The first chassis executive component 14a in this programme can be the differential lock oil cylinder, is used to drive the opening and closing of differential between the vehicle bridge wheel; Certainly, also can be used between four bridge drive patterns and two bridge drive patterns, switching for taking off the bridge oil cylinder.Should be appreciated that this first chassis executive component 14a is not limited to the differential lock oil cylinder or takes off the bridge oil cylinder, use needs all in the scope that the application asks for protection as long as satisfy.
Obviously, for the differential lock oil cylinder, having formed one as control unit, differential lock oil cylinder (the first chassis executive component 14a) as executive component as dynamical element, first direction control valve 13a by accumulator 8 provides the hydraulic control system of pressure by accumulator, is used to control differential between vehicle wheel.And for taking off the bridge oil cylinder, then by accumulator 8 as dynamical element, first direction control valve 13a as control unit, take off bridge oil cylinder (the first chassis executive component 14a) and formed one as executive component and provide the hydraulic control system of pressure by accumulator, be used to control the conversion and control of vehicle traction form.During practical operation, when opening discrepancy switch or taking off the bridge switch (not shown), first direction control valve 13a gets TURP and changes to working position, hydraulic oil in the accumulator 8 enters the differential lock oil cylinder or takes off the bridge oil cylinder by first direction control valve 13a, and vehicle was in the differential state or was transformed into two-wheel drive mode this moment; When closing discrepancy switch or taking off bridge switch, first direction control valve 13a dead electricity is returned to down working position, accumulator 8 and differential lock oil cylinder or take off between the bridge oil cylinder disconnects, differential lock oil cylinder or the hydraulic oil that takes off in the bridge oil cylinder flow back to hydraulic oil container by first direction control valve 13a, differential lock oil cylinder or take off bridge oil cylinder return, this moment, the four-wheel drive pattern is closed or be transformed into to vehicle differential state.
This system can with other hydraulic system common power elements of car load, also can as shown in FIG. independently dynamical element 3 be set, be used in fuel tank 17 pump and get fluid and delivery pressure fluid to system pressure oil circuit P; This dynamical element 3 adopts metering pump in this programme.Correspondingly, also be provided with second direction control valve 4, be used to control the oil outlet of described dynamical element 3 and being communicated with of system pressure oil circuit P or oil return circuit T.Like this, when liquid storage pressure in the accumulator 8 satisfied system's operation needs, then second direction control valve 4 was positioned at first working position, and the pressure oil liquid of dynamical element 3 outputs is communicated with oil return circuit through second direction control valve 4, flow back to fuel tank 17, thereby reduced energy consumption.When needs carried out the topping up ftercompction to accumulator, then second direction control valve 4 switched to second working position, and the pressure oil liquid of dynamical element 3 outputs is communicated with the pressure oil circuit through second direction control valve 4, sets up system pressure.Particularly, this second direction control valve 4 is specially the two-position four-way solenoid directional control valve, its filler opening is communicated with the oil outlet of dynamical element 3, its return opening through oil return circuit be communicated with fuel tank 17, its actuator port is communicated with the system pressure oil circuit, its another hydraulic fluid port is as overflowing back hydraulic fluid port; As shown in the figure, in first working position, the filler opening of this valve, return opening and overflow back hydraulic fluid port and be communicated with, in second working position, the filler opening of this valve is communicated with, overflows back hydraulic fluid port and is communicated with return opening with actuator port.
As previously mentioned, native system can with other hydraulic system common power elements, in like manner, the dynamical element 3 in this programme also can use needs as long as the delivery pressure of dynamical element 3 and discharge capacity satisfy two or more systems for other hydraulic systems provide pressure oil liquid.
This programme adopts third direction control valve 12 to realize reliably providing pressure oil liquid for other hydraulic systems.This third direction control valve 12 is arranged between second direction control valve 4 and the accumulator 8 on the oil circuit, is used for described second direction control valve 4 to the conducting of oil circuit between the accumulator 8 or non-conduction; Equally, second direction control valve 4 preferred bi-bit bi-pass solenoid directional control valves, perhaps electrically switchable grating valve etc.So design can have bypath system interface A at the path between dynamical element 3 and the second direction control valve 4.Like this, interface A place oil circuit can be connected with other hydraulic systems of vehicle, when the hydraulic system of this connection needs work, as long as second direction control valve 4(two-position four-way solenoid directional control valve) must electricly promptly can set up system pressure; Obviously, if this moment third direction control 12 valves and be in nonconducting state and promptly can be other hydraulic systems of vehicle working pressure fluid is provided.Certainly, because oil circuit is provided with third direction control valve 12 between second direction control valve 4 and the accumulator 8, when needs carried out the topping up ftercompction to accumulator, when second direction control valve 4 switched to second working position, third direction control valve 12 switched on state synchronously.
Need to prove that if native system and bypath system common power element, when dynamical element when only delivery pressure fluid is to native system pressure oil circuit, there is the possibility of the working pressure that exceeds accumulator 8 or executive component in its delivery pressure so.Be further to improve the system works performance, this programme also can be provided with the first reduction valve 9a at third direction control valve 12 to the path between the actuator port of accumulator 8, between the actuator port of accumulator 8 and oil return circuit T the first relief valve 5a is set; And the set pressure of the first reduction valve 9a is less than the set pressure of described first relief valve 5.So be provided with, the first reduction valve 9a set pressure can limit mouth pressure (pressure of accumulator 8), this pressure substantial constant.For the protection to system, it is the accumulator maximum pressure that the set pressure of the first relief valve 5a is set at system.Obviously,, the pressure of accumulator is limited between the set pressure of the set pressure of the first reduction valve 9a and first relief valve 5, can further improve the stability of system works by the first reduction valve 9a and the first relief valve 5a acting in conjunction.The return opening of the first relief valve 5a described here can be communicated with the hydraulic fluid port that overflows back of second direction control valve 4, is beneficial to pipeline connection.
Further, this programme can also have energy storage pressure self compensation function, that is to say, in the time of the energy storage pressure deficiency, this system can carry out the topping up ftercompction to accumulator automatically, does not need manual operation.This function mainly realizes by first pressure relay 6 and second pressure relay 7 set up, two pressure relayes all are used to gather the actuator port pressure of accumulator 8, and the predetermined pressure of first pressure relay 6 is less than the predetermined pressure of second pressure relay 7.So be provided with, form an accumulator topping up ftercompction system with pressure self compensation function by dynamical element 3, the first reduction valve 9a, the first relief valve 5a, second direction control valve 4, third direction control valve 12, first pressure relay 6, second pressure relay 7 and accumulator 8.When the actuator port pressure of accumulator 8 during less than the predetermined pressure of first pressure relay 6, first pressure relay 6 outputs control signals to second direction control valve 4 and third direction control valve 12, second direction control valve 4 and third direction control valve 12 get electric, the path between described dynamical element 3 of conducting and the described accumulator 8; The pressure oil that this moment, dynamical element 3 provided carries out the topping up ftercompction by second direction control valve 4 and third direction control valve 12 to accumulator 8.And when the actuator port pressure of accumulator 8 predetermined pressure greater than second pressure relay 7, second pressure relay 7 outputs control signals to second direction control valve 4 and third direction control valve 12, second direction control valve 4 and third direction control valve 12 dead electricity are got back to former working position, cut off the path between described dynamical element 3 and the described accumulator 8, accumulator stops topping up.
For optimizing the performance of native system, be disposed with stop valve 2 and oil suction oil purifier 1 on the path between dynamical element 3 and the fuel tank 17, the fluid of oil return circuit flows back to fuel tank 17 through oil return oil purifier 16.Simultaneously, on the path between the third direction control valve 12 and the first reduction valve 9a, be disposed with one-way valve 11 and restriction 10, to improve the stability of system works.Because the setting of said elements and not this Applicant's Abstract graph inventive point place are so this paper repeats no more.
Below in conjunction with schematic diagram shown in Figure 2, specify second embodiment of chassis hydraulic control system.
The present embodiment and first embodiment's basic design concept is identical, both compare difference and are: present embodiment has increased by the second chassis executive component 14b that is controlled, and control the actuator port of the second chassis executive component 14b and being communicated with of system pressure oil circuit P or oil return circuit T to control valve 13b by the four directions, and the four directions is communicated with the actuator port of accumulator 8 to the filler opening of control valve 13b.Similarly, this four directions can be the two-position three way solenoid directional control valve to control valve 13b, and its oil outlet is communicated with the actuator port of the second chassis executive component 14b, its filler opening is communicated with the pressure oil circuit, its return opening is communicated with oil return circuit; In the working procedure, the four directions can be switched between two working positions to control valve 13b, realizes that the working oil chamber of the second chassis executive component 14b is communicated with the pressure oil circuit or is communicated with oil return circuit.
In this programme, the first chassis executive component 14a can be specially the differential lock oil cylinder, and the second chassis executive component 14b can be specially and take off the bridge oil cylinder, thereby can control the differential lock oil cylinder simultaneously and take off the bridge oil cylinder.Generally, the oil cylinder rated pressure that acts on the different institutions load is different, for better coordinating two executive components, the path of actuator port to the four directions between control valve 13b of present embodiment accumulator 8 is provided with the second reduction valve 9b, and the path between the second reduction valve 9b and the oil return circuit T is provided with the second relief valve 5b; And the set pressure of the second reduction valve 9b is less than the set pressure of the second relief valve 5b, thereby the working pressure of the second chassis executive component 14b is limited between the set pressure of the set pressure of the second reduction valve 9b and the second relief valve 5b, has satisfied the situation of different rated working pressures.
Except that the hydraulic control system of aforementioned chassis, present embodiment also provides a kind of wheeled crane, sees also Fig. 4, the figure shows the overall structure schematic representation of wheeled crane.
What specify is, functional parts such as the chassis of this hoist, swirl gear, hoisting system, crane system are identical with prior art, and those skilled in the art can realize fully based on prior art, so no longer detailed description.Its chassis has executive component, and such as differential lock oil cylinder and take off the bridge oil cylinder, this chassis also has foregoing chassis hydraulic control system.
The above only is a preferred implementation of the present invention; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (7)
1. the chassis hydraulic control system is used to control the action of the first chassis executive component; It is characterized in that this system comprises:
The first direction control valve is used to control the actuator port of the described first chassis executive component and being communicated with of system pressure oil circuit or oil return circuit;
Accumulator, its actuator port is communicated with the filler opening of described first direction control valve;
Dynamical element is used for delivery pressure fluid to the system pressure oil circuit; With
The second direction control valve is used to control the oil outlet of described dynamical element and being communicated with of system pressure oil circuit or oil return circuit;
The third direction control valve is used to control described second direction control valve to the conducting of oil circuit between the accumulator or non-conduction; And the path between described dynamical element and described second direction control valve has the bypath system interface; Also comprise:
Be used to gather first pressure relay and second pressure relay of the actuator port pressure of described accumulator, and the predetermined pressure of described first pressure relay is less than the predetermined pressure of second pressure relay; The actuator port pressure of described accumulator is less than the predetermined pressure of first pressure relay, first pressure relay outputs control signals to described second direction control valve and described third direction control valve, the path between described dynamical element of conducting and the described accumulator; The actuator port pressure of described accumulator is greater than the predetermined pressure of described second pressure relay, second pressure relay outputs control signals to described second direction control valve and described third direction control valve, cuts off the path between described dynamical element and the described accumulator.
2. chassis according to claim 1 hydraulic control system is characterized in that, also comprises:
First reduction valve is arranged on described third direction control valve to the path between the actuator port of described accumulator; With
First relief valve is arranged between the actuator port and oil return circuit of described accumulator; And
The set pressure of described first reduction valve is less than the set pressure of described first relief valve.
3. chassis according to claim 1 and 2 hydraulic control system is characterized in that, the described first chassis executive component is specially the differential lock oil cylinder or takes off the bridge oil cylinder.
4. chassis according to claim 1 and 2 hydraulic control system, it is characterized in that, what also comprise actuator port that the second chassis executive component and being used to controls the described second chassis executive component and system pressure oil circuit or oil return circuit is communicated with the four directions to control valve, and described four directions is communicated with the actuator port of described accumulator to the filler opening of control valve.
5. chassis according to claim 4 hydraulic control system is characterized in that, the described first chassis executive component is specially the differential lock oil cylinder, and the described second chassis executive component is specially and takes off the bridge oil cylinder.
6. chassis according to claim 5 hydraulic control system is characterized in that, described rated working pressure of taking off the rated working pressure of bridge oil cylinder less than described differential lock oil cylinder; And described control system also comprises:
Second reduction valve, the actuator port that is arranged on described accumulator to described four directions on the path between the control valve; With
Second relief valve is arranged on the path between second reduction valve and the oil return circuit; And
The set pressure of described second reduction valve is less than the set pressure of second relief valve.
7. wheeled crane comprises the wheel undercarriage with executive component, it is characterized in that, also comprises as each described chassis hydraulic control system among the claim 1-6.
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| CN 201010591063 CN102022516B (en) | 2010-12-15 | 2010-12-15 | Wheeled crane and chassis hydraulic control system thereof |
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| CN 201010591063 CN102022516B (en) | 2010-12-15 | 2010-12-15 | Wheeled crane and chassis hydraulic control system thereof |
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| CN103692905B (en) * | 2013-12-12 | 2017-02-15 | 中联重科股份有限公司 | Autocrane and control method thereof |
| CN103696996A (en) * | 2013-12-31 | 2014-04-02 | 太原重工股份有限公司 | Crane and hydraulic control system thereof |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101260938A (en) * | 2007-12-27 | 2008-09-10 | 奇瑞汽车股份有限公司 | Automobile electric control mechanical type automatic speed variator hydraulic system and its control method |
| CN201884601U (en) * | 2010-12-15 | 2011-06-29 | 徐州重型机械有限公司 | Wheeled crane and chassis hydraulic control system thereof |
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| US7302797B2 (en) * | 2005-05-31 | 2007-12-04 | Caterpillar Inc. | Hydraulic system having a post-pressure compensator |
| CN101177139B (en) * | 2007-12-10 | 2011-05-18 | 常州科研试制中心有限公司 | Bidirectional steering vehicle braking transmission system |
| JP5480529B2 (en) * | 2009-04-17 | 2014-04-23 | 株式会社神戸製鋼所 | Braking control device for swivel work machine |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101260938A (en) * | 2007-12-27 | 2008-09-10 | 奇瑞汽车股份有限公司 | Automobile electric control mechanical type automatic speed variator hydraulic system and its control method |
| CN201884601U (en) * | 2010-12-15 | 2011-06-29 | 徐州重型机械有限公司 | Wheeled crane and chassis hydraulic control system thereof |
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| JP特开2010-247965A 2010.11.04 |
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