CN103626057A - Crane and hydraulic system thereof - Google Patents

Crane and hydraulic system thereof Download PDF

Info

Publication number
CN103626057A
CN103626057A CN201310685010.9A CN201310685010A CN103626057A CN 103626057 A CN103626057 A CN 103626057A CN 201310685010 A CN201310685010 A CN 201310685010A CN 103626057 A CN103626057 A CN 103626057A
Authority
CN
China
Prior art keywords
valve
oil
check valve
hoisting crane
communicated
Prior art date
Application number
CN201310685010.9A
Other languages
Chinese (zh)
Other versions
CN103626057B (en
Inventor
周丽云
李林
邹兴龙
Original Assignee
三一汽车起重机械有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 三一汽车起重机械有限公司 filed Critical 三一汽车起重机械有限公司
Priority to CN201310685010.9A priority Critical patent/CN103626057B/en
Publication of CN103626057A publication Critical patent/CN103626057A/en
Application granted granted Critical
Publication of CN103626057B publication Critical patent/CN103626057B/en

Links

Abstract

The invention provides a crane and a hydraulic system thereof. The hydraulic system comprises a load sensitive pump, a first execution mechanism and a second execution mechanism, wherein the first execution mechanism and the second execution mechanism are driven by the load sensitive pump; the first execution mechanism comprises a variable-amplitude oil cylinder, a balance valve and a first load sensitive multi-way valve, which are connected to the load sensitive pump in series, and an energy accumulator; the energy accumulator is provided with a one-way oil path which flows into the first load sensitive multi-way valve and other execution mechanisms in one way; a bypass oil path flowing into the energy accumulator in one way is arranged on an oil path between a rodless cavity of the variable-amplitude oil cylinder and the first load sensitive multi-way valve; a switch valve is arranged on the bypass oil path and is disconnected when the variable-amplitude oil cylinder stretches out and connected when the variable-amplitude oil cylinder withdraws. Through the hydraulic system, the valve opening flow of the first load sensitive multi-way valve is supplied by recycling flow and the output flow of the load sensitive pump commonly, so that the energy-saving effect is generated and energy is fully released.

Description

Hoisting crane and hydraulic efficiency pressure system thereof

Technical field

The present invention relates to hydraulic technique field, particularly a kind of hoisting crane and hydraulic efficiency pressure system thereof.

Background technology

At present, method and thinking that research engineering hoisting crane is energy-conservation emerge in an endless stream, but all can unresolved energy recovery fully discharge this two problems to the impact of actuating unit regular event and stored energy.As some hoisting crane, energy storage is directly connected on the rodless cavity of amplitude oil cylinder on side, when the weight of this crane arm below, by energy storage, converting gravitional force to pressure energy is stored in energy storage, but the rising along with energy storage absorbed inside pressure, amplitude oil cylinder falling speed is slack-off gradually, handling poor; When crane arm lifting, then the pressure energy of energy storage storage is discharged for driving amplitude oil cylinder to extend.But along with the reduction of the inner hold-off pressure of energy storage, the thrust of generation is difficult to promote amplitude oil cylinder gradually, not only causes the action of amplitude oil cylinder not accurate enough, the energy that causes again energy storage to reclaim can not fully discharge.In addition, crane requires very high to quality of movement, should be precisely reliable again, and therefore on crane, applicating energy-saving technology must guarantee the normal operation of original action.

Summary of the invention

In view of this, the present invention is intended to propose a kind of hoisting crane and hydraulic efficiency pressure system thereof, can recuperated energy and fully discharge, can not exert an influence to the regular event of actuating unit again.

For achieving the above object, technical scheme of the present invention is achieved in that

On the one hand, the invention provides a kind of hydraulic efficiency pressure system of hoisting crane, comprise load sensitive pump and by the first execution architecture and second actuating unit of its driving, described the first actuating unit comprises the amplitude oil cylinder with described load-sensitive series connection of pumps, balance cock and the first load sensing multi-way valve, the hydraulic efficiency pressure system of described hoisting crane also comprises energy storage, described energy storage is provided with the unidirectional unidirectional oil circuit that flows into described the first load sensing multi-way valve and the second actuating unit, on the rodless cavity of described amplitude oil cylinder to the side that is provided with the described energy storage of unidirectional inflow on the oil circuit between described the first load sensing multi-way valve, connect oil circuit, on described side, connect and on oil circuit, be provided with switch valve, described switch valve disconnects when described amplitude oil cylinder is stretched out, when retracting, described amplitude oil cylinder opens.

Further, also comprise the 3rd check valve and damping, after described the 3rd check valve and damping parallel connection, be connected on the oil circuit between described balance cock and described the first load sensing multi-way valve, and the oil inlet of described the 3rd check valve is communicated with described the first load sensing multi-way valve, and the oil outlet of described the 3rd check valve is communicated with described balance cock.

Further, the oil inlet that described side connects oil circuit is arranged on the oil circuit between described balance cock and described the 3rd check valve.

Further, connect on oil circuit be provided with the first check valve on described side, the oil inlet of described the first check valve is communicated with described switch valve, and the oil outlet of described the first check valve is communicated with described energy storage.

Further, on described unidirectional oil circuit, be provided with the second check valve, the oil inlet of described the second check valve is communicated with described energy storage, and the oil outlet of described the second check valve is communicated with the oil inlet of described the first load sensing multi-way valve.

Further, also comprise the first by pass valve, the oil inlet of described the first by pass valve is communicated with the oil outlet of described energy storage, described the first check valve, the oil inlet of described the second check valve simultaneously, and the oil outlet of described the first by pass valve takes back fuel tank.

Further, at the oil outlet place of described load sensitive pump, be provided with the 4th check valve, described the 4th oil inlet of check valve and the oil outlet of described load sensitive pump are communicated with, and the oil outlet of described the 4th check valve is communicated with the oil outlet of described the second check valve, the oil inlet of the first load sensing multi-way valve simultaneously.

Further, also comprise the second by pass valve, the oil inlet of described the second by pass valve is communicated with the oil outlet of described the 4th check valve, and the oil outlet of described the second by pass valve takes back fuel tank.

Further, described switch valve is two position two-way valve or two position three-way valve, and the type of drive of described switch valve is hydraulic control or electromagnetic control.

Further, described the second actuating unit comprises HM Hydraulic Motor or the hydraulic actuating cylinder that is provided with the second load sensing multi-way valve, and described the second actuating unit with shown in the first actuating unit in parallel.

On the other hand, the present invention also provides a kind of hoisting crane, and described hoisting crane is provided with the hydraulic efficiency pressure system of hoisting crane as above.

With respect to prior art, the present invention has following advantage: hydraulic efficiency pressure system of the present invention, its energy storage is provided with the other oil circuit that connects, the oil inlet of this energy storage is arranged between balance cock and the first load sensing multi-way valve, can make energy storage in stored energy simultaneously, can also pass through the pilot pressure of adjustment valve, make amplitude oil cylinder normal descend, not affect original action normal operation; Energy storage is also provided with unidirectional oil circuit, the oil outlet of this energy storage is arranged on the exit of load sensitive pump, the valve port flow that can make the first load sensing multi-way valve provides by reclaiming together with the delivery rate of flow and load sensitive pump, thereby produces energy saving effect and can fully release energy.

Accompanying drawing explanation

The accompanying drawing that forms a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention is used for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:

Fig. 1 is that hydraulic efficiency pressure system described in the embodiment of the present invention is at the hydraulic schematic diagram of initial condition;

Fig. 2 is the hydraulic schematic diagram that the hydraulic efficiency pressure system individual part described in the embodiment of the present invention realizes flow regeneration;

Fig. 3 is that the hydraulic efficiency pressure system composite move described in the embodiment of the present invention is realized the hydraulic schematic diagram that energy reclaims;

Fig. 4 is that the hydraulic efficiency pressure system composite move described in the embodiment of the present invention is realized exergonic hydraulic schematic diagram.

Description of reference numerals:

1-amplitude oil cylinder, 2-balance cock, 3-switch valve, 4-energy storage, 5-the first check valve, 6-the second check valve, 7-load sensitive pump, 8-the first by pass valve, 9-the 3rd check valve, 10-damping, 11-the first load sensing multi-way valve, 12-the 4th check valve, 13-the second by pass valve, 14-the second load sensing multi-way valve.

The specific embodiment

It should be noted that, in the situation that not conflicting, embodiment and the feature in embodiment in the present invention can combine mutually.Describe below with reference to the accompanying drawings and in conjunction with the embodiments the present invention in detail.

Fig. 1 to Fig. 4 is the relative theory figure of the hydraulic efficiency pressure system of the hoisting crane described in the present embodiment, Fig. 1 is that this hydraulic efficiency pressure system is at the hydraulic schematic diagram of initial condition, as shown in FIG., this hydraulic efficiency pressure system comprises the first actuating unit switch valve 3, energy storage 4, the first check valve 5, the second check valve 6, load sensitive pump 7, the first by pass valve 8, the 3rd check valve 9, damping 10, the 4th check valve 12, the second by pass valve 13, the second load sensing multi-way valve 14 and the second actuating unit.Wherein, this first actuating unit comprises amplitude oil cylinder 1, balance cock 2 and the first load sensing multi-way valve 11, the rodless cavity of amplitude oil cylinder 1 is communicated with the hydraulic fluid port b2 of balance cock 2, the rod chamber of amplitude oil cylinder 1 is communicated with the hydraulic fluid port B1 of the first load sensing multi-way valve 11, the hydraulic fluid port b1 while of balance cock 2 and the oil outlet d of the 3rd check valve 9, the hydraulic fluid port f of damping 10, the hydraulic fluid port a3 of switch valve 3 is communicated with, the oil inlet c of the 3rd check valve 9 and the hydraulic fluid port e of damping 10 are communicated with the hydraulic fluid port A1 of the first load sensing multi-way valve 11 simultaneously, the hydraulic fluid port a1 of switch valve 3 is communicated with the oil inlet c of the first check valve 5, 4 whiles and the first by pass valve 8 of energy storage, the oil outlet d of the first check valve 4, the oil inlet c of the second check valve 6 is communicated with, the oil outlet of load sensitive pump 7 is communicated with the oil inlet c of the 4th check valve 12, the oil outlet d while of the 4th check valve 12 and the oil inlet P of the first load sensing multi-way valve 11, the oil outlet d of the second check valve 6, the oil inlet of the second by pass valve 13, the oil inlet P of the second load sensing multi-way valve 14 is communicated with.This switch valve 3 is two position three way hydraulic controlled valve, when switch valve is during in spring position, the hydraulic fluid port a2 sealing of this switch valve 3 need not, hydraulic fluid port a1 and hydraulic fluid port a3 are in off-state.

Under initial condition: when the first load sensing multi-way valve 11 and the second load sensing multi-way valve 14 all in meta, balance cock 2 with switch valve 3 during all in spring position, energy storage 4 is in initial p 0 state; Load sensitive pump 7 because of valve ports such as the first load sensing multi-way valve 11 and the second load sensing multi-way valves 14 without traffic demand in minimum displacement condition to maintain system leak.Wherein, the first by pass valve 8 is the safety valve of energy storage 4, the second by pass valve 13 restriction system work top pressures, and balance cock 2 is in order to limit the contraction speed of amplitude oil cylinder 1, so that amplitude oil cylinder 1 steadily falls under weight effect.

Fig. 2 is the hydraulic schematic diagram that the hydraulic efficiency pressure system individual part described in the present embodiment realizes flow regeneration.When amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, when the second actuating unit is not worked, can realize the flow regeneration of individual part, the delivery pressure of Pa(load sensitive pump now) lower than the Preliminary pressure-filled of P0(energy storage inside), as shown in the figure, the first load sensing multi-way valve 11 is in left position, independent pilot control promotes balance cock 2 to throttling position, switch valve 3 is opened, amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, the fluid of amplitude oil cylinder 1 rodless cavity is through the hydraulic fluid port b2 of balance cock 2, after hydraulic fluid port b1, be divided into two-way: by leading up to, connecing oil circuit (is the hydraulic fluid port a3 of switch valve 3, hydraulic fluid port a1, the oil inlet c of the first check valve 5, oil outlet d, below identical in this), unidirectional oil circuit (the oil inlet c of the second check valve 6, oil outlet d, below identical in this) to the hydraulic fluid port P of the first load sensing multi-way valve 11, hydraulic fluid port B1 is to amplitude oil cylinder 1 rod chamber, separately lead up to hydraulic fluid port f, hydraulic fluid port e, the first load sensing multi-way valve 11 hydraulic fluid port A1, the hydraulic fluid port T oil sump tank of damping 10.Rodless cavity flow because of amplitude oil cylinder 1 in flow regenerative process makes its valve port flow in saturation conditions through the first load sensing multi-way valve 11, responsive to load pump 7 is without traffic demand, therefore load sensitive pump 7 moves under minimum discharge capacity (initial displacement) state, produces energy-saving benefit.

Fig. 3 is that the hydraulic efficiency pressure system composite move described in the present embodiment is realized the hydraulic schematic diagram that energy reclaims.When amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, when the second actuating unit is also worked, the flow that can realize composite move reclaims, the delivery pressure of Pa(load sensitive pump now) higher than the Preliminary pressure-filled of P0(energy storage inside), as shown in FIG., the second load sensing multi-way valve 14 is in left position, the first load sensing multi-way valve 11 is also when left position, and independent pilot control promotes balance cock 2 to throttling position, switch valve 3 is opened, amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, the fluid of amplitude oil cylinder 1 rodless cavity is through the hydraulic fluid port b2 of balance cock 2, after hydraulic fluid port b1, be divided into two-way: by leading up to, connect oil circuit to energy storage 4, it is energy storage stored energy, realizing flow reclaims, separately lead up to damping 10 hydraulic fluid port f, hydraulic fluid port e, the first load sensing multi-way valve 11 hydraulic fluid port A1, hydraulic fluid port T oil sump tank.Work oil sources is from hydraulic fluid port P minute two-way after oil inlet c, the oil outlet d of the 4th check valve 12 of load sensitive pump 7, one tunnel the first load sensing multi-way valve 11 hydraulic fluid port P, hydraulic fluid port B1 are to amplitude oil cylinder 1 rod chamber, and another road the second load sensing multi-way valve 14 hydraulic fluid port P, hydraulic fluid port B2 are to other actuating unit actuator port.

Fig. 4 is that the hydraulic efficiency pressure system composite move described in the present embodiment is realized exergonic hydraulic schematic diagram.When amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, when the second actuating unit is also worked, can realize energy at composite move discharges, the delivery pressure of Pa(load sensitive pump now) lower than the pressure of PQ(energy storage inside), as shown in FIG., the second load sensing multi-way valve 14 is in right position, the first load sensing multi-way valve 11 is when left position, and independent pilot control promotes balance cock 2 to throttling position, switch valve 3 is opened, amplitude oil cylinder 1 whereabouts of conducting oneself with dignity under weight effect, the fluid of amplitude oil cylinder 1 rodless cavity is through balance cock 2 hydraulic fluid port b2, after hydraulic fluid port b1, be divided into two-way: the other oil sources that connects oil circuit and energy storage inside of leading up to converges, then through unidirectional oil circuit, converge with the oil sources of load sensitive pump 7 again, and then minute two-way oil-feed, one tunnel oil-feed is through the first sensing multi-way valve 11 hydraulic fluid port P, hydraulic fluid port B1 is to amplitude oil cylinder 1 rod chamber, another road oil-feed is through the hydraulic fluid port P of the second sensing multi-way valve 14, hydraulic fluid port A2 is to other actuating unit actuator port, separately lead up to damping 10 hydraulic fluid port f, hydraulic fluid port e, the first load sensing multi-way valve 11 hydraulic fluid port A1, hydraulic fluid port T oil sump tank.In energy release process because the flow of amplitude oil cylinder 1 rodless cavity and the inner flow discharging of energy storage are all through the first load sensing multi-way valve 11 and the second load sensing multi-way valve 14 valve ports, the traffic demand of system responsive to load pump 7 is greatly reduced, produce energy-saving benefit.

The hydraulic efficiency pressure system of the hoisting crane described in the present embodiment, is connected to energy recycling member energy storage 4 between balance cock 2 and damping 10, object be energy storage 4 in stored energy, can make by the pilot pressure p of adjustment valve 2 amplitude oil cylinder 1 normal descend; The energy of energy storage 4 is released into the outlet of load sensitive pump 7, object is that the valve port flow (LS-load-reacting flow system flow control feature is that load sensitive pump is controlled its discharge capacity by load sensing multi-way valve valve port traffic demand) of the first load sensing multi-way valve 11 provides by reclaiming together with the delivery rate of flow and load sensitive pump 7, produces energy saving effect.

Except the hydraulic efficiency pressure system of above-mentioned hoisting crane, the embodiment of the present invention also provides a kind of hoisting crane that is provided with above-mentioned hydraulic efficiency pressure system, and the structure of other each several part of this hoisting crane, with reference to prior art, repeats no more herein.

The foregoing is only preferred embodiment of the present invention, in order to limit the present invention, within the spirit and principles in the present invention not all, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection scope of the present invention.

Claims (10)

1. the hydraulic efficiency pressure system of a hoisting crane, it is characterized in that, comprise load sensitive pump (7) and by the first execution architecture and second actuating unit of its driving, described the first actuating unit comprises the amplitude oil cylinder (1) of connecting with described load sensitive pump (7), balance cock (2) and the first load sensing multi-way valve (11), the hydraulic efficiency pressure system of described hoisting crane also comprises energy storage (4), described energy storage (4) is provided with the unidirectional unidirectional oil circuit that flows into described the first load sensing multi-way valve (11) and the second actuating unit, on the rodless cavity of described amplitude oil cylinder (1) to the side that is provided with the described energy storage of unidirectional inflow (4) on the oil circuit between described the first load sensing multi-way valve (11), connect oil circuit, on described side, connect and on oil circuit, be provided with switch valve (3), described switch valve (3) disconnects when described amplitude oil cylinder (1) is stretched out, when retracting, described amplitude oil cylinder (1) opens.
2. the hydraulic efficiency pressure system of hoisting crane according to claim 1, it is characterized in that, also comprise the 3rd check valve (9) and damping (10), after described the 3rd check valve (9) and damping (10) parallel connection, be connected on the oil circuit between described balance cock (2) and described the first load sensing multi-way valve (11), and the oil inlet of described the 3rd check valve (9) is communicated with described the first load sensing multi-way valve (11), the oil outlet of described the 3rd check valve (9) is communicated with described balance cock (2).
3. the hydraulic efficiency pressure system of hoisting crane according to claim 2, is characterized in that, the oil inlet that described side connects oil circuit is arranged on the oil circuit between described balance cock (2) and described the 3rd check valve (9).
4. according to the hydraulic efficiency pressure system of the hoisting crane described in claims 1 to 3 any one, it is characterized in that, on described side, connect and on oil circuit, be provided with the first check valve (5), the oil inlet of described the first check valve (5) is communicated with described switch valve (3), and the oil outlet of described the first check valve (5) is communicated with described energy storage (4).
5. the hydraulic efficiency pressure system of hoisting crane according to claim 4, it is characterized in that, on described unidirectional oil circuit, be provided with the second check valve (6), the oil inlet of described the second check valve (6) is communicated with described energy storage (4), and the oil outlet of described the second check valve (6) is communicated with the oil inlet of described the first load sensing multi-way valve (11).
6. the hydraulic efficiency pressure system of hoisting crane according to claim 5, it is characterized in that, also comprise the first by pass valve (8), the oil inlet of described the first by pass valve (8) is communicated with the oil outlet of described energy storage (4), described the first check valve (5), the oil inlet of described the second check valve (6) simultaneously, and the oil outlet of described the first by pass valve (8) takes back fuel tank.
7. the hydraulic efficiency pressure system of hoisting crane according to claim 4, it is characterized in that, at the oil outlet place of described load sensitive pump (7), be provided with the 4th check valve (12), the oil inlet of described the 4th check valve (12) is communicated with the oil outlet of described load sensitive pump (7), and the oil outlet of described the 4th check valve (12) is communicated with the oil outlet of described the 3rd check valve (9), the oil inlet of the first load sensing multi-way valve (11) simultaneously.
8. the hydraulic efficiency pressure system of hoisting crane according to claim 7, it is characterized in that, also comprise the second by pass valve (13), the oil inlet of described the second by pass valve (13) is communicated with the oil outlet of described the 4th check valve (12), and the oil outlet of described the second by pass valve (13) takes back fuel tank.
9. the hydraulic efficiency pressure system of hoisting crane according to claim 1, is characterized in that, described the second actuating unit comprises HM Hydraulic Motor or the hydraulic actuating cylinder that is provided with the second load sensing multi-way valve (14), and described the second actuating unit with shown in the first actuating unit in parallel.
10. a hoisting crane, is characterized in that, described hoisting crane is provided with the hydraulic efficiency pressure system of the hoisting crane as described in claim 1 to 9 any one.
CN201310685010.9A 2013-12-16 2013-12-16 Hoisting crane and hydraulic efficiency pressure system thereof CN103626057B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310685010.9A CN103626057B (en) 2013-12-16 2013-12-16 Hoisting crane and hydraulic efficiency pressure system thereof

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310685010.9A CN103626057B (en) 2013-12-16 2013-12-16 Hoisting crane and hydraulic efficiency pressure system thereof

Publications (2)

Publication Number Publication Date
CN103626057A true CN103626057A (en) 2014-03-12
CN103626057B CN103626057B (en) 2016-03-23

Family

ID=50207570

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310685010.9A CN103626057B (en) 2013-12-16 2013-12-16 Hoisting crane and hydraulic efficiency pressure system thereof

Country Status (1)

Country Link
CN (1) CN103626057B (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105156412A (en) * 2014-11-24 2015-12-16 徐州重型机械有限公司 Crane luffing energy recovery-recycle method and system, and crane
CN106115518A (en) * 2016-09-08 2016-11-16 圣邦集团有限公司 A kind of crane energy-saving hydraulic system
CN107829988A (en) * 2017-11-02 2018-03-23 中科聚信洁能热锻装备研发股份有限公司 A kind of hydraulic press backhaul without pump accumulator closed oil circuit and its control method
WO2018119972A1 (en) * 2016-12-30 2018-07-05 徐州重型机械有限公司 Crane hydraulic control system and crane
CN108483264A (en) * 2018-06-20 2018-09-04 徐州重型机械有限公司 The hydraulic control system and hoisting machinery of hoisting machinery
US10359063B2 (en) 2014-11-24 2019-07-23 Xuzhou Heavy Machinery Co.., Ltd. Method and system for recovering and utilizing operating energy of crane, and crane

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997013072A2 (en) * 1995-09-29 1997-04-10 Beringer Hydraulik Ag Pressure vibration damping in hydraulic systems
JP2003269406A (en) * 2002-03-18 2003-09-25 Kobelco Contstruction Machinery Ltd Speed control device for cylinder
CN102874697A (en) * 2012-10-18 2013-01-16 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of arm support and crane
CN202937532U (en) * 2012-12-12 2013-05-15 中联重科股份有限公司 Hydraulic amplitude variation loop of arm support and oil-liquid hybrid power system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997013072A2 (en) * 1995-09-29 1997-04-10 Beringer Hydraulik Ag Pressure vibration damping in hydraulic systems
JP2003269406A (en) * 2002-03-18 2003-09-25 Kobelco Contstruction Machinery Ltd Speed control device for cylinder
CN102874697A (en) * 2012-10-18 2013-01-16 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of arm support and crane
CN202937532U (en) * 2012-12-12 2013-05-15 中联重科股份有限公司 Hydraulic amplitude variation loop of arm support and oil-liquid hybrid power system

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105156412A (en) * 2014-11-24 2015-12-16 徐州重型机械有限公司 Crane luffing energy recovery-recycle method and system, and crane
US10359063B2 (en) 2014-11-24 2019-07-23 Xuzhou Heavy Machinery Co.., Ltd. Method and system for recovering and utilizing operating energy of crane, and crane
CN105156412B (en) * 2014-11-24 2017-08-08 徐州重型机械有限公司 Crane amplitude variation energy regenerating and reuse method and system and crane
CN106115518A (en) * 2016-09-08 2016-11-16 圣邦集团有限公司 A kind of crane energy-saving hydraulic system
WO2018119972A1 (en) * 2016-12-30 2018-07-05 徐州重型机械有限公司 Crane hydraulic control system and crane
US10822211B2 (en) 2016-12-30 2020-11-03 Xuzhou Heavy Machinery Co., Ltd. Crane hydraulic control system and crane
CN107829988A (en) * 2017-11-02 2018-03-23 中科聚信洁能热锻装备研发股份有限公司 A kind of hydraulic press backhaul without pump accumulator closed oil circuit and its control method
CN108483264A (en) * 2018-06-20 2018-09-04 徐州重型机械有限公司 The hydraulic control system and hoisting machinery of hoisting machinery
CN108483264B (en) * 2018-06-20 2019-06-25 徐州重型机械有限公司 The hydraulic control system and hoisting machinery of hoisting machinery

Also Published As

Publication number Publication date
CN103626057B (en) 2016-03-23

Similar Documents

Publication Publication Date Title
CN104196080B (en) Variable speed volume directly drives pure electric hydraulic crawler excavator and drives and energy-recuperation system
CN100424361C (en) Closed electrohydraulic controlling system
CN104411519B (en) The fluid shock absorber that can be recovered energy
CN103569882B (en) Hydraulic lifting system of attached tower crane
CN102226453B (en) Dual-redundancy electro hydraulic servo actuator
EP2876306B1 (en) Flow control valve for construction machinery
CN103148031B (en) Energy-saving control system of hydraulic movable arm loop
CN105156391A (en) Composite variable pump and hydraulic control system using composite variable pump
CN202924661U (en) Hydraulic system of hoisting mechanism and crane
CN104595289B (en) Double-redundancy electro-hydrostatic actuator (EHA)
CN103016453A (en) Impulse test system of hydraulic hose
CN103741755B (en) A kind of excavator energy-recuperation system
CN102874697A (en) Hydraulic system for controlling amplitude variation of arm support and crane
CN105201944B (en) Flux amplification valve and steering hydraulic system
CN102889273B (en) Electro-hydraulic system for recycling and releasing potential energy of engineering machinery
CN103896156B (en) A kind of hoist energy-saving hydraulic system and hoist
CN202296914U (en) Telescopic arm control system and crane
CN102502433B (en) Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane
CN101408107A (en) Energy-saving type shield propulsion hydraulic system by using zone control
CN201288566Y (en) Energy-saving shield advance hydraulic system employing zone control
CN203604293U (en) Engineering mechanical equipment and hydraulic control circuit thereof
CN102561451A (en) Energy optimization system for hydraulic excavator
CN102874704B (en) Hydraulic system, hoisting mechanism and engineering machinery
CN104828135A (en) Hydraulic control system and mining dump truck with same
CN103085865A (en) Load sensitive turning hydraulic system of loading machine

Legal Events

Date Code Title Description
PB01 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model