CN103010980A - Rotary control hydraulic system and crane - Google Patents
Rotary control hydraulic system and crane Download PDFInfo
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- CN103010980A CN103010980A CN2012105279074A CN201210527907A CN103010980A CN 103010980 A CN103010980 A CN 103010980A CN 2012105279074 A CN2012105279074 A CN 2012105279074A CN 201210527907 A CN201210527907 A CN 201210527907A CN 103010980 A CN103010980 A CN 103010980A
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Abstract
The invention discloses a rotary control hydraulic system and a crane. The rotary control hydraulic system disclosed comprises a pilot oil passage, a hydraulic control main reversing valve for controlling the flow direction and on/off of a main oil passage by the pilot oil passage, and a cushion valve, wherein the cushion valve is provided with a first working oil port, a second working oil port and a control oil port for controlling the on/off of the first and the second working oil ports. When the first and the second working oil ports are communicated with each other, the high pressure segment of the main oil passage is communicated with an oil return passage through the cushion valve, the control oil port of the cushion valve is communicated with the pilot oil passage, a damp is arranged on a passage from the control oil port to the pilot oil passage, and the control oil port of the cushion valve is communicated with the pilot oil passage, and the pilot oil source is a low-pressure and stable oil source which is independent from a load pressure. Compared with the background art that the cushion valve is communicated with the feedback oil passage having larger fluctuation, the cushion valve, provided by the invention, is not affected by load fluctuation and can give a timely response for cushioning, so that the rotary system keeps more stable during start-up and stop.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly a kind of revolution control hydraulic efficiency pressure system and hoisting crane.
Background technology
The car hosit rotary control system mainly is can held stationary when guarantee starting and stopping, reliable and without impact, generally all be to realize this function by rotary buffering valve.
Please refer to Fig. 1, Fig. 1 is a kind of schematic diagram that turns round the control hydraulic efficiency pressure system in the prior art.
Among Fig. 1, mainly comprise fix-displacement pump, proportional control valve with the three-way pressure compensating device, independently cushion valve 11, proportional control valve is main reversing valve, cushion valve 11 is by pass valve, one actuator port of cushion valve 11 is communicated with oil return line, another actuator port is communicated with the second working connection 14 that is in the first working connection 13 of high pressure or is in high pressure by shuttle valve, the control port of cushion valve 11 is communicated with feedback oil circuit 12, when main reversing valve is positioned at left position or right position, and when being in static state, the built-in pressure of spring cavity that the pressure oil of feedback oil circuit 12 can enter cushion valve 11, the pressure oil of working connection can enter with spring in the chamber, oil pressure and spring force in the spring cavity can keep balance to cavity pressure with spring, and spool passed so that two actuator ports of cushion valve 11 remain open state, then the first working connection 13 and the second working connection 14 normally advance, oil return.In addition, the feedback oil circuit 12 that is communicated with cushion valve 11 is provided with damping 15
Start moment, because the existence of damping 15, cushion valve 11 spring cavitys are built the pressure time lag, be that spring cavity fails to set up high pressure at short notice, and spring is very fast to the pressure voltage built-up rate in the chamber, then the high pressure person between the first working connection 13 and the second working connection 14 can overcome cushion valve 11 interior spring pressures and conducting cushion valve 11, and then is communicated with oil return line, the buffer action when starting with realization.When treating that the spring cavity pressure rise is extremely identical with load, namely at ordinary times at a stalemate to the chamber oil pressure with spring, cushion valve 11 is closed again, returns to static state, then working connection normal operation.
Yet there is following technical matters in technique scheme:
The first, the control port of cushion valve 11 is communicated with feedback oil circuit 12, the pressure of feedback oil circuit 12 can fluctuate with the fluctuation of load pressure, and when higher or amplitude was larger when oscillation frequency, cushion valve 11 can't in time respond and cushion, can cause the system pressure fluctuation, external manifestation is shake;
Second, when handle returns meta (main reversing valve is positioned at meta among Fig. 1), working connection at the main reversing valve place by shutoff, because the factors such as the external structure part such as arm and inertia can cause power element (such as rotary motor among Fig. 1) in time to stop, but under effect of inertia, continue epitrochoidal chamber and the pipeline of rotary motor are compressed, the one-sided working connection that namely is in high pressure can continue high pressure, it is also higher correspondingly to feed back oil circuit 12 oil pressure, then the spring cavity of cushion valve 11 still is in high pressure and closes, can't discharge working connection pressure, can cause the cycle of higher pressure between two working connections, until actuator movement stops, causing shake;
When three, stopping, damping 15 also can cause the pressure of cushion valve 11 spring cavitys in time to discharge, and causes shake.
In view of this, how making the rotary system can be more steady when starting and stopping, be the technical matters that those skilled in the art need to be resolved hurrily.
Summary of the invention
Core of the present invention is for providing a kind of revolution control hydraulic efficiency pressure system and hoisting crane, and this hydraulic efficiency pressure system is so that rotary system can be more steady when starting and stopping.
For solving the problems of the technologies described above, the invention provides a kind of revolution control hydraulic efficiency pressure system, comprise guide's oil circuit, flowed to and the hydraulic control main reversing valve of break-make by described guide's oil circuit control working connection, and cushion valve; Described cushion valve has the first actuator port, the second actuator port, and the control port of controlling described the first actuator port, the second actuator port break-make, when described the first actuator port and described the second actuator port conducting, the high pressure section of described working connection is communicated with oil return line by described cushion valve, the described control port of described cushion valve is communicated with guide's oil circuit, and described control port to the path of described guide's oil circuit is provided with damping.
Preferably, the number of described cushion valve is two, described working connection comprises the first working connection and the second working connection between hydraulic control main reversing valve and power element, the first actuator port of two described cushion valves connects respectively described the first working connection and described the second working connection, and the second actuator port of two described cushion valves all is communicated with oil return line; Described hydraulic control main reversing valve has two control ends, and two described control ends are communicated with respectively two described guide's oil circuits, and the control port of two described cushion valves is communicated with respectively two described guide's oil circuits.
Preferably, described working connection comprises the first working connection and the second working connection between hydraulic control main reversing valve and power element, and described hydraulic control main reversing valve has two control ends, and two described control ends are communicated with respectively two described guide's oil circuits; The first actuator port of described cushion valve is communicated with the first working connection or the second working connection by the first shuttle valve, and the second actuator port of described cushion valve is communicated with oil return line, and the control port of described cushion valve is communicated with one in two described guide's oil circuits by the second shuttle valve.
Preferably, the described control port of described cushion valve is provided with check valve to the path of described guide's oil circuit, and described check valve and described damping are set up in parallel.
Preferably, described damping and described check valve are integrated in one.
Preferably, described hydraulic control main reversing valve is the type three-position four-way valve that surges.
The control port of cushion valve is communicated with guide's oil circuit in this invention, pilot control is low pressure and stable oil sources, irrelevant with load pressure, cushion valve is communicated with the larger feedback oil circuit of fluctuation in the background technology, cushion valve is not affected by the fluctuation of load among the present invention, can in time respond and cushion, so that rotary system is comparatively steady when starting and stopping.And rotary system is when stopping, guide's oil circuit pressure decreased, although one-sided working connection pressure is still higher under effect of inertia, but the pressure in the cushion valve spring cavity can pass through the successfully pressure release of guide's oil circuit, then the first actuator port of cushion valve and the second actuator port can keep conducting state, make the working connection of high pressure by the rapid pressure release of cushion valve, thereby when stopping, also can play preferably pooling feature.
The present invention also provides a kind of hoisting crane, comprises power element and drives the revolution control hydraulic efficiency pressure system that described power element moves, and described revolution control hydraulic efficiency pressure system is above-mentioned each described revolution control hydraulic efficiency pressure system.
Preferably, described power element is rotary motor.
Because above-mentioned revolution control hydraulic efficiency pressure system has above-mentioned technique effect, the hoisting crane with this revolution control hydraulic efficiency pressure system also has identical technique effect.
Description of drawings
Fig. 1 is a kind of schematic diagram that turns round the control hydraulic efficiency pressure system in the prior art;
Fig. 2 is the schematic diagram of a kind of specific embodiment of revolution control hydraulic efficiency pressure system provided by the present invention;
Fig. 3 is the schematic diagram of the another kind of specific embodiment of revolution control hydraulic efficiency pressure system provided by the present invention.
Among Fig. 1:
11 cushion valves, 12 feedback oil circuits, 13 first working connections, 14 second working connections, 15 dampings, P oil inlet, T return opening;
Among Fig. 2-3:
21 cushion valves, 211 first actuator ports, 212 second actuator ports, 213 control ports, 221 dampings, 222 check valves, 23 rotary motors, 241 first working connections, 242 second working connections, 25 hydraulic control main reversing valves, 26 guide's oil circuits, 27 first shuttle valves, 28 second shuttle valves, P oil inlet, T return opening
The specific embodiment
Core of the present invention is for providing a kind of revolution control hydraulic efficiency pressure system and hoisting crane, and this hydraulic efficiency pressure system is so that rotary system can be more steady when starting and stopping.
In order to make those skilled in the art understand better technical scheme of the present invention, the present invention is described in further detail below in conjunction with the drawings and specific embodiments.
Please refer to Fig. 2, Fig. 2 is the schematic diagram of a kind of specific embodiment of revolution control hydraulic efficiency pressure system provided by the present invention.
Revolution among this embodiment control hydraulic efficiency pressure system comprises guide's oil circuit 26, is flowed to and the hydraulic control main reversing valve 25 of break-make by guide's oil circuit 26 control working connections.As described in Figure 2, the spool of hydraulic control main reversing valve 25 moves to left or moves to right under 26 effects of guide oil road, thereby switches the flow direction or the break-make of working connection between hydraulic control main reversing valve 25 and the power element.Hydraulic control main reversing valve 25 among Fig. 2 is three-position four-way valve, it has two control ends, two control ends are communicated with respectively two guide's oil circuits 26, when left side guide's oil circuit 26 pressure raise, be positioned at left position, when right side guide's oil circuit 26 pressure raise, be positioned at right position, when both sides guide's oil circuit 26 pressure all reduce, be positioned at meta.Three-position four-way valve is suitable for the revolution control needs of this kind closed system, can expect that hydraulic control main reversing valve 25 also can be the six logical or pilot-operated type change-over valves of other types.
This revolution control hydraulic efficiency pressure system also comprises cushion valve 21, cushion valve 21 is by pass valve, has the first actuator port 211, the second actuator port 212, and control the first actuator port 211, the control port 213 of the second actuator port 212 break-makes, as shown in Figure 2, control port 213 is communicated with spring cavity, spring is communicated with its first actuator port 211 to the chamber, then high pressure oil flows to spring cavity and builds through control port 213 and presses and when with spring the chamber being maintained an equal level, the first actuator port 211 of cushion valve 21 and the second actuator port 212 disconnect, otherwise, the first actuator port 211 and 212 conductings of the second actuator port.When the first actuator port 211 and 212 conducting of the second actuator port, the high pressure section of working connection can be communicated with oil return line by cushion valve 21.Among Fig. 2, working connection comprises the first working connection 241 and the second working connection 242 between rotary motor 23 and the hydraulic control main reversing valve 25, when the first working connection 241 is high-pressure oil passage, the high pressure section of working connection is the first working connection 241, when the second working connection 242 switched to high-pressure oil passage, the high pressure section of working connection was the second working connection 242.Namely no matter the first working connection 241 is in high pressure or the second working connection 242 is in high pressure, and the working connection that is in high pressure all can be communicated with oil return lines by cushion valve 21.
In addition, in the present embodiment, the control port 213 of cushion valve 21 is communicated with guide's oil circuit 26.And control port 213 to the path of guide's oil circuit 26 is provided with damping 221, similar with the principles illustrated of background technology, the setting of damping 221 is intended to realize that cushion valve 21 spring cavitys are built is pressed in temporal sluggishness, thereby reaches instantaneous conducting cushion valve 21 and play buffer action.
Because the control port 213 of cushion valve 21 is communicated with guide's oil circuit 26 among this embodiment, guide's oil circuit 26 is low pressure and stable oil sources, irrelevant with load pressure, as can be seen from Figure 2, guide's oil circuit 26 mainly is to realize commutation for the spool that promotes hydraulic control main reversing valve 25.Cushion valve 21 is communicated with the larger feedback oil circuit of fluctuations in the background technology, the control port 213 of this cushion valve 21 is communicated with stable guide's oil circuit 26, then cushion valve 21 is not affected by the fluctuation of load among this embodiment, can in time respond and cushion, so that rotary system is comparatively steady when starting and stopping.And rotary system is when stopping, when hydraulic control main reversing valve 25 is in meta among Fig. 2, guide's oil circuit 26 pressure decreaseds, although one-sided working connection pressure is still higher under effect of inertia, but the pressure in cushion valve 21 spring cavitys can pass through successfully pressure release of guide's oil circuit 26, then the first actuator port 211 of cushion valve 21 and the second actuator port 212 can keep conducting state, make the working connection that keeps high pressure owing to inertia by cushion valve 21 rapid pressure releases, thereby when stopping, also can play preferably pooling feature.
Further, the number of cushion valve 21 is two among this embodiment, and as shown in Figure 2, the first actuator port 211 of two cushion valves 21 connects respectively the first working connection 241 and the second working connection 242, and the second actuator port 212 of two cushion valves 21 all is communicated with oil return line.Then the first working connection 241 is high-pressure oil passage, and when the second working connection 242 was low pressure oil way, the first working connection 241 can by cushion valve 21 bufferings in left side, during commutation, can pass through cushion valve 21 bufferings on right side as the second working connection 242 of high-pressure oil passage.Correspondingly, the control port 213 of two cushion valves 21 is communicated with respectively two guide's oil circuits 26 of both sides.Certainly in order to guarantee that cushion valve 21 can realize pooling feature; the working connection that cushion valve 21 first actuator ports 211 connect is positioned at the same side with guide's oil circuit 26 that its control port 213 is communicated with; when guaranteeing that namely cushion valve 21 is communicated with the working connection of high pressure, its control port 213 is communicated with guide's oil circuit 26 that pressure raises.
In above-described embodiment, hydraulic control main reversing valve 25 to each working connection between the power element is realized buffering by independent cushion valve 21, has avoided the interference in the crank motion.And when rotary motor 23 rotated and reverse, general pressure at both sides required different.Such as, among Fig. 2, when the first working connection 241 and the second working connection 242 are in high pressure respectively, the high-pressure demand may be different, and the buffering of cushion valve 21 depends on that spring cavity pressure and spring are to cavity pressure (corresponding working connection pressure), after two cushion valves 21 were set, each cushion valve 21 can be regulated according to the working connection pressure of correspondence, has increased the adjustability of pooling feature.
When two cushion valves 21 is set, the control port 213 of cushion valve 21 can arrange check valve 222 to the path of guide's oil circuit 26, check valve 222 and damping 221 are set up in parallel, be that control port 213 has two paths with guide's oil circuit 26, as shown in Figure 2, the hydraulic oil of guide's oil circuit 26 can flow to control port 213 through damping 221, and hydraulic oil can flow back to guide's oil circuit 26 through check valve 222 from control port 213 in cushion valve 21 spring cavitys.After check valve 222 was set, when rotary system stopped, the hydraulic oil in the spring cavity can be back to rapidly 26 pressure releases of guide's oil circuit through check valve 222, rather than through damping 221 slow pressure releases, further improved the buffering effect that stops moment.The damping 221 and the check valve 222 that arrange can be integrated in one, and form one-way damper valve, are convenient to install and simplify piping layout.
Adopt two cushion valves 21 in above-described embodiment, produced aforesaid technique effect, and realize that stable buffering does not arrange two cushion valves 21 and is fine yet.Please refer to Fig. 3, Fig. 3 is the schematic diagram of the another kind of specific embodiment of revolution control hydraulic efficiency pressure system provided by the present invention.This embodiment only arranges a cushion valve 21.
Equally, working connection comprises the first working connection 241 and the second working connection 242 between hydraulic control main reversing valve 25 and the rotary motor 23, and hydraulic control main reversing valve 25 has two control ends, and two control ends are communicated with respectively two guide's oil circuits 26.The first actuator port 211 of cushion valve 21 is communicated with the first working connection 241 or the second working connections 242 by the first shuttle valve 27, namely during the first working connection 241 high pressure, when being communicated with the first working connection 241, the second working connections 242 high pressure, is communicated with the second working connection 242.In addition, the second actuator port 212 of cushion valve 21 is communicated with oil return line, 213 one that are communicated with in two guide's oil circuits 26 by the second shuttle valve 28 of the control port of cushion valve 21.
Consistent with above-described embodiment principle, in order to realize pooling feature, when the first actuator port 211 of cushion valve 21 was communicated with the high-pressure main oil path of a side, its control port 213 was communicated with guide's oil circuit 26 of the pressure rising of homonymy.This embodiment is communicated with guide's oil circuit 26 with the control port 213 of cushion valve 21 equally, so that the startup of rotary system and stop all accessing effective buffering, reduce and impact, and a cushion valve 21 also can be simplified the hydraulic tubing layout, certainly, compared to above-described embodiment, the adjustability of cushion valve buffering is taken second place among this embodiment.
When a cushion valve 21 only is set, also can damping arranged side by side 222 and check valve 221 be set at cushion valve 21 control ports 213 to guide's oil circuit 26.As shown in Figure 3, after the hydraulic oil of left side guide's oil circuit 26 enters the spring cavity of cushion valve 21 through left side damping 222, the 28 left side conductings of the second shuttle valve, then spring cavity can pass through the 28 left side oil circuit oil return pressure releases of the second shuttle valve; Right side guide's oil circuit 26 hydraulic oil are after right side damping 222 enters cushion valve 21 spring cavitys, the 28 right side conductings of the second shuttle valve, spring cavity can pass through right side oil circuit oil return pressure release, as seen among this embodiment check valve 221 the technique effect that can reach same with above-described embodiment is set.In addition, same as the previously described embodiments, damping 222 and the check valve 221 formation one-way damper valve that can be integrated in one.
Need to prove, for the various embodiments described above, answer the ratio of the area (acting on spring to the chamber) of the area (acting on spring cavity) of guide's oil circuit effect on the appropriate design cushion valve 21 and the effect of load oil sources, this ratio is crossed conference and is caused buffering effect bad, and the pressure excess gradient is larger; Inadequate and the cal val increase of speed of revolutions affected work efficiency when the too small meeting of ratio caused heavy duty.
The present invention also provides a kind of hoisting crane, comprises power element and drives the revolution control hydraulic efficiency pressure system that power element moves, and described revolution control hydraulic efficiency pressure system is the described revolution control of above-mentioned arbitrary embodiment hydraulic efficiency pressure system.Because above-mentioned revolution control hydraulic efficiency pressure system has above-mentioned technique effect, the hoisting crane with this revolution control hydraulic efficiency pressure system also has identical technique effect, repeats no more herein.Power element specifically can be rotary motor 23, shown in Fig. 2,3.
More than a kind ofly state revolution control hydraulic efficiency pressure system and hoisting crane all is described in detail to provided by the present invention.Used specific case herein principle of the present invention and embodiment are set forth, the explanation of above embodiment just is used for helping to understand method of the present invention and core concept thereof.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 carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of claim of the present invention.
Claims (8)
1. revolution control hydraulic efficiency pressure system comprises guide's oil circuit (26), is flowed to and the hydraulic control main reversing valve (25) of break-make by described guide's oil circuit (26) control working connection, and cushion valve (21); Described cushion valve (21) has the first actuator port (211), the second actuator port (212), and control described the first actuator port (211), the control port (213) of the second actuator port (212) break-make, when described the first actuator port (211) and described the second actuator port (212) conducting, the high pressure section of described working connection is communicated with oil return line by described cushion valve (21), it is characterized in that, the described control port (213) of described cushion valve (21) is communicated with guide's oil circuit (26), and described control port (213) to the path of described guide's oil circuit (26) is provided with damping (222).
2. hydraulic efficiency pressure system is controlled in revolution as claimed in claim 1, it is characterized in that, the number of described cushion valve (21) is two, described working connection comprises the first working connection (241) and the second working connection (242) that is positioned between hydraulic control main reversing valve (25) and the power element, first actuator port (211) of two described cushion valves (21) connects respectively described the first working connection (241) and described the second working connection (242), and second actuator port (212) of two described cushion valves (21) all is communicated with oil return line; Described hydraulic control main reversing valve (25) has two control ends, and two described control ends are communicated with respectively two described guide's oil circuits (26), and the control port (213) of two described cushion valves (21) is communicated with respectively two described guide's oil circuits (26).
3. hydraulic efficiency pressure system is controlled in revolution as claimed in claim 1, it is characterized in that, described working connection comprises the first working connection (241) and the second working connection (242) that is positioned between hydraulic control main reversing valve (25) and the power element, described hydraulic control main reversing valve (25) has two control ends, and two described control ends are communicated with respectively two described guide's oil circuits (26); First actuator port (211) of described cushion valve (21) is communicated with the first working connection (241) or the second working connection (242) by the first shuttle valve (27), second actuator port (212) of described cushion valve (21) is communicated with oil return line, and the control port (213) of described cushion valve (21) is communicated with the one of (26) in two described guide's oil circuits by the second shuttle valve (28).
4. such as each described revolution control hydraulic efficiency pressure system of claim 1-3, it is characterized in that, the described control port (213) of described cushion valve (21) is provided with check valve (221) to the path of described guide's oil circuit (26), and described check valve (221) and described damping (222) are set up in parallel.
5. revolution control hydraulic efficiency pressure system as claimed in claim 4 is characterized in that described damping (222) and described check valve (221) are integrated in one.
6. such as each described revolution control hydraulic efficiency pressure system of claim 1-3, it is characterized in that described hydraulic control main reversing valve (25) is the type three-position four-way valve that surges.
7. a hoisting crane comprises power element and drives the revolution control hydraulic efficiency pressure system that described power element moves, and it is characterized in that, described revolution control hydraulic efficiency pressure system is each described revolution control hydraulic efficiency pressure system of claim 1-6.
8. hoisting crane as claimed in claim 7 is characterized in that, described power element is rotary motor (23).
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| CN201210527907.4A CN103010980B (en) | 2012-12-10 | 2012-12-10 | Rotary control hydraulic system and crane |
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| CN201210527907.4A CN103010980B (en) | 2012-12-10 | 2012-12-10 | Rotary control hydraulic system and crane |
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Cited By (10)
| 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 |
| CN103727076A (en) * | 2013-11-19 | 2014-04-16 | 徐州重型机械有限公司 | Hydraulic-controlled rotation control device and crane rotation system |
| CN104912136A (en) * | 2015-05-28 | 2015-09-16 | 潍柴动力股份有限公司 | Excavator and rotational hydraulic system thereof |
| CN105443469A (en) * | 2015-12-21 | 2016-03-30 | 山河智能装备股份有限公司 | Hydraulic control device for speed of engineering machine |
| CN106414306A (en) * | 2014-03-04 | 2017-02-15 | 马尼托瓦克起重机有限责任公司 | Electronically controlled hydraulic swing system |
| CN106629396A (en) * | 2016-12-23 | 2017-05-10 | 徐州重型机械有限公司 | Electro-hydraulic union speed adjustment rotary system for crane and control method |
| CN107152429A (en) * | 2017-06-26 | 2017-09-12 | 常德中联重科液压有限公司 | Engineering machinery, hydraulic control circuit and valve terminal |
| CN107269628A (en) * | 2017-07-28 | 2017-10-20 | 重集团大连工程技术有限公司 | A kind of vertical heavy load stall protection loop |
| CN111891949A (en) * | 2020-07-24 | 2020-11-06 | 徐州重型机械有限公司 | Open type rotation control system |
| CN114623114A (en) * | 2022-05-17 | 2022-06-14 | 中海油能源发展股份有限公司采油服务分公司 | Hydraulic rotation control system of marine hose crane |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004044309A (en) * | 2002-07-15 | 2004-02-12 | Hitachi Constr Mach Co Ltd | Rotation control device for construction machine |
| CN102269189A (en) * | 2011-07-04 | 2011-12-07 | 长沙中联重工科技发展股份有限公司 | Hydraulic control loop |
| CN102515042A (en) * | 2011-12-20 | 2012-06-27 | 浙江大学 | Rotation buffering circuit |
| CN202337656U (en) * | 2011-11-25 | 2012-07-18 | 常德中联重科液压有限公司 | Electro-hydraulic rotation control valve and automobile crane |
| CN202967952U (en) * | 2012-12-10 | 2013-06-05 | 徐州重型机械有限公司 | Rotary control hydraulic system and crane |
-
2012
- 2012-12-10 CN CN201210527907.4A patent/CN103010980B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004044309A (en) * | 2002-07-15 | 2004-02-12 | Hitachi Constr Mach Co Ltd | Rotation control device for construction machine |
| CN102269189A (en) * | 2011-07-04 | 2011-12-07 | 长沙中联重工科技发展股份有限公司 | Hydraulic control loop |
| CN202337656U (en) * | 2011-11-25 | 2012-07-18 | 常德中联重科液压有限公司 | Electro-hydraulic rotation control valve and automobile crane |
| CN102515042A (en) * | 2011-12-20 | 2012-06-27 | 浙江大学 | Rotation buffering circuit |
| CN202967952U (en) * | 2012-12-10 | 2013-06-05 | 徐州重型机械有限公司 | Rotary control hydraulic system and crane |
Cited By (16)
| 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 |
| CN103727076B (en) * | 2013-11-19 | 2016-04-27 | 徐州重型机械有限公司 | A kind of hydraulic control rotation control device and crane rotation system |
| CN103727076A (en) * | 2013-11-19 | 2014-04-16 | 徐州重型机械有限公司 | Hydraulic-controlled rotation control device and crane rotation system |
| CN106414306B (en) * | 2014-03-04 | 2018-10-09 | 马尼托瓦克起重机有限责任公司 | Electric-controlled type hydraulic rocking system |
| CN106414306A (en) * | 2014-03-04 | 2017-02-15 | 马尼托瓦克起重机有限责任公司 | Electronically controlled hydraulic swing system |
| US9878886B2 (en) | 2014-03-04 | 2018-01-30 | Manitowoc Crane Companies, Llc | Electronically controlled hydraulic swing system |
| US10906786B2 (en) | 2014-03-04 | 2021-02-02 | Manitowoc Crane Companies, Llc | Electronically controlled hydraulic swing system |
| CN104912136A (en) * | 2015-05-28 | 2015-09-16 | 潍柴动力股份有限公司 | Excavator and rotational hydraulic system thereof |
| CN105443469A (en) * | 2015-12-21 | 2016-03-30 | 山河智能装备股份有限公司 | Hydraulic control device for speed of engineering machine |
| CN106629396A (en) * | 2016-12-23 | 2017-05-10 | 徐州重型机械有限公司 | Electro-hydraulic union speed adjustment rotary system for crane and control method |
| CN106629396B (en) * | 2016-12-23 | 2018-05-18 | 徐州重型机械有限公司 | A kind of crane electro-hydraulic joint speed governing rotary system and control method |
| CN107152429A (en) * | 2017-06-26 | 2017-09-12 | 常德中联重科液压有限公司 | Engineering machinery, hydraulic control circuit and valve terminal |
| CN107152429B (en) * | 2017-06-26 | 2018-09-07 | 常德中联重科液压有限公司 | Engineering machinery, hydraulic control circuit and valve terminal |
| CN107269628A (en) * | 2017-07-28 | 2017-10-20 | 重集团大连工程技术有限公司 | A kind of vertical heavy load stall protection loop |
| CN111891949A (en) * | 2020-07-24 | 2020-11-06 | 徐州重型机械有限公司 | Open type rotation control system |
| CN114623114A (en) * | 2022-05-17 | 2022-06-14 | 中海油能源发展股份有限公司采油服务分公司 | Hydraulic rotation control system of marine hose crane |
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| CN103010980B (en) | 2015-05-13 |
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