Hydraulic transmission system and crane
阅读说明:本技术 液压传动系统和起重机 (Hydraulic transmission system and crane ) 是由 李武 胡廷江 李英智 沈昌武 于 2019-10-18 设计创作,主要内容包括:本发明涉及工程机械技术领域,公开了一种液压传动系统和起重机。所述液压传动系统包括主控制油路和辅助控制油路;所述主控制油路包括第一动力单元(1)和执行单元以及连接在所述第一动力单元(1)和所述执行单元之间用于控制所述执行单元动作的第一控制模块(2);所述辅助控制油路输出的液压油能够和从所述第一控制模块(2)输出的液压油合流以控制所述执行单元。该液压传动系统既能保证使用这种液压传动系统的设备在重载时拥有良好的微动性能,又能够在轻载和空载时满足对高速的要求,并能够节约成本。(The invention relates to the technical field of engineering machinery and discloses a hydraulic transmission system and a crane. The hydraulic transmission system comprises a main control oil way and an auxiliary control oil way; the main control oil circuit comprises a first power unit (1), an execution unit and a first control module (2) which is connected between the first power unit (1) and the execution unit and used for controlling the action of the execution unit; the hydraulic oil output by the auxiliary control oil path can be combined with the hydraulic oil output by the first control module (2) to control the execution unit. The hydraulic transmission system can ensure that equipment using the hydraulic transmission system has good micromotion performance during heavy load, can meet the requirement on high speed during light load and no load, and can save cost.)
1. A hydraulic transmission system is characterized by comprising a main control oil way and an auxiliary control oil way; the main control oil circuit comprises a first power unit (1), an execution unit and a first control module (2) which is connected between the first power unit (1) and the execution unit and used for controlling the action of the execution unit; the hydraulic oil output by the auxiliary control oil path can be combined with the hydraulic oil output by the first control module (2) to control the execution unit.
2. The hydraulic transmission system according to claim 1, wherein the main control circuit comprises a first power unit (1) and the auxiliary control circuit comprises a second power unit (8); the first power unit (1) and the second power unit (8) are different.
3. The hydraulic transmission system according to claim 2, characterized in that the auxiliary control circuit comprises a second control module (6) connected between the second power unit (8) and the actuator unit for controlling the actuator unit, and a first non-return valve (9); the execution unit comprises a first pressure cylinder (3); a T port of the second control module (6) returns oil, and a P port of the second control module (6) is communicated with the second power unit (8); an oil inlet of the first check valve (9) is connected with a working oil port of the second control module (6), and the working oil port of the first check valve (9) is communicated with a rodless cavity of the first pressure cylinder (3).
4. A hydraulic transmission system according to claim 3, characterized in that a first balancing valve (31) for protecting the first pressure cylinder (3) is arranged in the oil circuit between the first pressure cylinder (3) and the first control module (2); a second balance valve (41) used for protecting the second pressure cylinder (4) is arranged on an oil path between the second pressure cylinder (4) and the first control module (2); the working oil path of the first check valve (9) to the first pressure cylinder (3) or the second pressure cylinder (4) intersects with the working oil path from the first control module (2) to the rodless chamber of the first pressure cylinder (3) or the rodless chamber of the second pressure cylinder (4) between the first or second counter valve (31, 41) and the first control module (2).
5. The hydraulic transmission system according to claim 4, wherein the auxiliary control oil circuit further comprises a second check valve (9 '), oil inlets of the first check valve (9) and the second check valve (9') are respectively communicated with a working oil port A and a working oil port B of the second control module (6); the oil outlets of the first check valve (9) and the second check valve (9') are respectively communicated with the rodless cavities of the first pressure cylinder (3) and the second pressure cylinder (8); the working oil passages leading from the first check valve (9) to the first pressure cylinder (3) and from the second pressure cylinder (4) to the second check valve (9') intersect working oil passages leading from the first control module (2) to the rodless chamber of the first pressure cylinder (3) and from the first control module (2) to the rodless chamber of the second pressure cylinder (4), respectively, between the first balancing valve (31) and the first control module 2, and between the second balancing valve (41) and the first control module (2).
6. The hydraulic transmission system according to claim 5, characterized in that the first control module (2) comprises a plurality of valve plates; and each valve plate controls the corresponding execution unit.
7. The hydraulic transmission system of claim 6, wherein the valve plate comprises a first valve plate (21) and a second valve plate (22); a working oil port A1 and a working oil port B1 of the first valve plate (21) are respectively communicated with a rodless cavity and a rod cavity of a first pressure cylinder (3) of the execution unit; and a working oil port A2 and a working oil port B2 of the second valve plate (22) are respectively communicated with a rodless cavity and a rod cavity of the second pressure cylinder (4).
8. The hydraulic transmission system according to claim 7, characterized in that a working oil passage leading from the first check valve (9) to the first pressure cylinder (3) and a working oil passage leading from the first valve plate (21) to a rodless chamber of the first pressure cylinder (3) in the auxiliary control oil passage intersect between the first balance valve (31) and the first valve plate (21); and a working oil path leading from the second check valve (9') to the second pressure cylinder (4) in the auxiliary control oil path intersects with a working oil path leading from the second valve plate (22) to a rodless chamber of the second pressure cylinder (4) between the second balance valve (41) and the second valve plate (22).
9. The hydraulic transmission system according to claim 5, characterized in that the second control module (6) comprises an electro-hydraulic proportional valve; a port P of the electro-hydraulic proportional valve is communicated with a second power unit (8) of the auxiliary control oil way, and a port T of the electro-hydraulic proportional valve is communicated with an oil return way of the hydraulic transmission system; a working oil port A of the electro-hydraulic proportional valve is communicated with an oil inlet of the one-way valve (9); and a working oil port B of the electro-hydraulic proportional valve is communicated with an oil inlet of the second single valve (9').
10. The hydraulic transmission system according to claim 1, further comprising a makeup line (7) for replenishing oil to an oil return line of the hydraulic transmission system, a T port of the second control module (6) of the auxiliary control oil line leading to the makeup line (7).
11. A crane, characterized by comprising a hydraulic transmission system according to any one of claims 1-10.
Technical Field
The invention relates to the field of engineering machinery, in particular to a hydraulic transmission system and a crane.
Background
With the wide application of large-tonnage cranes in the market, users have higher requirements on the pressure and the inching property of amplitude-variable lifting, and gradually improve the requirements on the amplitude-variable speed of no-load and light load; the requirement on the telescopic speed of the suspension arm is gradually increased. Under normal conditions, the power unit adopts a variable pump 1'; the first control module 2 'adopts a plurality of large-flow electro-hydraulic proportional valves, wherein one control module is used for controlling the luffing mechanism 3', one control module is used for controlling the boom telescoping mechanism 4 ', and the other control module is used for controlling the hoisting mechanism 5', so that the requirements of a common crane can be met. In order to meet the requirements of customers on the amplitude variation speed of no-load and light-load and the telescopic speed of the suspension arm, as shown in fig. 1, in an embodiment, a valve plate needs to be additionally arranged on an amplitude variation mechanism 3' to meet the requirements on high-speed amplitude variation during no-load and light-load; the boom extension mechanism 4' needs to be additionally provided with a valve plate to meet the requirement of high-speed extension of the boom during no-load and light-load; therefore, two valve plates are needed to be added to the first control module 2 'on the original basis, wherein the first valve plate 21' and the second valve plate 21 'are used for controlling the amplitude variation mechanism 3'; the third valve plate 22 ' and the fourth valve plate 22 ' are used for controlling the boom extension mechanism 4 ', and the 5 th valve plate 23 ' is used for controlling the hoisting mechanism 5 '; therefore, on one hand, the size of the first control module 2' is increased, the whole machine arrangement is not facilitated, on the other hand, the cost is improved, and the micro-motion performance of the crane is reduced. Therefore, a hydraulic transmission system is urgently needed, and a crane with the hydraulic transmission system can ensure that the crane has good micromotion performance when the crane is subjected to amplitude variation and heavy load at low speed, and can meet the requirements of amplitude variation at high speed and telescopic boom at high speed when the crane is subjected to light load and no load.
Disclosure of Invention
The invention aims to solve the problems that the amplitude variation speed of no-load and light-load and the telescopic speed of a suspension arm are improved by using a plurality of large-flow electro-hydraulic proportional valves as main valves in the prior art, so that the production cost is improved and the micro-motion performance of the suspension arm is reduced, and provides a hydraulic transmission system which can ensure that a crane using the hydraulic transmission system has good micro-motion performance at low speed of amplitude variation and heavy load, can have higher amplitude variation speed and suspension arm telescopic speed at light load and no-load, and saves the cost.
In order to achieve the above object, an aspect of the present invention provides a hydraulic transmission system including a main control oil passage and an auxiliary control oil passage; the main control oil circuit comprises a first power unit, an execution unit and a first control module which is connected between the first power unit and the execution unit and used for controlling the action of the execution unit; the hydraulic oil output from the auxiliary control oil passage can be merged with the hydraulic oil output from the first control module to control the execution unit.
Further, the main control oil path comprises a first power unit, and the auxiliary control oil path comprises a second power unit; the first power unit and the second power unit are different.
Further, the auxiliary control oil path comprises a second control module and a first one-way valve, wherein the second control module and the first one-way valve are connected between the second power unit and the execution unit and used for controlling the execution unit; the execution unit comprises a first pressure cylinder; a T port of the second control module returns oil, and a P port of the second control module is communicated with the second power unit; an oil inlet of the first check valve is connected with a working oil port of the second control module, and the working oil port of the first check valve is communicated with a rodless cavity of the first pressure cylinder.
Further, a first balance valve used for protecting the first pressure cylinder is arranged on an oil path between the first pressure cylinder and the first control module; a second balance valve used for protecting the second pressure cylinder is arranged on an oil path between the second pressure cylinder and the first control module; the working oil path of the first check valve to the first pressure cylinder or the second pressure cylinder intersects with the working oil path from the first control module to the rodless chamber of the first pressure cylinder or the rodless chamber of the second pressure cylinder between the first or second counter valve and the first control module.
Further, the auxiliary control oil path further comprises a second one-way valve, and oil inlets of the first one-way valve and the second one-way valve are respectively communicated with a working oil port A and a working oil port B of the second control module; oil outlets of the first check valve and the second check valve are respectively communicated with rodless cavities of the first pressure cylinder and the second pressure cylinder; the working oil passages of the auxiliary control oil passage leading from the first check valve to the first pressure cylinder and from the second pressure cylinder to the second check valve intersect the working oil passages of the rodless chamber leading from the first control module to the first pressure cylinder and the rodless chamber leading from the first control module to the second pressure cylinder, between the first counter balance valve and the
Further, the first control module comprises a plurality of valve plates; and each valve plate controls the corresponding execution unit.
Further, the valve plate comprises a first valve plate and a second valve plate; the working oil port A1 and the working oil port B1 of the first valve plate are respectively communicated with a rodless cavity and a rod cavity of a first pressure cylinder of the execution unit; and the working oil port A2 and the working oil port B2 of the second valve plate are respectively communicated with the rodless cavity and the rod cavity of the second pressure cylinder.
Further, a working oil path leading from the first check valve to the first pressure cylinder in the auxiliary control oil path intersects with a working oil path leading from the first valve plate to a rodless chamber of the first pressure cylinder between the first balance valve and the first valve plate; and a working oil passage leading from the second check valve to the second pressure cylinder in the auxiliary control oil passage intersects with a working oil passage leading from the second land to a rodless chamber of the second pressure cylinder between the second balance valve and the second land.
Further, the second control module comprises an electro-hydraulic proportional valve; a port P of the electro-hydraulic proportional valve is communicated with a second power unit of the auxiliary control oil way, and a port T of the electro-hydraulic proportional valve is communicated with an oil return way of the hydraulic transmission system; a working oil port A of the electro-hydraulic proportional valve is communicated with an oil inlet of the one-way valve; and a working oil port B of the electro-hydraulic proportional valve is communicated with an oil inlet of the second single valve.
Furthermore, the hydraulic transmission system further comprises an oil supplementing path used for supplementing oil to an oil return path of the hydraulic transmission system, and a T port of a second control module of the auxiliary control oil path leads to the oil supplementing path.
In a second aspect, the invention provides a crane comprising the hydraulic transmission described above
According to the technical scheme, the auxiliary control oil way is additionally arranged outside the main control oil way, and the hydraulic oil output by the auxiliary control oil way can be converged with the hydraulic oil output by the first control module to control the execution unit. The hydraulic transmission system can ensure that equipment using the hydraulic transmission system has good micromotion performance during heavy load, can meet the requirement on high speed during light load and no load, and can save cost.
Drawings
FIG. 1 is a diagram of a prior art hydraulic drive system;
FIG. 2 is a diagram of a hydraulic drive system according to an embodiment of the present invention;
FIG. 3 is a diagram of a hydraulic drive system according to another embodiment of the present invention;
FIG. 4 is an enlarged view of the second control module of FIG. 2.
Description of the reference numerals
A variable pump 1'; a first control module 2'; a first valve plate 21'; a
Detailed Description
The following detailed description of embodiments of the invention refers to the accompanying drawings. In the present invention, it is to be understood that the terms "away", "toward", "upper", "lower", "front", "rear", "left", "right", and the like indicate an orientation or positional relationship corresponding to an orientation or positional relationship in actual use; "inner and outer" refer to the inner and outer relative to the profile of the components themselves; this is done solely for the purpose of facilitating the description of the invention and simplifying the description without indicating that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation and therefore should not be construed as limiting the invention.
In the invention, the "micro-motion performance" refers to the capability of finely adjusting a hoisting mechanism or an amplitude variation mechanism when the crane lifts or amplitudes to ensure that a load reaches an accurate positioning position.
The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
The invention provides a hydraulic transmission system, which comprises a main control oil way and an auxiliary control oil way, wherein the main control oil way is connected with the auxiliary control oil way; the main control oil circuit comprises a
The
Preferably, the auxiliary control oil circuit comprises a
By providing the
The
Preferably, a first balance valve 31 for protecting the first pressure cylinder 3 is arranged on an oil path between the first pressure cylinder 3 and the
The balance protection control of the first pressure cylinder 3 can be realized by arranging the first balance valve 31, and the protection effect can be realized in the case of oil pipe burst or leakage. So that it serves its maximum function.
Preferably, the auxiliary control oil path further includes a second check valve 9 ', and oil inlets of the
Preferably, the
Preferably, the valve plates include a
Preferably, a working oil path leading from the
In order to control the auxiliary control oil path to perform the switching of the oil supply and oil supply stop states of the execution unit, a control valve needs to be arranged in the
The electro-hydraulic proportional valve comprises a proportional
Preferably, the hydraulic transmission system further comprises an
Preferably, the
In a second aspect, the invention provides a crane comprising a hydraulic transmission system as described above.
In a specific embodiment, the crane comprises an upper crane and a lower crane, wherein the upper crane comprises an execution unit, and the execution unit comprises a luffing mechanism, a suspension arm telescopic mechanism and a hoisting mechanism, wherein the luffing mechanism adopts a first pressure cylinder 3 for luffing; and the boom stretching mechanism adopts a second pressure cylinder 4 to stretch the boom. The lifting mechanism adopts a third execution unit 5 to lift and lower the heavy object, and the third execution unit 5 comprises a motor with large torque. Therefore, the crane can realize the functions of heavy load and slow speed.
The
The
The load-sensitive multi-way reversing valve set adopted in the
In the application, preferably, when the luffing mechanism and the boom mechanism are under light load or no load, the rapid telescoping of the first pressure cylinder 3 or the second pressure cylinder 4 is controlled by adopting a mode of confluence of hydraulic oil output by the auxiliary control oil path and hydraulic oil output from the
Further preferably, the power units for providing pressure oil for the main control oil circuit and the auxiliary control oil circuit respectively adopt two power units with different structural forms, namely a
Further preferably, the
When the upper engine is started and the whole crane does not act, the hydraulic oil output by the gear pump enters the
When the load is light or no load, the amplitude variation action of the amplitude variation mechanism can adopt a high-speed mode. At the moment, the hydraulic oil output by the gear pump 5 passes through the port A of the electro-hydraulic reversing valve, is converged with the hydraulic oil output from the
When the heavy load is carried out, the amplitude variation action can adopt a more accurate control mode. At the moment, hydraulic oil output by the gear pump enters the
If only one of the first pressure cylinder 3 of the luffing mechanism or the second pressure cylinder 4 of the boom extension mechanism needs to be extended quickly, what can be achieved by adding a valve plate to the
In the scheme, an oil inlet path leading to a rodless cavity of the first pressure cylinder 3 is only required to be arranged at the working oil port a of the electro-hydraulic proportional valve or the working oil port B of the electro-hydraulic proportional valve, and correspondingly, an oil inlet facing the electro-hydraulic proportional valve and an oil outlet facing the
If both of the first and second pressure cylinders 3, 4 have a need for a fast extension during crane operation, but may not simultaneously extend fast, the solution shown in fig. 2 may be used. Namely, an oil inlet channel leading to the rodless cavity of one of the first pressure cylinder 3 and the second pressure cylinder 4 is arranged from the working oil port a of the electro-hydraulic proportional valve, another oil inlet channel leading to the rodless cavity of the other of the first pressure cylinder 3 and the second pressure cylinder 4 is arranged from the working oil port B of the electro-hydraulic proportional valve, and the two oil inlet channels are respectively provided with a one-way valve with an oil inlet facing the electro-hydraulic proportional valve so as to prevent the hydraulic oil in the first pressure cylinder 3 or the second pressure cylinder 4 from being discharged from the auxiliary control oil channel.
Similarly, if the upper vehicle comprises a plurality of luffing mechanisms or boom telescoping mechanisms, the high-speed requirement can be realized by a plurality of luffing mechanisms or boom telescoping mechanisms by the similar scheme of the invention. The arrangement reduces the cost, and the control of the amplitude variation speed of the crane and the telescopic speed of the suspension arm is more reasonable and flexible. Wherein, the
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, but the present invention is not limited thereto. Within the technical concept scope of the invention, the technical scheme of the invention can be simply modified, for example, if only the extension speed of the luffing mechanism needs to be increased, the technical scheme can be realized by only adding one valve plate, and the technical scheme can also be adopted; similarly, if only the boom extension speed of the boom extension mechanism needs to be raised, the similar scheme of the present invention can be used, that is, as shown in fig. 3, when only one of the first pressure cylinder 3 or the second pressure cylinder 4 needs to be extended and retracted quickly, the similar scheme can be used. The valve plates in the
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