WO2015035903A1 - 一种摇摆机构及混凝土泵送设备 - Google Patents

一种摇摆机构及混凝土泵送设备 Download PDF

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WO2015035903A1
WO2015035903A1 PCT/CN2014/086185 CN2014086185W WO2015035903A1 WO 2015035903 A1 WO2015035903 A1 WO 2015035903A1 CN 2014086185 W CN2014086185 W CN 2014086185W WO 2015035903 A1 WO2015035903 A1 WO 2015035903A1
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stage
cylinder
piston
cavity
piston rod
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PCT/CN2014/086185
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English (en)
French (fr)
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胡任
黄勃
康磊
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三一汽车制造有限公司
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Publication of WO2015035903A1 publication Critical patent/WO2015035903A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/061—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement by unidirectional means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous

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  • the invention relates to the field of engineering machinery, in particular to a rocking mechanism and a concrete pumping device of a concrete pumping device.
  • the pumping mechanism of the existing concrete pump includes a main cylinder 1a, 1b, a water tank 2, a transfer cylinder 3a, 3b, a weir piston 4a, 4b, a rocking mechanism, a stirring system 6, a hopper 7, and a distribution valve 8. And other parts.
  • the swing mechanism is composed of two left and right swing valve cylinders 5a, 5b and a swing arm. In the pumping state, under the action of the master cylinders 1a, 1b, the piston 4b is advanced, 4a is retracted, at this time, the swing valve cylinder 5b of the swing mechanism is in the extended state, 5a is in the retracted state, and the swing arm drives the distribution valve 8 to swing.
  • the distribution valve 8 is connected to the concrete delivery cylinder 3b, and the concrete inside the 3b is pushed by the distribution valve 8 into the delivery pipe under the push of the piston 4b; and the concrete in the hopper 7 is sucked into the concrete delivery cylinder 3a by the continuously retreating piston 4a.
  • the control system sends a signal to cause the swing valve cylinder 5a to extend, 5b to retreat, and the swing valve cylinders 5a, 5b are reversing into position, and a signal is sent to cause the main cylinders 1a, 1b to reverse, pushing the piston 4a advances, 4b retreats, and the concrete sucked into the transfer cylinder 3a in the previous round is pushed into the distribution valve 8, and then enters the conveying pipe, and at the same time, the conveying cylinder 3b sucks. This repeated action completes the pumping of the concrete material.
  • the commutation speed is required to be fast, and the impact is small.
  • the reversing time of the left and right swing valve cylinders 5a, 5b is close to or even smaller than the commutation time of the main cylinders 1a, 1b, which can greatly Improve pumping continuity.
  • the existing swing valve cylinder is a single-stage hydraulic cylinder, and the swing valve cylinder is composed of a piston rod assembly and a cylinder barrel.
  • the distribution valve of the swing mechanism has a large static friction resistance at the initial stage of starting, and the hydraulic system pipeline has a limited flow capacity. Hydraulic cylinder design needs to weigh the pros and cons. in case The cylinder diameter is too large.
  • the present invention proposes a rocking mechanism and a concrete pumping device to solve the above problems in the rocking mechanism.
  • the present invention provides a rocking mechanism for driving a dispensing valve swing of a concrete pumping apparatus, including a swing arm for driving a dispensing valve, two hydraulic cylinders for driving swinging of the swing arm, and two hydraulic cylinders One end is connected to the left and right sides of the swing arm, and the hydraulic cylinder is a two-stage hydraulic cylinder.
  • the two-stage hydraulic cylinder comprises a cylinder, a first-stage piston and a piston rod assembly, and the first-stage piston cooperates with the inner cavity of the cylinder, the first-stage piston is provided with a cavity, and the piston rod assembly has one end and the first The cavity of the stage piston fits.
  • first stage piston is provided with a first inlet and outlet port and a second inlet and outlet port, the first inlet and outlet ports communicate with the rodless cavity of the cylinder tube, and the second inlet and outlet ports communicate with the rod cavity of the cylinder barrel.
  • a buffer hole is arranged on the rodless cavity end cover of the cylinder tube, and one end of the piston rod assembly is provided with a buffer rod, and the buffer hole is connected with the rodless cavity, and the buffer rod diameter is smaller than the diameter of the first inlet and outlet port.
  • a buffer groove is disposed on the rod end cover of the cylinder tube, and a buffer groove is disposed on an end surface of the piston rod assembly that cooperates with the first stage piston.
  • the piston rod assembly includes a piston rod and a second stage piston, the piston rod is fixedly coupled to the second stage piston, and the second stage piston is mated with the cavity of the first stage piston.
  • the piston rod assembly includes a piston rod having one end that mates with a cavity of the first stage piston.
  • the reciprocating stroke of the first stage piston is smaller than the reciprocating stroke of the piston rod assembly.
  • the rocking mechanism further includes a hydraulic system for driving two hydraulic cylinders, and the first oil passage and the oil inlet and outlet are provided on the rodless cavity end cover of the cylinder tube, and the rod cavity position of the cylinder tube
  • the second oil passage is arranged, one end of the inlet and outlet oil passage communicates with the rodless cavity of the cylinder tube, the other end of the inlet and outlet oil passage communicates with the first oil passage port, and the second oil passage port communicates with the rod cavity of the cylinder tube;
  • the second oil passage of the hydraulic cylinder is in communication with the oil tank of the hydraulic system; the first oil passages of the two hydraulic oil cylinders are respectively connected with the high pressure oil passage and the low pressure oil passage of the hydraulic system.
  • a concrete pumping apparatus including the rocking mechanism described above.
  • the swinging mechanism and the concrete pumping device of a concrete pumping device provided by the invention adopt a two-stage hydraulic oil cylinder to solve the problem of the rocking speed of the rocking mechanism and the commutation time of the concrete pumping equipment.
  • the first stage piston has a large area, a short stroke, so that the cylinder has sufficient thrust, and close to the highest movement speed in a short stroke;
  • the piston rod assembly has a small area, a long stroke, in the drive distribution valve
  • the piston rod assembly is moved as much as possible at a higher speed for most of the stroke, the rocking speed of the rocking mechanism is increased, and the commutation time of the concrete pumping equipment is shortened.
  • the swing mechanism of the two-stage hydraulic cylinder not only obtains a faster acceleration at the initial stage of the start, but also achieves a stable moving speed as soon as possible, has a higher stable moving speed in the middle stage, and has a better cushioning effect at the end.
  • the left two-stage hydraulic cylinder extends, and the right two-stage hydraulic cylinder retracts.
  • the first-stage piston of the right two-stage hydraulic cylinder retreats, due to the first
  • the larger piston area makes the oil output of the two-stage hydraulic cylinder on the right side increase, the back pressure is increased, and the extension speed of the left two-stage hydraulic cylinder at the end is reduced, thereby obtaining a better cushioning effect.
  • the right two-stage hydraulic cylinder When swinging to the left, the right two-stage hydraulic cylinder extends, the left two-stage hydraulic cylinder retracts, and the right two-stage hydraulic cylinder is in place, the first-stage piston of the left two-stage hydraulic cylinder retreats, due to the first
  • the larger piston area makes the oil output of the two-stage hydraulic cylinder on the left side increase, the back pressure is increased, and the extension speed of the right two-stage hydraulic cylinder at the final stage is reduced, thereby obtaining a better cushioning effect.
  • the technical solution has the advantages of fast reversing speed and small impact, so that the reversing time of the swinging mechanism is close to the reversing time of the main cylinder of the concrete pumping equipment, greatly improving the pumping continuity, and achieving the unpredictable technical effect. .
  • FIG. 1 is a schematic view of a pumping mechanism of a prior art concrete pumping apparatus
  • FIG. 2 is a schematic structural view of a rocking mechanism of the present invention
  • FIG. 3 is a schematic structural view of a two-stage hydraulic cylinder of the first embodiment of FIG. 1;
  • FIG. 4 is a schematic structural view of a two-stage hydraulic cylinder of the second embodiment of FIG. 1;
  • FIG. 5 is a schematic structural view of a two-stage hydraulic cylinder of the third embodiment of FIG. 1.
  • FIG. 5 is a schematic structural view of a two-stage hydraulic cylinder of the third embodiment of FIG. 1.
  • a rocking mechanism for driving a distribution valve swing of a concrete pumping device includes a swing arm 6 for driving a dispensing valve, two hydraulic cylinders for driving the swing arm 6 to swing left and right, and a left side.
  • the hydraulic cylinder 2 drives the swing arm 6 to swing to the right
  • the right hydraulic cylinder 4 drives the swing arm 6 to swing to the left.
  • the cylinder 10 of the left hydraulic cylinder 2 is ball-connected to the left support 1 mounted on the hopper of the concrete pumping device, the cylinder 10 of the right hydraulic cylinder 4 and the right support mounted on the hopper of the concrete pumping device 5 balls are connected, and the piston rods 20 of the left and right hydraulic cylinders 2, 4 are respectively balled to the left and right sides of the swing arm 6.
  • the left hydraulic cylinder 2 and the right hydraulic cylinder 4 are two-stage hydraulic cylinders.
  • the so-called two-stage hydraulic cylinder refers to the extension or retraction stroke of the piston rod 20 of the hydraulic cylinder, and has two-stage thrust under the action of constant pressure oil.
  • the two-stage hydraulic cylinder includes a cylinder 10, a first-stage piston 30, and a piston rod assembly.
  • the first-stage piston 30 is located in the inner cavity of the cylinder 10, and the first-stage piston 30 and the inner cavity of the cylinder 10.
  • the cylinder 10 is divided into a rod chamber and a rodless chamber, and the first stage piston 30 does not extend out of the cylinder 10 during the reciprocating stroke in the cylinder 10.
  • the reciprocating stroke of the first stage piston 30 in the cylinder 10 is short, and can be designed according to actual conditions.
  • the first stage piston 30 is provided with a first inlet and outlet port 300 and a second inlet and outlet port 301.
  • the first inlet and outlet port 300 communicates with the rodless cavity of the cylinder tube 10, and the second inlet and outlet port 301 has a rod with the cylinder tube 10.
  • the cavity is connected.
  • the first stage piston 30 is provided with a cavity, one end of the piston rod assembly is engaged with the cavity of the first stage piston 30, and the piston rod assembly reciprocates in the cavity of the first stage piston 30, and the piston rod assembly is at the first stage.
  • the reciprocating stroke in the cavity of the piston 30 is greater than the reciprocation of the first stage piston 30 in the cylinder 10 Exercise schedule.
  • the piston rod assembly includes a piston rod 20 and a second stage piston 21, the piston rod 20 being fixedly coupled to the second stage piston 21, and the second stage piston 21 mating with the cavity of the first stage piston 30.
  • a first oil passage 101 is disposed on the rodless chamber end cover 103 of the cylinder 10, and a second oil passage 100 is disposed at a rod chamber position of the cylinder 10, and the first oil passage 101 and the cylinder 10 are disposed.
  • the rodless chamber communicates, and the second oil passage 100 communicates with the rod cavity of the cylinder 10.
  • the second oil passages 100 of the two-stage hydraulic cylinders on the left and right sides are in communication with the fuel tank 3 of the hydraulic system; the first oil passages 101 of the two-stage hydraulic cylinders on the left and right sides are respectively used for hydraulic pressure.
  • the high pressure oil circuit of the system is connected to the low pressure oil circuit.
  • a buffer groove 105 is provided on the rod end cover 104 of the cylinder 10, and the buffer groove 105 can reduce the first stage piston 30 and the piston.
  • the rod assembly impacts the rod end cap 104.
  • the rodless cavity end cover 103 of the cylinder 10 is provided with a buffer hole 102, the buffer hole 102 and the first oil hole. It is in communication with the rodless cavity of the cylinder 10, and a buffer rod 22 is disposed at one end of the piston rod assembly.
  • the buffer rod 22 When the piston rod 20 is retracted to the end point, the buffer rod 22 is inserted into the first inlet and outlet port 300 and the buffer hole 102, and the rodless chamber hydraulic oil of the two-stage hydraulic cylinder flows out through the gap between the buffer rod 22 and the buffer hole 102.
  • the piston rod 20 continues to retract, and the gap between the buffer rod 22 and the buffer hole 102 is gradually reduced, thereby reducing the impact of the piston rod assembly in the end position of the first stage piston 30 in the end position of the retraction stroke.
  • the end surface of the piston rod assembly that cooperates with the first stage piston 30 is provided with a buffer groove 23, and the piston rod 20 is retracted into the stroke, and the buffer rod 22 is inserted into the first inlet and outlet port 300 and the buffer hole 102, when the piston rod assembly is When the end faces of the first stage pistons 30 are close, the buffer grooves 23 reduce the impact of the piston rod assembly on the first stage pistons 30.
  • the working area of the hydraulic oil is the cross-sectional area of the buffer rod 22, and after a short stroke, the hydraulic oil passes through the cooperation between the buffer rod 22 and the buffer hole 102.
  • the gap enters the rodless cavity of the cylinder 10.
  • the working area of the hydraulic oil is the cross-sectional area of the first-stage piston 30, and the first-stage propulsive force of the two-stage hydraulic cylinder is the product of the cross-sectional area of the first-stage piston 30 and the oil pressure.
  • the piston rod assembly and the first stage piston 30 move to the left under the action of the first stage propulsive force, and the piston rod 20 extends.
  • the second inlet and outlet port 301 on the first stage piston 30 is aligned with the second port port 100, and the hydraulic oil enters the first inlet and outlet of the first stage piston 30.
  • Oil port 300, the liquid in the rod chamber of the cylinder 10 The pressure oil is returned to the oil tank 3 through the second inlet and outlet port 301 and the second oil passage port 100.
  • the two-stage hydraulic cylinder is in the middle stage, the working area of the hydraulic oil is the cross-sectional area of the second-stage piston 21, and the second-stage hydraulic cylinder is the second.
  • the stage propulsive force is the product of the cross-sectional area of the second-stage piston 21 and the oil pressure, and the piston rod assembly continues to move to the left under the action of the second-stage propulsive force, and the piston rod 20 continues to extend.
  • the first stage piston 30 has a large area, a short stroke, so that the two-stage hydraulic cylinder has sufficient thrust and reaches or approaches the highest movement speed in a shorter stroke; the second stage piston 21 has a smaller area and a longer length.
  • the piston rod assembly is made to perform most of the stroke at a higher speed as much as possible, the swing speed of the swing mechanism is increased, and the commutation time of the concrete pumping equipment is shortened.
  • This technical solution combines the characteristics of fast start-up of large-bore hydraulic cylinders and fast movement of small-cylinder hydraulic cylinders.
  • the left hydraulic cylinder 2 drives the swing arm 6 to swing to the right
  • the right hydraulic cylinder 4 drives the swing arm 6 to swing to the left.
  • the two-stage hydraulic cylinder not only achieves a faster acceleration at the initial stage of starting, but also achieves a stable moving speed as soon as possible, has a higher stable moving speed in the middle stage, and has a better cushioning effect at the end stage.
  • the piston rod 20 of the left two-stage hydraulic cylinder 2 is extended, the piston rod 20 of the right two-stage hydraulic cylinder 4 is retracted by the propulsive force of the left two-stage hydraulic cylinder 2, and the left two-stage hydraulic cylinder 2
  • the first stage piston 30 of the right two-stage hydraulic cylinder starts to retreat due to the first stage piston.
  • the larger area of 30 makes the oil output of the two-stage hydraulic cylinder on the right side increase, which increases the back pressure and reduces the extension speed of the left two-stage hydraulic cylinder 2 at the end, thereby obtaining a better cushioning effect.
  • the two-stage hydraulic cylinder of the second embodiment is different from the two-stage hydraulic cylinder shown in FIG. 3 in that the piston rod assembly is composed of a piston rod 20 and a buffer rod 22, and one end of the piston rod 20 is directly connected to the first The cavity of the stage piston 30 is mated.
  • the second stage piston 21 is omitted.
  • the two-stage hydraulic cylinder can also be of other types of construction, and as long as the two-stage propulsion can be realized, it is within the scope of the present invention.
  • the two-stage hydraulic cylinder of the third embodiment does not have the two-stage hydraulic cylinder shown in FIG.
  • the same is to provide an inlet and outlet oil passage 106 on the rodless chamber end cover 103 of the cylinder tube.
  • One end of the inlet and outlet oil passage 106 communicates with the rodless chamber of the cylinder tube, and the other end of the inlet and outlet oil passage 106 communicates with the first oil passage port 101.
  • the hydraulic oil enters the rodless chamber of the cylinder through the inlet and outlet oil passage 106.
  • the area of action of the hydraulic oil is the cross-sectional area of the first stage piston 30.
  • the invention also provides a concrete pumping device, comprising the above-mentioned rocking mechanism, which has the advantages of fast reversing speed and small impact, so that the reversing time of the rocking mechanism is close to the main cylinder reversing time of the concrete pumping equipment. Greatly improve pumping continuity and achieve unpredictable technical results.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)

Abstract

一种摇摆机构，用于驱动混凝土泵送设备的分配阀摆动，包括用于驱动分配阀的摆臂（6）、用于驱动摆臂（6）左右摆动的两个液压油缸（2，4），两个液压油缸（2，4）的一端分别与摆臂（6）的左右两侧连接，液压油缸（2，4）为两级液压油缸（2，4）；还公开了一种包括上述摇摆机构的混凝土泵送设备，上述摇摆机构及具有上述摇摆机构的混凝土泵送设备，换向速度快，冲击小，使得摇摆机构的换向时间接近混凝土泵送设备的主油缸换向时间，极大的提高泵送连续性。

Description

一种摇摆机构及混凝土泵送设备
本申请要求于2013年9月10日提交中国专利局、申请号为201310409281.1、发明名称为“一种摇摆机构及混凝土泵送设备”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及工程机械领域，特别涉及一种混凝土泵送设备的摇摆机构及混凝土泵送设备。
背景技术
如图1所示：现有的混凝土泵的泵送机构包括主油缸1a、1b、水箱2、输送缸3a、3b、砼活塞4a、4b、摇摆机构、搅拌系统6、料斗7和分配阀8等零部件。摇摆机构由左、右两个摆阀油缸5a、5b和摆臂组成。在泵送状态时，在主油缸1a、1b的作用下，砼活塞4b前进，4a后退，此时摇摆机构的摆阀油缸5b处于伸出状态，5a处于后退状态，摆臂驱动分配阀8摆动，分配阀8接通混凝土输送缸3b，3b里面的混凝土在活塞4b的推动下，由分配阀8进入输送管道；而料斗7里的混凝土被不断后退的活塞4a吸入混凝土输送缸3a。当4b前进，4a后退到位以后，控制系统发出信号，使摆阀油缸5a伸出，5b后退，摆阀油缸5a、5b换向到位后，发出信号，使主油缸1a、1b换向，推动活塞4a前进，4b后退，上一轮吸进输送缸3a里的混凝土被推入分配阀8，然后进入输送管道，同时，输送缸3b吸料。如此反复动作完成混凝土料的泵送。
在混凝土泵送设备中要求换向速度快，冲击小，尽可能使左、右两个摆阀油缸5a、5b的换向时间接近甚至小于主油缸1a、1b的换向时间，这样能够极大的提高泵送连续性。现有的摆阀油缸为单级液压油缸，摆阀油缸由活塞杆组件和缸筒组成。目前摇摆机构的分配阀在启动初期，静摩擦阻力大，液压系统管道通流能力有限。液压油缸设计需要权衡利弊。如果 缸径偏大，虽然推力大，启动速度快，但是运动过程中需要更多油液，加大了管道的压力损失，使得液压油缸最终速度较慢，总换向时间过长。如果缸径偏小，虽然运动最终速度快，但是启动偏慢，尤其是负载偏大时尤为明显，影响最终的换向时间。
发明内容
有鉴于此，本发明提出一种摇摆机构及混凝土泵送设备，以解决摇摆机构中所存在的上述问题。
一方面，本发明提供了一种摇摆机构，用于驱动混凝土泵送设备的分配阀摆动，包括用于驱动分配阀的摆臂、用于驱动摆臂摆动的两个液压油缸，两个液压油缸的一端分别与摆臂的左右两侧连接，液压油缸为两级液压油缸。
进一步地，两级液压油缸包括缸筒、第一级活塞、活塞杆组件，第一级活塞与缸筒的内腔配合，第一级活塞上设置有空腔，活塞杆组件的一端与第一级活塞的空腔配合。
进一步地，第一级活塞设置有第一进出油口和第二进出油口，第一进出油口与缸筒的无杆腔相通，第二进出油口与缸筒的有杆腔相通。
进一步地，在缸筒的无杆腔端盖上设置有缓冲孔，活塞杆组件的一端设置有缓冲杆，缓冲孔与无杆腔相连通，缓冲杆直径小于第一进出油口直径。
进一步地，在缸筒的有杆腔端盖上设置有缓冲槽，活塞杆组件与第一级活塞配合的端面上设置有缓冲槽。
进一步地，活塞杆组件包括活塞杆和第二级活塞，活塞杆与第二级活塞固定连接，第二级活塞与第一级活塞的空腔配合。
进一步地，活塞杆组件包括活塞杆，活塞杆的一端与第一级活塞的空腔配合。
进一步地，第一级活塞往复运动行程小于活塞杆组件往复运动行程。
进一步地，所述摇摆机构还包括用于驱动两个液压油缸的液压系统，在缸筒的无杆腔端盖上设置有第一过油口和进出油道，在缸筒的有杆腔位 置设置有第二过油口，进出油道一端与缸筒的无杆腔相通，进出油道另一端与第一过油口相通，第二过油口与缸筒的有杆腔相通；两个液压油缸的第二过油口与液压系统的油箱相连通；两个液压油缸的第一过油口分别与液压系统的高压油路和低压油路相连通。
另一方面还提供了一种混凝土泵送设备，包括上述的摇摆机构。
本发明提供的一种混凝土泵送设备的摇摆机构及混凝土泵送设备，采用两级液压油缸，解决摇摆机构的摇摆速度和混凝土泵送设备的换向时间的问题。第一级活塞具有较大面积，较短的行程，使油缸具有足够推力，并且在较短的行程内接近最高运动速度；活塞杆组件具有较小面积，较长的行程，在满足驱动分配阀摆动推力的情况下，尽可能的使活塞杆组件以更高速度运动大部分行程，提高了摇摆机构的摇摆速度，缩短混凝土泵送设备的换向时间。
另外，采用两级液压油缸的摇摆机构，不仅在启动初期获得较快加速度，尽快达到稳定运动速度，在中期具有更高的稳定运动速度，而且在末期有更佳的缓冲效果。向右摆动时，左侧两级液压油缸伸出，右侧两级液压油缸缩回，左侧两级液压油缸快到位时，右侧的两级液压油缸的第一级活塞后退，由于第一级活塞面积较大，使得右侧的两级液压油缸的油液输出量增大，提高背压，降低了左侧两级液压油缸在末期的伸出速度，从而获得更佳的缓冲效果。向左摆动时，右侧两级液压油缸伸出，左侧两级液压油缸缩回，右侧两级液压油缸快到位时，左侧的两级液压油缸的第一级活塞后退，由于第一级活塞面积较大，使得左侧的两级液压油缸的油液输出量增大，提高背压，降低了右侧两级液压油缸在末期的伸出速度，从而获得更佳的缓冲效果。
该技术方案具备换向速度快、冲击小的优点，使得摇摆机构的换向时间接近混凝土泵送设备的主油缸换向时间，极大的提高泵送连续性，取得了预见不到的技术效果。
附图说明
图1为现有技术的混凝土泵送设备的泵送机构示意图；
图2为本发明摇摆机构的结构示意图；
图3为图1中第一实施例的两级液压油缸结构示意图；
图4为图1中第二实施例的两级液压油缸结构示意图；
图5为图1中第三实施例的两级液压油缸结构示意图。
具体实施方式
需要说明的是，在不冲突的情况下，本发明中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。
下面结合图2至图4，对本发明的优选实施例作进一步详细说明，本优选实施例的摇摆机构为例：
如图2所示，一种摇摆机构，用于驱动混凝土泵送设备的分配阀摆动，包括用于驱动分配阀的摆臂6、用于驱动摆臂6左右摆动的两个液压油缸，左侧液压油缸2驱动摆臂6向右摆动，右侧液压油缸4驱动摆臂6向左摆动。左侧液压油缸2的缸筒10与安装在混凝土泵送设备的料斗上的左支座1球接，右侧液压油缸4的缸筒10与安装在混凝土泵送设备的料斗上的右支座5球接，左右侧液压油缸2、4的活塞杆20分别与摆臂6的左右两侧球接。左侧液压油缸2和右侧液压油缸4均为两级液压油缸。所谓两级液压油缸是指液压油缸的活塞杆20伸出或缩回行程中，在恒定压力油作用下，具有两级推力。
如图3所示，两级液压油缸包括缸筒10、第一级活塞30、活塞杆组件，第一级活塞30位于缸筒10内腔内，第一级活塞30与缸筒10的内腔配合，将缸筒10分隔成有杆腔和无杆腔，第一级活塞30在缸筒10内往复运动行程中，不伸出缸筒10。第一级活塞30在缸筒10内往复运动行程较短，可以根据实际情况设计。第一级活塞30设置有第一进出油口300和第二进出油口301，第一进出油口300与缸筒10的无杆腔相通，第二进出油口301与缸筒10的有杆腔相通。
第一级活塞30上设置有空腔，活塞杆组件的一端与第一级活塞30的空腔配合，活塞杆组件在第一级活塞30的空腔中往复运动，活塞杆组件在第一级活塞30的空腔中往复运动行程大于第一级活塞30在缸筒10内往复 运动行程。活塞杆组件包括活塞杆20和第二级活塞21，活塞杆20与第二级活塞21固定连接，第二级活塞21与第一级活塞30的空腔配合。在缸筒10的无杆腔端盖103上设置有第一过油口101，在缸筒10的有杆腔位置设置有第二过油口100，第一过油口101与缸筒10的无杆腔相通，第二过油口100与缸筒10的有杆腔相通。如图2所示，左右两侧的两级液压油缸的第二过油口100与液压系统的油箱3相连通；左右两侧的两级液压油缸的第一过油口101分别用于与液压系统的高压油路和低压油路相连通。
为减少第一级活塞30在缸筒10内往复运动行程终点位置的冲击，在缸筒10的有杆腔端盖104上设置有缓冲槽105，缓冲槽105可以减少第一级活塞30和活塞杆组件对有杆腔端盖104的冲击。为了减少活塞杆组件在第一级活塞30的内腔中往复运动行程终点位置的冲击，在缸筒10的无杆腔端盖103上设置有缓冲孔102，缓冲孔102与第一过油孔和缸筒10的无杆腔相通，活塞杆组件的一端设置有的缓冲杆22。活塞杆20缩回快到终点时，缓冲杆22插入第一进出油口300和缓冲孔102中，两级液压油缸的无杆腔液压油经过缓冲杆22与缓冲孔102之间的间隙流出，活塞杆20继续缩回，缓冲杆22与缓冲孔102之间的间隙逐渐减少，从而减少活塞杆组件在第一级活塞30的内腔中缩回行程终点位置的冲击。另外，活塞杆组件与第一级活塞30配合的端面上设置有缓冲槽23，活塞杆20缩回行程中，缓冲杆22插入第一进出油口300和缓冲孔102中，当活塞杆组件与第一级活塞30的端面靠近时，缓冲槽23减少了活塞杆组件对第一级活塞30的冲击。
两级液压油缸工作过程如下：
当第一过油口101进入液压油，在启动初期，首先液压油的作用面积为缓冲杆22的横截面积，在很短行程之后，液压油通过缓冲杆22与缓冲孔102之间的配合间隙进入缸筒10的无杆腔内。此时，液压油的作用面积为第一级活塞30的横截面积，两级液压油缸的第一级推进力为第一级活塞30的横截面积与油压之乘积。活塞杆组件和第一级活塞30在第一级推进力的作用下，向左移动，活塞杆20伸出。当第一级活塞30被有杆腔端盖104阻挡时，第一级活塞30上的第二进出油口301与第二过油口100对齐，液压油进入第一级活塞30的第一进出油口300，缸筒10的有杆腔内的液 压油通过第二进出油口301和第二过油口100回油箱3，两级液压油缸处于中期，液压油的作用面积为第二级活塞21的横截面积，两级液压油缸的第二级推进力为第二级活塞21的横截面积与油压之乘积，活塞杆组件在第二级推进力的作用下，向左继续移动，活塞杆20继续伸出。第一级活塞30具有较大面积，较短的行程，使两级液压油缸具有足够推力，并且在较短的行程内达到或接近最高运动速度；第二级活塞21具有较小面积，较长的行程，在满足驱动分配阀摆动推进力的情况下，尽可能的使活塞杆组件以更高速度完成大部分行程，提高了摇摆机构的摇摆速度，缩短混凝土泵送设备的换向时间。此技术方案结合了大缸径液压油缸启动快与小缸径液压油缸运动速度快的特点。
另外，如图2所示，采用左侧液压油缸2驱动摆臂6向右摆动，右侧液压油缸4驱动摆臂6向左摆动。这种组合结构，两级液压油缸不仅在启动初期获得较快加速度，尽快达到稳定运动速度，在中期具有更高的稳定运动速度，而且在末期有更佳的缓冲效果。因为，左侧两级液压油缸2的活塞杆20伸出，右侧两级液压油缸4的活塞杆20在左侧两级液压油缸2的推进力作用下缩回，左侧两级液压油缸2快到位时，也就是说活塞杆20继续伸出快到终点时，左侧两级液压油缸2处于末期时，右侧的两级液压油缸的第一级活塞30开始后退，由于第一级活塞30面积较大，使得右侧的两级液压油缸的油液输出量增大，增大了背压，降低了左侧两级液压油缸2在末期伸出速度，从而获得更佳的缓冲效果。反之，右侧两级液压油缸4快到位时，也就是说活塞杆20继续伸出快到终点时，右侧两级液压油缸4处于末期时，左侧的两级液压油缸的第一级活塞30开始后退，由于第一级活塞30面积较大，使得左侧的两级液压油缸的油液输出量增大，提高背压，降低了右侧两级液压油缸4在末期伸出速度，从而获得更佳的缓冲效果。
如图4所示，第二实施例的两级液压油缸与图3所示的两级液压油缸不同在于，活塞杆组件由活塞杆20和缓冲杆22组成，活塞杆20的一端直接与第一级活塞30的空腔配合。省去了第二级活塞21。两级液压油缸还可以其它类型结构，只要能实现两级推进力，都在本发明保护范围之内。
如图5所示，第三实施例的两级液压油缸与图3所示两级液压油缸不 同在于，在缸筒的无杆腔端盖103上设置有进出油道106，进出油道106一端与缸筒的无杆腔相通，进出油道106另一端与第一过油口101相通。当第一过油口101进入液压油，在启动初期，液压油通过进出油道106进入缸筒的无杆腔内。液压油的作用面积为第一级活塞30的横截面积。该技术方案与图3所示的第一实施方案启动更快，在很短的行程内达到或接近最高运动速度。另外，为了避免影响缸筒10无杆腔的回油缓冲效果，可以在进出油道106上设置单向阀。
本发明还提供了一种混凝土泵送设备，包括上述的摇摆机构，该摇摆机构具有换向速度快、冲击小的优点，使得摇摆机构的换向时间接近混凝土泵送设备的主油缸换向时间，极大的提高泵送连续性，取得了预见不到的技术效果。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。

Claims (10)

  1. 一种摇摆机构，用于驱动混凝土泵送设备的分配阀摆动，包括用于驱动分配阀的摆臂(6)、用于驱动摆臂(6)左右摆动的两个液压油缸(2，4)，两个液压油缸(2，4)的一端分别与摆臂(6)的左右两侧连接，其特征在于，液压油缸为两级液压油缸。
  2. 根据权利要求1所述的摇摆机构，其特征在于，两级液压油缸包括缸筒(10)、第一级活塞(30)、活塞杆组件，第一级活塞(30)与缸筒(10)的内腔配合，第一级活塞(30)上设置有空腔，活塞杆组件的一端与第一级活塞(30)的空腔配合。
  3. 根据权利要求2所述的摇摆机构，其特征在于，第一级活塞(30)设置有第一进出油口(300)和第二进出油口(301)，第一进出油口(300)与缸筒(10)的无杆腔相通，第二进出油口(301)与缸筒(10)的有杆腔相通。
  4. 根据权利要求3所述的摇摆机构，其特征在于，在缸筒(10)的无杆腔端盖(103)上设置有缓冲孔(102)，活塞杆组件的一端设置有缓冲杆(22)，缓冲孔(102)与无杆腔相连通，缓冲杆(22)直径小于第一进出油口(300)直径。
  5. 根据权利要求4所述的摇摆机构，其特征在于，在缸筒(10)的有杆腔端盖(104)上设置有缓冲槽(105)，活塞杆组件与第一级活塞(30)配合的端面上设置有缓冲槽(23)。
  6. 根据权利要求2至5任意一项所述的摇摆机构，其特征在于，活塞杆组件包括活塞杆(20)和第二级活塞(21)，活塞杆(20)与第二级活塞(21)固定连接，第二级活塞(21)与第一级活塞(30)的空腔配合。
  7. 根据权利要求2至5任意一项所述的摇摆机构，其特征在于，活塞杆组件包括活塞杆(20)，活塞杆(20)的一端与第一级活塞(30)的空腔配合。
  8. 根据权利要求2至5任意一项所述的摇摆机构，其特征在于，第一级活塞(30)往复运动行程小于活塞杆组件往复运动行程。
  9. 根据权利要求8所述的摇摆机构，其特征在于，还包括用于驱动两 个液压油缸(2，4)的液压系统，在缸筒(10)的无杆腔端盖(103)上设置有第一过油口(101)和进出油道(106)，在缸筒(10)的有杆腔位置设置有第二过油口(100)，进出油道(106)一端与缸筒(10)的无杆腔相通，进出油道(106)另一端与第一过油口(101)相通，第二过油口(100)与缸筒(10)的有杆腔相通；两个液压油缸(2，4)的第二过油口(100)与液压系统的油箱(3)相连通；两个液压油缸(2，4)的第一过油口(101)分别与液压系统的高压油路和低压油路相连通。
  10. 一种混凝土泵送设备，其特征在于，包括如权利要求1至9任意一项所述的摇摆机构。
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