WO2022205538A1 - 一种大冲程游梁式抽油机 - Google Patents

一种大冲程游梁式抽油机 Download PDF

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Publication number
WO2022205538A1
WO2022205538A1 PCT/CN2021/088826 CN2021088826W WO2022205538A1 WO 2022205538 A1 WO2022205538 A1 WO 2022205538A1 CN 2021088826 W CN2021088826 W CN 2021088826W WO 2022205538 A1 WO2022205538 A1 WO 2022205538A1
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Prior art keywords
bracket
pumping unit
base
stroke
connecting rod
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PCT/CN2021/088826
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English (en)
French (fr)
Inventor
张聪
张健
宋洋洋
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德瑞石油装备（青岛）有限公司
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Publication of WO2022205538A1 publication Critical patent/WO2022205538A1/zh

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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B43/00—Methods or apparatus for obtaining oil, gas, water, soluble or meltable materials or a slurry of minerals from wells
    • E21B43/12—Methods or apparatus for controlling the flow of the obtained fluid to or in wells
    • E21B43/121—Lifting well fluids
    • E21B43/126—Adaptations of down-hole pump systems powered by drives outside the borehole, e.g. by a rotary or oscillating drive
    • E21B43/127—Adaptations of walking-beam pump systems

Definitions

  • the invention relates to the technical field of pumping units, in particular to a large-stroke beam pumping unit.
  • the world's oil production equipment is mainly divided into beam pumping units and tower pumping units.
  • the beam pumping units are mainly used for small and medium strokes (240in. and below), and the tower type is used for long strokes (above 240in.). ). Therefore, there is no application of the beam type in the long-stroke pumping unit, and the tower type is mainly used.
  • the reliability of the beam pumping unit is 50% higher than that of the tower type, and the manufacturing cost of the beam pumping unit is 30% to % lower than that of the tower type. of fifty.
  • the main reason is: as shown in Figure 2, the stroke size of the beam pumping unit is mainly related to the A value and the H value. The larger the stroke, the larger the A value and the H value. Under the same wellhead load, all structural parts The more unsatisfactory the force is (the force is greater than the strength of the material, or the stress concentration occurs, which causes the structural parts to crack), if the force state is improved by changing other values, it will cause poor motion characteristics (the force transmission ratio is very low, the efficiency will be reduced. very low).
  • the purpose of the present invention is to provide a large stroke beam pumping unit to solve the technical problems in the prior art.
  • the present invention specifically provides the following technical solutions:
  • a large-stroke beam pumping unit comprising a base and a drive mechanism fixedly installed at one end of the base, a travel beam is provided at the other end of the base through a bracket mechanism, and a donkey head is installed at the front end of the travel beam , and the rear end of the beam is connected with the drive mechanism through a connecting rod, a middle seat is slidably installed on the beam, and the connection between the middle seat and the bracket mechanism is connected by a stress arc device, and the bracket
  • the mechanism includes a front bracket and a rear bracket whose top ends are connected by a hinge, and the other ends of the front bracket and the rear bracket are both slidably installed on both sides of the base.
  • A is the distance from the donkey head to the middle seat
  • C is the distance from the middle seat to the rear end of the beam
  • I is the distance from the center of rotation of the drive mechanism to the projection of the middle seat on the base
  • P is the length of the connecting rod
  • H is the distance from the middle seat to the base
  • G is the distance from the rotation center of the drive mechanism to the base
  • R is the turning radius of the drive mechanism
  • the beam pumping unit adjusts the distance, length and turning radius through a trial-and-error method, and outputs the dynamic characteristic curve of the beam pumping unit through dynamic simulation calculation, and according to the dynamic characteristics
  • the feedback of the curve adjusts the distance, length and turning radius again until the dynamic characteristic curve is optimized.
  • the connecting rod is connected with the crank of the driving mechanism to form a crank connecting rod structure, and the traveling beam and the bracket mechanism are adjusted to form a large-stroke traveling beam structure by adjusting the distance, length and turning radius.
  • the crank connecting rod structure, the stress arc device and the bracket mechanism cooperate with the large-stroke beam structure.
  • the stress arc device extends in an arc shape to both ends along the long axis direction of the beam.
  • the stress arc device includes a bearing seat connected with the bracket mechanism and a patch body connected with the middle seat;
  • the cross section of the bearing seat is trapezoidal, and the bearing seat and the patch body are connected by an arc-shaped extension body, and the bearing seat, the arc-shaped extension body and the patch body are an integrated structure.
  • extension columns are provided on both sides of the hinge piece, the front bracket and the rear bracket are respectively sleeved on the extension columns on both sides of the hinge piece, and the front bracket and the rear bracket are in the same position.
  • the base is movably installed along the long axis direction of the beam to adjust the included angle between the front bracket and the rear bracket.
  • the vertical line of the middle seat is set as the center line, the angle between the front bracket and the center line is 0-10°, and the angle between the rear bracket and the center line is 0-10°. Angle is 0-16°
  • slide rails are fixedly installed on the front support and the rear support along the axial direction, and each of the slide rails is provided with a free base that moves freely along the slide rail, and the two The free bases are connected by a gas spring group, and the gas spring group is composed of a plurality of self-locking gas springs connected in sequence, and each adjacent self-locking gas spring and self-locking gas spring are connected with The free bases are connected by hinges.
  • a self-balancing counterweight box is movably installed on the travel beam by sliding, and a plurality of isolation baffles arranged in a return shape are arranged inside the self-balancing counterweight box, and corresponding to the self-balancing counterweight box.
  • the inlet of the isolation baffle is provided with a liquid injection hole;
  • the liquid injection hole is connected with a liquid distribution box arranged on the base through a liquid injection conduit, and the liquid distribution box is controlled by the control system according to the difference between the angle between the front bracket and the rear bracket and the center line. To supply the weight liquid to balance the weight of the beam.
  • FIG. 1 is a schematic structural diagram of an embodiment of the present invention
  • Fig. 2 is the structural principle diagram of the beam pumping unit of the present invention.
  • FIG. 3 is a schematic structural diagram of a stress arc device in the present invention.
  • FIG. 4 is a schematic diagram of the included angle between the bracket mechanism and the center line in the present invention.
  • the present invention provides a large-stroke beam pumping unit, comprising a base 1 and a drive mechanism 2 fixedly installed at one end of the base 1 , and a bracket mechanism 3 is provided at the other end of the base 1
  • a traveling beam 4 to form a traveling beam structure
  • a donkey head 5 is installed at the front end of the traveling beam 4
  • a crank connecting rod structure is formed by connecting the rear end of the traveling beam 4 with the driving mechanism 2 through a connecting rod 6 .
  • a beam-type structure is formed by arranging a beam 4 at the other end of the base 1 through a bracket mechanism 3 , and a link 6 is connected to the drive mechanism 2 at the rear end of the beam 4 .
  • the connection forms a crank connecting rod structure, that is, the principle of the crank connecting rod mechanism (four connecting rod) is applied to the beam pumping unit with a large stroke (240in., that is, more than 6.1m) for the first time.
  • the driving mechanism includes an electric motor, the electric motor is connected with the reducer through a belt, and the reducer is connected with a connecting rod 6 through a crankshaft.
  • the beam pumping unit is mainly used for medium and small strokes (240in. and below), and the tower type is used for long strokes (above 240in.). Therefore, there is no application of the beam type in the long-stroke pumping unit, and the tower type is mainly used.
  • A is the distance from the donkey head 5 to the middle seat 7;
  • I is the distance from the center of rotation of the drive mechanism 2 to the projection of the middle seat 7 on the base 1;
  • P is the length of the connecting rod 6
  • H is the distance between the middle seat 7 and the base 1;
  • G is the distance from the rotation center of the drive mechanism 2 to the base 1;
  • R is the turning radius of the drive mechanism 2 .
  • the stroke size of the beam pumping unit is mainly related to the A value and the H value. Material strength, or stress concentration occurs, resulting in cracking of structural parts), if the stress state is improved by changing other values, it will cause poor motion characteristics (low force transmission ratio and low efficiency). Therefore, the best match of each value in the figure can not only make the force transmission relatively high and stable, but also meet the sports performance (complete a large stroke), and also the structural strength can be satisfied and economical.
  • these requirements are contradictory, so the development of beam pumping units in the direction of long stroke has been limited.
  • the travel beam 4 is connected with the crank of the drive mechanism 2 through the connecting rod 6 to form a crank connecting rod structure, and the travel beam 4 and the bracket mechanism 3 are formed by adjusting the distance, length and turning radius to form a large
  • the travel beam structure of stroke, the crank connecting rod structure, the stress arc device 8 and the bracket mechanism 3 cooperate with the travel beam structure of large stroke.
  • the crank connecting rod mechanism is applied to the large-stroke beam pumping unit to improve its reliability and reduce the manufacturing cost. Specifically: the distance and length of the beam pumping unit are adjusted by trial and error. and turning radius, and output the dynamic characteristic curve of the beam pumping unit through dynamic simulation calculation, and adjust the distance, length and turning radius again according to the feedback of the dynamic characteristic curve until the dynamic characteristic curve reaches the maximum good.
  • each dimension value is optimized as follows:
  • a middle seat 7 is slidably installed on the beam 4 , and the connection between the middle seat 7 and the bracket mechanism 3 is connected by a stress arc device 8 , and the bracket mechanism 3.
  • It includes a front bracket 301 and a rear bracket 302 whose top ends are connected by hinges, and the other ends of the front bracket 301 and the rear bracket 302 are both slidably installed on both sides of the base 1 .
  • the stress arc device 8 extends in an arc shape to both ends along the long axis direction of the beam 4 .
  • the stress arc device 8 includes a bearing seat 801 connected with the bracket mechanism 3 and a patch body 802 connected with the middle seat 7;
  • the cross section of the bearing seat 801 is trapezoidal, and the bearing seat 801 and the patch body 802 are connected by an arc-shaped extension body 803, the bearing seat 801, the arc-shaped extension body 803 and the patch body 802 is an integrated structure.
  • the stress arc device 8 is used to connect the middle seat 7 and the bracket mechanism 3, so as to reduce the stress of the middle seat 7 and improve the fatigue strength.
  • the main reason is that the large-stroke beam pumping machine causes the A value to be very large, so the force state of the beam is poor, stress concentration occurs, and the life of the structure is greatly reduced.
  • the present invention adopts the stress arc structure to release the stress concentration. Reduced to 98Mpa.
  • extension columns 9 are provided on both sides of the hinge
  • the front bracket 301 and the rear bracket 302 are respectively sleeved on the extension columns 9 on both sides of the hinge
  • the front bracket 301 and the rear bracket 302 are respectively sleeved on the extension columns 9 on both sides of the hinge.
  • the rear bracket 302 is movably installed on the base 1 along the long axis direction of the beam 4 to adjust the included angle between the front bracket 301 and the rear bracket 302 .
  • Feature 1 On the front bracket 301 and the rear bracket 302, oppositely arranged slide rails are fixedly installed along the axial direction, and each of the slide rails is provided with a free base that freely moves along the slide rails 303, the two free bases are connected by a gas spring group 304.
  • the gas spring group 304 By arranging the gas spring group 304, it is connected with the front bracket 301 and the rear bracket 302 to form a triangular shape, so as to improve its stability, and the gas spring group 304 in the present invention can follow the movement of the front bracket 301 and the rear bracket 302.
  • follow-up changes occur within the allowable range, so that it has stability and flexibility at the same time.
  • the free base connected with the gas spring group 304 has a relative movable ability.
  • the gas spring group 304 is composed of a plurality of self-locking gas springs connected end to end in sequence, and each adjacent self-locking gas spring and a self-locking gas spring are Both the spring and the free base 303 are connected by hinges.
  • the gas spring in the present invention has the ability of automatic locking, that is, it can be stopped at any position in the stroke by means of the release mechanism, and has a larger locking force after stopping, so as to achieve the purpose of locking.
  • a self-balancing counterweight box 10 is movably installed on the beam 4 in a sliding manner, and a plurality of isolation baffles arranged in a return shape are arranged inside the self-balancing counterweight box 10, A liquid injection hole is provided on the heavy box 10 corresponding to the inlet of the isolation baffle.
  • the liquid injection hole is connected with the liquid distribution box 12 arranged on the base 1 through the liquid injection conduit 11.
  • the liquid distribution tank 12 is based on the center line of the front bracket 301 and the rear bracket 302 through the control system. The difference between the included angles is used to supply the weight liquid to balance the weight of the beam 4.
  • the self-balancing counterweight box 10 when the balance of the beam changes due to the adjustment of the front bracket 301 and the rear bracket 302, on the one hand, the self-balancing counterweight box 10 is moved to realize the counterweight, and the self-balancing counterweight box is adjusted according to the needs through the control system.
  • the self-weight of 10 thus realizes the counterweight to the beam.
  • the present invention balances the load of the pumping unit through the two functions of the self-balancing counterweight box 10, and can effectively buffer the sudden change of the force of each component when the pumping unit is started and during the operation, so as to automatically adapt to the oil well.
  • the load variation curve balances the influence of the angle adjustment between the front bracket 301 and the rear bracket 302 on the oil pumping unit, so that it can adapt to the aforementioned improvements.
  • the stress concentration is reduced mainly by setting the stress arc device 8 and optimizing the asynchronous sliding of the front bracket 301 and the rear bracket 302 to adjust the angle between them and the center line of the connecting line between the hinge and the projection point, thereby reducing the stress concentration.
  • crank connecting rod mechanism for the application of crank connecting rod mechanism to large stroke beam pumping units.
  • the present invention reduces stress concentration by setting the stress arc device and optimizing the asynchronous sliding of the bracket mechanism to adjust the angle between the bracket and the connecting line between the hinge and the projection point, so as to apply the crank connecting rod mechanism to the large-stroke beam-type extractor. Oil machine service.

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Abstract

一种大冲程游梁式抽油机，包括底座（1）和固定安装在底座（1）一端的驱动机构（2），在底座（1）另一端通过支架机构（3）设置有游梁（4）形成游梁式结构，在游梁（4）的前端安装有驴头（5），且在游梁（4）的后端通过连杆（6）与驱动机构（2）连接形成曲柄连杆结构，游梁（4）上滑动安装有中座（7），中座（7）和支架机构（3）的连接处通过应力弧装置（8）连接，支架机构（3）包括顶端通过铰接件连接的前支架（301）和后支架（302），前支架（301）和后支架（302）的另一端均滑动安装在底座（1）两侧。

Description

一种大冲程游梁式抽油机 技术领域
本发明涉及抽油机技术领域，具体涉及一种大冲程游梁式抽油机。
背景技术
石油作为世界主要能源之一，随着汽车等制造工业的发展，对石油制品的需求量越来越大，因此对采油设备的需求也越来越高。但世界各地地质差异万千，因此对采油设备也提出了不同的性能要求。
目前世界采油设备主要分为游梁式抽油机和塔架式抽油机，游梁式抽油机主要应用于中小冲程(240in.及以下)，塔架式应用于长冲程(240in.以上)。因此，长冲程的抽油机中没有游梁式的应用，主要都是采用塔架式。
但是在实际应用中发现，游梁式抽油机的可靠性比塔架式高百分之五十，且游梁式抽油机的制造成本比塔架式低百分之三十到百分之五十。其主要在于：如图2所示，游梁式抽油机冲程大小主要与A值和H值有关，冲程越大，A值和H值也越大，同样井口载荷的情况下，所有结构件受力就越不理想(受力大于材料强度，或出现应力集中，而造成结构件开裂)，如若通过改变其他值改善受力状态，会造成运动特性很差(传力比很低，效率就很低)。因此图中的各个值的最佳匹配，既能使的传力比较高且平稳，又能满足运动性能(完成大冲程)，还要结构强度能满足且经济，然而由于曲柄连杆机构的特点，这些要求是相互矛盾的，因此一直限制了游梁式抽油机在长冲程方向的发展。
发明内容
本发明的目的在于提供一种大冲程游梁式抽油机，以解决现有技术中的技术问题。
为解决上述技术问题，本发明具体提供下述技术方案：
一种大冲程游梁式抽油机，包括底座和固定安装在所述底座一端的驱动机构，在所述底座另一端通过支架机构设置有游梁，在所述游梁的前端安装 有驴头，且在所述游梁的后端通过连杆与所述驱动机构连接，所述游梁上滑动安装有中座，所述中座和支架机构的连接处通过应力弧装置连接，所述支架机构包括顶端通过铰接件连接的前支架和后支架，所述前支架和所述后支架的另一端均滑动安装在所述底座两侧。
进一步地，设定：
A为所述驴头至所述中座的距离；
C为所述中座至所述游梁后端的距离；
I为所述驱动机构转动中心至所述中座在所述底座上投影之间的距离；
P为所述连杆的长度；
H为所述中座至所述底座之间的距离；
G为所述驱动机构转动中心至所述底座之间的距离；
R为所述驱动机构的转动半径；
所述A＝5791～7395毫米，所述C＝3050～3611毫米，所述I＝3050～3569毫米，所述P＝5759～7386毫米，所述H＝8636～10838毫米，所述G＝2819～3643毫米，所述R＝1524～2047毫米。
进一步地，所述游梁式抽油机通过试凑法调整所述距离、长度和转动半径并通过动力学仿真计算输出所述游梁式抽油机的动态特征曲线，并依据所述动态特征曲线的反馈再次调整所述距离、长度和转动半径直至所述动态特征曲线达到最佳。
进一步地，所述游梁通过连杆与所述驱动机构的曲柄连接形成曲柄连杆结构，所述游梁和支架机构通过调整所述距离、长度和转动半径形成大冲程的游梁结构，所述曲柄连杆结构和所述应力弧装置以及支架机构配合大冲程的游梁结构。
进一步地，所述应力弧装置沿着所述游梁的长轴方向向两端呈弧形延伸。
进一步地，所述应力弧装置包括与支架机构连接的轴承座和与所述中座连接的贴片体；
所述轴承座的剖面呈梯形，且所述轴承座和所述贴片体之间通过弧形延 展体连接，所述轴承座、弧形延展体和所述贴片体为一体化结构。
进一步地，所述铰接件两侧均设置有延伸柱，所述前支架和所述后支架分别套设在所述铰接件两侧的延伸柱上，所述前支架和所述后支架在所述底座上沿着游梁的长轴方向活动安装以调整所述前支架和所述后支架之间的夹角。
进一步地，设定所述中座的铅垂线为中心线，所述前支架和所述中心线之间的夹角为0-10°，所述后支架和所述中心线之间的夹角为0-16°
进一步地，在所述前支架和后支架上均沿着轴向均固定安装有相对设置的滑轨，每个所述滑轨上均设置有沿着所述滑轨自由活动的游离底座，两个所述游离底座之间通过气弹簧组连接，所述气弹簧组通过多个首尾顺次连接的自锁型气弹簧组成，且每个相邻自锁型气弹簧以及自锁型气弹簧与所述游离底座之间均通过铰接连接。
进一步地，所述游梁上通过滑动的方式活动安装有自平衡配重箱，所述自平衡配重箱内部设置有多个呈回形设置的隔离挡板，并且在所述自平衡配重箱上对应所述隔离挡板的入口处设置有注液孔；
所述注液孔通过注液输导管连接有设置在所述底座上的配液箱，所述配液箱通过控制系统依据所述前支架和所述后支架与中心线之间夹角的区别来供给配重液以平衡游梁的配重。
附图说明
为了更清楚地说明本发明的实施方式或现有技术中的技术方案，下面将对实施方式或现有技术描述中所需要使用的附图作简单地介绍。显而易见地，下面描述中的附图仅仅是示例性的，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据提供的附图引伸获得其它的实施附图。
图1为本发明实施例的结构示意图；
图2为本发明游梁式抽油机结构原理图；
图3为本发明中应力弧装置的结构示意图；
图4为本发明中支架机构和中心线夹角示意图。
图中的标号分别表示如下：
1-底座；2-驱动机构；3-支架机构；4-游梁；5-驴头；6-连杆；7-中座；8-应力弧装置；9-延伸柱；10-自平衡配重箱；11-注液输导管；12-配液箱；
301-前支架；302-后支架；303-游离底座；304-气弹簧组；
801-轴承座；802-贴片体；803-弧形延展体。
本发明的较佳实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本发明一部分实施例，而不是全部的实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本发明保护的范围。
如图1所示，本发明提供了一种大冲程游梁式抽油机，包括底座1和固定安装在所述底座1一端的驱动机构2，在所述底座1另一端通过支架机构3设置有游梁4形成游梁式结构，在所述游梁4的前端安装有驴头5，且在所述游梁4的后端通过连杆6与所述驱动机构2连接形成曲柄连杆结构。
在本实施方式中，通过在所述底座1另一端通过支架机构3设置有游梁4形成游梁式结构，并通过在所述游梁4的后端通过连杆6与所述驱动机构2连接形成曲柄连杆结构，即首次将曲柄连杆机构(四连杆)的原理在大冲程(240in.，即6.1m以上)游梁式抽油机上应用。
其中，驱动机构包括电动机，电动机通过皮带与减速器连接，减速器通过曲柄轴连接有连杆6。
在现有技术中，游梁式抽油机主要应用于中小冲程(240in.及以下)，塔架式应用于长冲程(240in.以上)。因此，长冲程的抽油机中没有游梁式的应用，主要都是采用塔架式。
其原因主要是考虑传力比和结构件的受力强度问题。为了进一步说明上 述问题，如图2所示，首先设定：
A为所述驴头5至所述中座7的距离；
C为所述中座7至所述游梁4后端的距离；
I为所述驱动机构2转动中心至所述中座7在所述底座1上投影之间的距离；
P为所述连杆6的长度；
H为所述中座7至所述底座1之间的距离；
G为所述驱动机构2转动中心至所述底座1之间的距离；
R为所述驱动机构2的转动半径。
游梁式抽油机冲程大小主要与A值和H值有关，冲程越大，A值和H值也越大，同样井口载荷的情况下，所有结构件受力就越不理想(受力大于材料强度，或出现应力集中，而造成结构件开裂)，如若通过改变其他值改善受力状态，会造成运动特性很差(传力比很低，效率就很低)。因此图中的各个值的最佳匹配，既能使的传力比较高且平稳，又能满足运动性能(完成大冲程)，还要结构强度能满足且经济，然而由于曲柄连杆机构的特点，这些要求是相互矛盾的，因此一直限制了游梁式抽油机在长冲程方向的发展。
在本发明中，所述游梁4通过连杆6与所述驱动机构2的曲柄连接形成曲柄连杆结构，所述游梁4和支架机构3通过调整所述距离、长度和转动半径形成大冲程的游梁结构，所述曲柄连杆结构和所述应力弧装置8以及支架机构3配合大冲程的游梁结构。将曲柄连杆机构应用于大冲程的游梁式抽油机中，以提高其可靠性，并降低制造成本，具体地：所述游梁式抽油机通过试凑法调整所述距离、长度和转动半径并通过动力学仿真计算输出所述游梁式抽油机的动态特征曲线，并依据所述动态特征曲线的反馈再次调整所述距离、长度和转动半径直至所述动态特征曲线达到最佳。
在本实施方式中，各个尺寸值优化如下：
A(mm) C(mm) I(mm) P(mm) H(mm) G(mm) R(mm)
5791～7395 3050～3611 3050～3569 5759～7386 8636～10838 2819～3643 1524～2047
在本发明中，仅仅依据参数的优化并不能够实现将曲柄连杆机构应用于 大冲程的游梁式抽油机的目的。因此，进一步地，如图1和图3所示，所述游梁4上滑动安装有中座7，所述中座7和支架机构3的连接处通过应力弧装置8连接，所述支架机构3包括顶端通过铰接件连接的前支架301和后支架302，所述前支架301和所述后支架302的另一端均滑动安装在所述底座1两侧。
第一方面，所述应力弧装置8沿着所述游梁4的长轴方向向两端呈弧形延伸。具体地，所述应力弧装置8包括与支架机构3连接的轴承座801和与所述中座7连接的贴片体802；
所述轴承座801的剖面呈梯形，且所述轴承座801和所述贴片体802之间通过弧形延展体803连接，所述轴承座801、弧形延展体803和所述贴片体802为一体化结构。
采用应力弧装置8连接中座7和支架机构3，降低中座7的受力，提高疲劳强度。主要原因在于，大冲程游梁抽油机会造成A值很大，因此游梁受力状态差，出现应力集中，大大降低结构寿命，本发明采用应力弧结构，释放应力集中，根据实验证明：应力由310Mpa降低为98Mpa。
第二方面，所述铰接件两侧均设置有延伸柱9，所述前支架301和所述后支架302分别套设在所述铰接件两侧的延伸柱9上，所述前支架301和所述后支架302在所述底座1上沿着游梁4的长轴方向活动安装以调整所述前支架301和所述后支架302之间的夹角。设定所述中座7的铅垂线为中心线，优化支架前后腿角度，改善支架受力状态，提高可靠性，通过试凑法不断调整前后腿角度进行动力学和有限元分析，直到满足强度要求，其中，如图4所示，前支架301和中心线之间的夹角为10°，而后支架302和中心之间的夹角为16°。
在本实施方式中，由于前支架301和后支架302处于非对称设置的状态，因此，在无外力作用的前提下可能会存在非平衡的问题，因此，在本发明中为了进一步提高整个游梁式抽油机的稳定性和可靠性，将通过以下两个特征对此做进一步的改进：
特征1：在所述前支架301和后支架302上均沿着轴向均固定安装有相对设置的滑轨，每个所述滑轨上均设置有沿着所述滑轨自由活动的游离底座303， 两个所述游离底座之间通过气弹簧组304连接。通过设置气弹簧组304，使其与前支架301和后支架302联系起来形成三角形状，从而提高其稳定性，并且本发明中的气弹簧组304能够跟随前支架301和后支架302的移动而在允许的范围内发生追随性的变化，从而使其在具备稳定性的同时又具有灵活的适变性。
其中，通过在前支架301和后支架302上均设置滑轨，使得与气弹簧组304连接的游离底座具有相对的可移动能力。
进一步地，为了使得气弹簧组304具有更好的稳定能力，气弹簧组304通过多个首尾顺次连接的自锁型气弹簧组成，且每个相邻自锁型气弹簧以及自锁型气弹簧与所述游离底座303之间均通过铰接连接。在本发明中的气弹簧具有自动锁定的能力，即借助释放机构可以在行程中的任意位置停止，并且停止以后具有较大的锁紧力，从而达到锁止的目的。
特征2：所述游梁4上通过滑动的方式活动安装有自平衡配重箱10，所述自平衡配重箱10内部设置有多个呈回形设置的隔离挡板，并且在所述自平衡配重箱10上对应所述隔离挡板的入口处设置有注液孔。
所述注液孔通过注液输导管11连接有设置在所述底座1上的配液箱12，所述配液箱12通过控制系统依据所述前支架301和所述后支架302与中心线之间夹角的区别来供给配重液以平衡游梁4的配重。
在本发明中，当因为调节前支架301和后支架302导致游梁配重发生变化时，一方面通过移动自平衡配重箱10来实现配重，另外通过控制系统依据所需调节自平衡配重箱10的自重从而实现对游梁的配重。
本发明通过自平衡配重箱10两个方面的作用来平衡抽油机的载荷，能够有效的缓冲抽油机启动时和运转过程中各部件受力的急剧变化，从而很好的自动适应油井的载荷变化曲线，平衡前支架301和后支架302之间夹角调整对抽油机的影响，从而使其能够适应前述的改进。
综合上述，在本发明中主要是通过设置应力弧装置8以及优化前支架301和后支架302的不同步滑动来调整其与铰接件和投影点连线中心线的夹角来 降低应力集中，从而为将曲柄连杆机构应用于大冲程的游梁式抽油机服务。
以上实施例仅为本申请的示例性实施例，不用于限制本申请，本申请的保护范围由权利要求书限定。本领域技术人员可以在本申请的实质和保护范围内，对本申请做出各种修改或等同替换，这种修改或等同替换也应视为落在本申请的保护范围内。
工业实用性
本发明通过设置应力弧装置以及优化支架机构的不同步滑动来调整其与铰接件与投影点连线的夹角来降低应力集中，从而为将曲柄连杆机构应用于大冲程的游梁式抽油机服务。

Claims (10)

  1. 一种大冲程游梁式抽油机，包括底座(1)和固定安装在所述底座(1)一端的驱动机构(2)，在所述底座(1)另一端通过支架机构(3)设置有游梁(4)，在所述游梁(4)的前端安装有驴头(5)，在所述游梁(4)的后端通过连杆(6)与所述驱动机构(2)连接，其特征在于，所述游梁(4)上通过滑动的方式活动安装有自平衡配重箱(10)，所述游梁(4)上滑动安装有中座(7)，所述驱动机构(2)通过连杆(6)驱动游梁(4)带动所述驴头(5)发生运动，其中，所述连杆(6)和所述游梁(4)的连接处以及所述中座(7)和支架机构(3)的连接处均安装有用于防止出现应力集中的应力弧装置(8)；
    所述支架机构(3)包括顶端通过铰接件连接的前支架(301)和后支架(302)，所述前支架(301)和所述后支架(302)在所述底座(1)上沿着游梁(4)的长轴方向活动安装以调整所述前支架(301)和所述后支架(302)之间的夹角来改善支架机构(3)的受力状态。
  2. 根据权利要求1所述的一种大冲程游梁式抽油机，其特征在于，设定：
    A为所述驴头(5)至所述中座(7)的距离；
    C为所述中座(7)至所述游梁(4)后端的距离；
    I为所述驱动机构(2)转动中心至所述中座(7)在所述底座(1)上投影之间的距离；
    P为所述连杆(6)的长度；
    H为所述中座(7)至所述底座(1)之间的距离；
    G为所述驱动机构(2)转动中心至所述底座(1)之间的距离；
    R为所述驱动机构(2)的转动半径；
    所述A＝5791～7395毫米，所述C＝3050～3611毫米，所述I＝3050～3569毫米，所述P＝5759～7386毫米，所述H＝8636～10838毫米，所述G＝2819～3643毫米，所述R＝1524～2047毫米。
  3. 根据权利要求2所述的一种大冲程游梁式抽油机，其特征在于，所述 游梁式抽油机通过试凑法调整所述距离、长度和转动半径并通过动力学仿真计算输出所述游梁式抽油机的动态特征曲线，并依据所述动态特征曲线的反馈再次调整所述距离、长度和转动半径直至所述动态特征曲线达到最佳。
  4. 根据权利要求3所述的一种大冲程游梁式抽油机，其特征在于，所述游梁(4)通过连杆(6)与所述驱动机构(2)的曲柄连接形成曲柄连杆结构，所述游梁(4)和支架机构(3)通过调整所述距离、长度和转动半径形成大冲程的游梁结构，所述曲柄连杆结构和所述应力弧装置(8)以及支架机构(3)配合大冲程的游梁结构。
  5. 根据权利要求1所述的一种大冲程游梁式抽油机，其特征在于，所述应力弧装置(8)沿着所述游梁(4)的长轴方向向两端呈弧形延伸。
  6. 根据权利要求5所述的一种大冲程游梁式抽油机，其特征在于，所述应力弧装置(8)包括与支架机构(3)连接的轴承座(801)和与所述中座(7)连接的贴片体(802)；
    所述轴承座(801)的剖面呈梯形，且所述轴承座(801)和所述贴片体(802)之间通过弧形延展体(803)连接，所述轴承座(801)、弧形延展体(803)和所述贴片体(802)为一体化结构。
  7. 根据权利要求1所述的一种大冲程游梁式抽油机，其特征在于，所述铰接件两侧均设置有延伸柱(9)，所述前支架(301)和所述后支架(302)的另一端均活动安装在所述底座(1)两侧，所述前支架(301)和所述后支架(302)分别套设在所述铰接件两侧的延伸柱(9)上。
  8. 根据权利要求7所述的一种大冲程游梁式抽油机，其特征在于，设定所述中座(7)的铅垂线为中心线，所述前支架(301)和所述中心线之间的夹角为0-10°，所述后支架(302)和所述中心线之间的夹角为0-16°。
  9. 根据权利要求7所述的一种大冲程游梁式抽油机，其特征在于，在所述前支架(301)和后支架(302)上均沿着轴向均固定安装有相对设置的滑轨，每个所述滑轨上均设置有沿着所述滑轨自由活动的游离底座(303)，两个所述游离底座之间通过气弹簧组(304)连接，所述气弹簧组(304)通过 多个首尾顺次连接的自锁型气弹簧组成，且每个相邻自锁型气弹簧以及自锁型气弹簧与所述游离底座(303)之间均通过铰接连接。
  10. 根据权利要求8所述的一种大冲程游梁式抽油机，其特征在于，所述自平衡配重箱(10)内部设置有多个呈回形设置的隔离挡板，并且在所述自平衡配重箱(10)上对应所述隔离挡板的入口处设置有注液孔；
    所述注液孔通过注液输导管(11)连接有设置在所述底座(1)上的配液箱(12)，所述配液箱(12)通过控制系统依据所述前支架(301)和所述后支架(302)与中心线之间夹角的区别来供给配重液以平衡游梁(4)的配重。
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Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
CN214035623U (zh) * 2021-03-31 2021-08-24 德瑞石油装备（青岛）有限公司 一种大冲程游梁式抽油机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1540132A (zh) * 2003-10-29 2004-10-27 金成群 抽油机配重体的制造方法
CN206382788U (zh) * 2017-05-15 2017-08-08 山东神宇机械制造有限公司 一种游梁式抽油机支架焊接工装
US20170329311A1 (en) * 2016-05-13 2017-11-16 General Electric Company Beam pumping unit and method of operation
CN110566163A (zh) * 2019-09-17 2019-12-13 德瑞石油装备（青岛）有限公司 一种超大冲程和荷载的游梁式抽油机
CN111441600A (zh) * 2020-05-19 2020-07-24 山西省工业设备安装集团有限公司 工地通道走廊平台模板加固结构

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1210992A (en) * 1983-07-28 1986-09-09 Quentin Siebold Off-vertical pumping unit
US6015271A (en) * 1998-10-14 2000-01-18 Lufkin Industries, Inc. Stowable walking beam pumping unit
CN101100936B (zh) * 2007-07-22 2011-08-17 周宏强 游梁式液压节能抽油机
CN100572745C (zh) * 2007-08-24 2009-12-23 北京嘉捷联众节能技术有限公司 发电态能量再利用电液压节能游梁式抽油机
CN201381840Y (zh) * 2009-03-20 2010-01-13 新疆维吾尔自治区第三机床厂 大型长冲程重载荷节能型抽油机
CN201866107U (zh) * 2010-11-05 2011-06-15 杭州巨能铸钢有限公司 一种轴承座
CN102155190B (zh) * 2011-05-10 2012-11-07 高林 滑轮增程游梁式抽油机
CN102536171A (zh) * 2012-02-07 2012-07-04 克拉玛依市派腾节能科技有限公司 斜挂泵式小型液压系统抽油机
CN104060968A (zh) * 2014-07-17 2014-09-24 李世銮 一种数字化抽油机
CN204186355U (zh) * 2014-10-31 2015-03-04 白红东 一种游梁式抽油机
CN204922409U (zh) * 2015-09-17 2015-12-30 山东神宇机械制造有限公司 抽油机支架后腿定位保护装置
CN205154108U (zh) * 2015-10-19 2016-04-13 德瑞石油装备（青岛）有限公司 一种抽油机的调试平台
CN205089288U (zh) * 2015-10-21 2016-03-16 胜利油田高原石油装备有限责任公司 游梁式抽油机新型支架
US10941761B2 (en) * 2017-01-17 2021-03-09 Ravdos Holdings Inc. Rear leg connection for beam pumping unit
WO2019053513A1 (en) * 2017-09-12 2019-03-21 4Iiii Innovations Inc. OIL WELL PUMP INSTRUMENTATION DEVICE AND SURFACE CARD GENERATION METHOD
WO2019005850A1 (en) * 2017-06-26 2019-01-03 General Electric Company INTEGRATED PREFABRICATED FOUNDATION BASE FOR PUMP UNIT
US20190107105A1 (en) * 2017-10-10 2019-04-11 Lufkin Industries, Llc Linear Drive Beam Pumping Unit
CN110947677A (zh) * 2019-12-13 2020-04-03 怀化耀岷汽车货厢制造有限公司 一种基于汽车曲轴加工的清洗防锈一体化装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1540132A (zh) * 2003-10-29 2004-10-27 金成群 抽油机配重体的制造方法
US20170329311A1 (en) * 2016-05-13 2017-11-16 General Electric Company Beam pumping unit and method of operation
CN206382788U (zh) * 2017-05-15 2017-08-08 山东神宇机械制造有限公司 一种游梁式抽油机支架焊接工装
CN110566163A (zh) * 2019-09-17 2019-12-13 德瑞石油装备（青岛）有限公司 一种超大冲程和荷载的游梁式抽油机
CN111441600A (zh) * 2020-05-19 2020-07-24 山西省工业设备安装集团有限公司 工地通道走廊平台模板加固结构

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Welding Structure and Manufacture", 31 March 2016, CN, ISBN: 978-7-5682-1954-9, article LUO, HUI ET AL.: "Structural manufacturability review of heavy-duty vehicle axle housing", pages: 174 - 175, XP009540133 *

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