WO2013091402A1 - 多级减速多级平衡抽油机 - Google Patents

多级减速多级平衡抽油机 Download PDF

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Publication number
WO2013091402A1
WO2013091402A1 PCT/CN2012/080958 CN2012080958W WO2013091402A1 WO 2013091402 A1 WO2013091402 A1 WO 2013091402A1 CN 2012080958 W CN2012080958 W CN 2012080958W WO 2013091402 A1 WO2013091402 A1 WO 2013091402A1
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Prior art keywords
stage
reducer
shaft
pumping unit
fixed
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PCT/CN2012/080958
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English (en)
French (fr)
Inventor
李娟�
徐金超
李举辉
韩修廷
孙盛祥
梁宏宝
韩梅
Original Assignee
大庆大华宏业石油工程技术有限公司
中国石油大学(华东)
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Publication of WO2013091402A1 publication Critical patent/WO2013091402A1/zh

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Classifications

    • 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
    • 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
    • F04B47/00—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps
    • F04B47/02—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level
    • F04B47/028—Pumps or pumping installations specially adapted for raising fluids from great depths, e.g. well pumps the driving mechanisms being situated at ground level details of the walking beam

Definitions

  • the invention relates to the technical field of oil fields, in particular to a multi-stage deceleration multi-stage flat #f pumping unit. Background technique
  • the technology for extracting energy such as oil, natural gas and coalbed methane is mainly an artificial lifting method, and mechanical lifting is a commonly used artificial lifting method.
  • the rod pumping system is the earliest and most widely used mechanical lifting system. According to incomplete statistics, more than 70% of China's oil wells use rod pumping systems, while rod pumping systems are used for ground dragging.
  • the equipment is a pumping unit. After more than 100 years of development, the pumping unit has undergone great changes in both structure and performance. It has evolved from a simple beam pumping unit to a beam pumping unit, a beamless pumping unit, and a tower type. Pumping machines and other types.
  • the beam pumping unit includes a conventional beam pumping unit, a variable diameter beam pumping unit, a pendulum beam pumping unit, etc.; the beamless pumping unit includes a chain pumping unit and a sun gear type. Pumping unit, involute profile pumping unit, etc.; tower type pumping unit includes reversing pumping unit, linear reciprocating pumping unit, etc.
  • a variety of special pumping units have been developed to meet the requirements of different working conditions such as heavy oil, deep wells and low production wells.
  • the beam pumping unit is still the main equipment for oil and gas coalbed methane mining, and also the main energy-consuming equipment.
  • the energy consumed by the beam pumping unit is about 80% of the total power consumption. That is, the recreational pumping unit consumes more than 10 billion kilowatt-hours per year. .
  • the main reasons for the large power consumption of the beam pumping unit are: The pumping unit has a large volume and weight, many energy transmission links, and high energy consumption; the effective load rate is low, the motor instantaneously performs negative work, and the reducer has a short periodicity. There is a negative torque, a large fluctuation in power torque, and the like. Summary of the invention
  • the present invention provides a multi-stage deceleration multi-stage balanced pumping
  • the multi-stage deceleration multi-stage balance pumping unit is combined with multi-stage deceleration and multi-harmonic multiple superposition balance, and is equipped with a flexible pulley system, which can reduce the amplitude of alternating load fluctuations, overcome the cyclical instantaneous negative work and deceleration of the motor.
  • the problem of negative torque is short-term cyclical, which makes the pumping unit low in energy consumption and small in torque fluctuation.
  • the technical proposal of the invention is: a multi-stage deceleration multi-stage balanced pumping unit, comprising an electric motor and a first-stage speed reducer connected to the output shaft of the electric motor, wherein the output shaft of the primary speed reducer drives the second-stage deceleration through the bevel gear pair
  • the shaft of the two-stage reducer rotates the shaft of the three-stage reducer through the spur gear pair.
  • the first-stage reducer is connected with a three-stage flat #f weight
  • the second-stage reducer is fixed with a second-level flat #f heavy.
  • the third-stage reducer shaft has a first-stage counterweight connected by a crank.
  • a small bevel gear is disposed on the output shaft of the primary reducer, a large bevel gear and a pinion gear are fixed on the shaft of the secondary reducer, and a large gear is fixed on the shaft of the three-stage reducer,
  • the bevel pinion meshes with the large bevel gear, and the pinion gear meshes with the large gear.
  • the ratio of the pinion of the bevel pinion to the bevel pinion is 1:2 or 1:3 or 1:4, and the gear ratio of the pinion to the large gear is 1:2 or 1:3 or 1:4.
  • the primary speed reducer is a needle cycloidal speed reducer.
  • the primary reduction gear output shaft and the secondary reducer shaft are on the same horizontal plane and perpendicular to each other, and the three-stage reducer shaft and the first-stage reducer output shaft and the secondary reducer shaft are In the same horizontal plane, this arrangement can make rational use of space, making the pumping unit compact and small in size.
  • the weight of the primary balance weight is greater than the secondary balance weight, and the weight of the secondary balance weight is greater than the third-level balance weight, so that the pumping unit is balanced overall.
  • the pumping unit further comprises a bracket, a movable pulley, a fixed pulley and a flexible rope, wherein the movable pulley is fixed on the first balance weight, the fixed pulley is fixed at one end of the bracket, and the other end of the bracket is fixed with a support, the flexible rope One end is fixed on the support, and the other end is connected to the wellhead by bypassing the movable pulley and the fixed pulley.
  • the invention mainly solves the problems of large energy consumption and large fluctuation of power torque of the recreational pumping unit.
  • the invention has the following beneficial effects: Due to the above scheme, the pumping unit uses multi-stage deceleration, wherein the first-stage reducer is a needle-shaped cycloidal speed reducer, the third-stage reducer is a spur gear reducer, and the cycloidal speed reduction is utilized.
  • the high gear ratio of the machine and the high torque characteristics of the spur gear reducer, and the speed reducer shafts of each stage are provided Balanced weight, multi-level balance is realized by the principle of harmonic superposition, and the power torque fluctuation is stable, thereby reducing the heat loss amount which is proportional to the power torque fluctuation, thereby improving the effective mechanical work and system efficiency, and reducing the energy consumption. . DRAWINGS
  • Figure 1 is a schematic view of the structure of the present invention
  • a multi-stage deceleration multi-stage balance pumping unit comprises a bracket 7, an electric motor 2 and a primary speed reducer 3 connected to an output shaft of the electric motor 2, wherein the primary speed reducer 3 is preferably needle-shaped. Cycloid reducer, pin cycloid reducer features high gear ratio.
  • the pumping unit also includes a secondary reducer and a three-stage reducer.
  • the pumping unit further includes a reducer housing 5, wherein the reducer housing 5 is provided with a secondary reducer shaft 15 and a three-stage reducer shaft 16, and the output shaft of the primary speed reducer 3 passes through a pair of bevel gears
  • the secondary driven secondary reducer shaft 15 rotates to form a secondary reducer, and the secondary reducer shaft 15 drives the three-stage reducer shaft 16 through another pair of spur gear pairs to form a three-stage reducer, wherein three stages of speed reduction
  • the spur gear drive features high torque.
  • the output shaft of the primary speed reducer 3 and the secondary reducer shaft 15 are on the same horizontal plane and perpendicular to each other.
  • the output shaft of the primary speed reducer 3 is provided with a bevel pinion 17 and the secondary reducer shaft 15 is fixed.
  • the bevel gear 1 and the pinion 10, the three-stage reducer shaft 16 is in the same horizontal plane as the primary reducer 3 output shaft and the secondary reducer shaft 15, and the third-stage reducer shaft 16 A large gear 11 is fixed, the small bevel gear 17 meshes with the large bevel gear 1, and the pinion 10 meshes with the large gear 11.
  • the bevel pinion 17 and the bevel pinion 1 constitute the bevel gear pair; the pinion 10 and the large gear 11 constitute the spur gear pair.
  • the gear ratio between the bevel pinion 17 and the bevel pinion 1 is an integral multiple, and the gear ratio of the pinion 10 to the large gear 11 is also an integral multiple.
  • the gear ratio of the bevel pinion 17 to the bevel pinion 1 is 1:2 or 1:3 or 1:4, and the gear ratio of the pinion 10 to the large gear 11 is 1:2 or 1:3 or 1: 4.
  • the first-stage reducer 3 is connected with a three-stage balance weight 4, and the second-stage reducer shaft 15 is connected with a secondary balance weight 6.
  • the third-stage reducer shaft 16 is connected with a first-stage balance weight 13 through a crank 14, wherein The weight of the primary balance weight 13 is greater than the secondary balance weight 6, and the weight of the secondary balance weight 6 is greater than the tertiary balance weight 4.
  • the specific weight of the above-mentioned balance weights can be calculated according to the actual oil well conditions on site and the structural size of the pumping unit used.
  • the pumping unit further includes a movable pulley 12, a fixed pulley 8 and a flexible cord 9.
  • the first balance weight 13 is fixed with a movable pulley 12, wherein the distance between the movable pulley 12 and the center of the third-stage reducer shaft 16 can be adjusted according to the oil well load, and the three-stage reducer shaft 16 is connected to the first-stage balance by the crank 14.
  • Weight 13, the crank 14 has different connection positions, and the movable pulley 12 can be respectively connected to these positions to change the crank radius.
  • One end of the bracket 7 is fixed with a fixed pulley 8 , and the other end is fixed with a support.
  • One end of the flexible rope 9 is fixed on the support, and the other end is wound around the movable pulley 12 and the fixed pulley 8 to be connected to the wellhead.
  • the motor 2 drives the first-stage reducer 3 to rotate, and the output shaft of the first-stage reducer 3 drives the three-stage balance weight 4 to form a three-stage balance torque, and adjusts the output shaft of the reducer 3 to perform work;
  • the output shaft drives the secondary reducer shaft 15 to rotate through the bevel gear pair, thereby driving the secondary balance weight 6 to perform a rotary motion to form a secondary balance torque and balance the torque fluctuation;
  • the secondary reducer shaft 15 drives the third stage through the spur gear pair.
  • the reducer shaft 16 moves, thereby driving the first balance weight B to perform a rotary motion, forming a first-level balance torque to balance the oil well load;
  • the flexible rope 9 passes the crank 14 upper movable pulley 12 and the wellhead fixed pulley 8 and the sucker rod column and the well"
  • the f pump is connected to convert the rotary motion into a reciprocating motion of the downhole pump.
  • the motor can usually adopt a closed squirrel cage asynchronous motor.
  • Figure 2 Figure 3 and Figure 4 show the oil well load torque after primary balance, secondary balance and tertiary balance.
  • Various torque fluctuation curves are described in detail below:
  • the oil well load torque a is superimposed with the first-level equilibrium torque b to obtain the first-order balanced net torque c.
  • the net torque c after the first-level balance has a negative torque value.
  • the fluctuation range is large;
  • Figure 3 after the first-order equilibrium net torque c and the secondary balance torque d are superimposed, the net-balanced net e is obtained, and it is seen that the net torque e after the second-level balance has eliminated the negative value and fluctuates.
  • the amplitude is also small; in Figure 4, after the secondary balance net torque e and the three-stage balance torque f are superimposed to obtain the three-stage equilibrium net torque g, it can be seen that the torque fluctuation of the net torque g after the three-stage balance is further reduced, tending It is smooth and always has a positive value during the crank rotation period.
  • the three-stage balance torque f period is an integral multiple of the two-stage balance torque d period, and the multiple is the gear ratio of the large bevel gear 1 and the bevel pinion 17, and the second-balanced torque d period is the first-level flat #f-torque b An integral multiple of the period, the multiple of which is the gear ratio of the large gear 11 to the pinion 10.
  • the weight of the primary balance weight 13 is greater than the secondary balance weight 6, the weight of the secondary balance weight 6 is greater than the tertiary balance weight 4, which makes the amplitude of the torque fluctuation curve smaller.
  • the pumping unit adopts multi-stage deceleration, which realizes multi-stage balance by using the principle of harmonic superposition.
  • the multi-stage balance shaft is parallel-crossed and combined, and the phase is adjusted to achieve stable power torque fluctuation, thereby reducing the fluctuation with power torque.
  • the amount of heat loss in a positive proportional function increases the effective mechanical work and system efficiency and reduces energy consumption.
  • the pumping unit has a compact overall structure, small volume and weight, and low steel consumption, further reducing energy consumption.

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Abstract

一种多级减速多级平衡抽油机，包括电动机（2）及与电动机（2）输出轴相连的一级减速器（3），所述的一级减速器（3）输出轴通过锥齿轮副带动二级减速器轴（15）转动，二级减速器轴（15）通过直齿轮副带动三级减速器轴（16）转动，其中一级减速器（3）输出轴上连接有三级平衡重（4），二级减速器轴（15）上连接有二级平衡重（6），三级减速器轴（16）上通过曲柄（14）连接有一级平衡重（13）。该多级减速多级平衡抽油机通过多级减速与多谐波倍数叠加平衡相结合，配套柔性滑轮体系，减小交变载荷波动幅度，克服电机周期性瞬时做负功及减速器周期性短时存在负扭矩问题，使抽油机能耗低、扭矩波动小。

Description

多级减速多级平衡抽油机
技术领域
本发明涉及油田技术领域， 具体的说是一种多级减速多级平 #f抽油机。 背景技术
目前世界范围内开采石油、天然气及煤层气等能源的技术主要为人工举升 方法， 其中机械举升是一种常用的人工举升手段。 有杆泵抽油系统是应用最早 且应用最广泛的机械举升系统， 据不完全统计， 中国 70%以上的油井釆用有杆 泵抽油系统， 而有杆泵抽油系统的地面拖动设备是抽油机。 抽油机经过百余年 的发展， 无论是结构还是性能都发生了很大变化， 在结构上从简易游梁抽油机 发展为游梁抽油机、 无游梁抽油机、 塔架式抽油机等多种类型。 其中游梁抽油 机包括常规游梁型抽油机、 调径变矩游梁抽油机、 摆杆式游梁抽油机等； 无游 梁抽油机包括链条抽油机、 天轮式抽油机、 渐开线异形抽油机等； 塔架式抽油 机包括换向抽油机、 直线往复式抽油机等。 在性能上发展了适应稠油、 深井、 低产井等不同工况要求的多种特殊抽油机。但是游梁式抽油机由于结构稳固可 靠、 维修方便的优点， 仍然是石油天然气煤层气开采的主要设备， 也是主要的 耗能设备。 有资料表明， 我国油田生产成本的三分之一为电能消耗， 游梁式抽 油机消耗的电能约为总电能消耗的 80%,即游粱式抽油机每年耗电 100多亿千 瓦时。 造成游梁式抽油机耗电量大的主要原因是： 抽油机体积和重量较大， 能 量传递环节多， 能耗大； 有效负载率低， 电机瞬时做负功， 减速器周期性短时 存在负扭矩， 功率扭矩波动较大等。 发明内容
为了克服现有技术中上述的不足， 本发明提供一种多级减速多级平衡抽油 机， 该多级减速多级平衡抽油机通过多级减速与多谐波倍数叠加平衡相结合， 配套柔性滑轮体系， 能够减小交变载荷波动幅度， 克服电机周期性瞬时做负功 及减速器周期性短时存在负扭矩的问题， 使抽油机能耗低、 扭矩波动小。
本发明的技术方案是： 一种多级减速多级平衡抽油机， 包括电动机及与电 动机输出轴相连的一级减速器， 所述的一级减速器输出轴通过锥齿轮副带动二 级减速器轴转动， 二级减速器轴通过直齿轮副带动三级减速器轴转动， 其中一 级减速器上连接有三级平 #f重， 二级减速器轴上固定有二级平 #f重， 三级减速 器轴上通过曲柄连接有一级平衡重。
所述的一级减速器输出轴上设有小锥齿轮， 所述的二级减速器轴上固定有 大锥齿轮及小齿轮， 所述的三级减速器轴上固定有大齿轮， 所述的小锥齿轮与 大锥齿轮相啮合， 所述的小齿轮与大齿轮相啮合。
优选的是， 小锥齿轮与大锥齿轮的齿数比为 1 : 2或 1 : 3或 1 : 4, 小齿轮 与大齿轮的齿数比为 1 : 2或 1 : 3或 1 : 4。
其中， 所述的一级减速器为针形摆线减速器。
优选的是， 所述的一级减速器输出轴与二级减速器轴在同一水平面上且方 向相互垂直， 所述的三级减速器轴与一级减速器输出轴及二级减速器轴在同一 水平面内， 这样设置可以合理利用空间， 使得抽油机结构紧凑， 体积小。
其中， 一级平衡重的重量大于二级平衡重， 二级平衡重的重量大于三级平 衡重， 以使抽油机整体平衡。
优选的是， 该抽油机还包括支架、 动滑轮、 定滑轮和柔性绳， 所述动滑轮 固定在一级平衡重上， 定滑轮固定在支架的一端， 支架的另一端固定有支座， 柔性绳的一端固定在所述支座上， 其另一端绕过动滑轮及定滑轮后连接井口。
本发明主要可以解决游粱式抽油机能耗大、 功率扭矩波动大的问题。 本发明具有如下有益效果： 由于采取上述方案， 该抽油机釆用多级减速， 其中一级减速器为针形摆线减速器， 三级减速器为直齿轮减速器， 利用了摆线 减速机的高传动比与直齿轮减速机的高扭矩特点， 并且各级减速器轴上均设有 平衡重， 利用谐波叠加原理实现多级平衡， 实现了功率扭矩波动平稳， 从而降 低了与功率扭矩波动成正比例函数关系的热损失量， 进而提高了有效机械功和 系统效率， 减少了能量消耗。 附图说明
图 1是本发明的结构示意图；
图 2至图 4是本发明各级减速平衡的扭矩曲线图。
图中： 1-大锥齿轮， 2-电动机， 3-—级减速器， 4-三级平衡重， 5-减速机壳 体， 6二级平衡重， 7-支架， 8-定滑轮， 9-柔性绳， 10-小齿轮， 11-大齿轮， 12- 动滑轮， 13—级平衡重， 14-曲柄, 15二级减速器轴， 16三级减速器轴， 17小 锥齿轮， a油井载荷扭矩， b—级平衡扭矩 c-一级平衡后净扭矩， d二级平衡 扭矩， e二级平衡后净扭矩， f三级平 #f扭矩， g三级平衡后净扭矩。 具体实施方式
下面结合附图对本发明作进一步说明：
由图 1所示， 一种多级减速多级平衡抽油机， 包括支架 7、 电动机 2及与 电动机 2输出轴相连的一级减速器 3， 所述的一级减速器 3优选采用针形摆线 减速器， 针形摆线减速器具有高传动比的特点。 该抽油机中还包括二级减速器 和三级减速器。 该抽油机还包括有减速器壳体 5， 减速器壳体 5内设有二级减 速器轴 15及三级减速器轴 16， 所述的一级减速器 3输出轴通过一对锥齿轮副 带动二级减速器轴 15转动， 构成了二级减速器， 二级减速器轴 15通过另一对 直齿轮副带动三级减速器轴 16转动， 构成了三级减速器， 其中三级减速器的 直齿轮传动具有高扭矩的特点。所述的一级减速器 3输出轴与二级减速器轴 15 在同一水平面上且方向相互垂直，一级减速器 3输出轴上设有小锥齿轮 17，二 级减速器轴 15上固定有大锥齿轮 1及小齿轮 10，所述的三级减速器轴 16与一 级减速器 3输出轴及二级减速器轴 15在同一水平面内，且三级减速器轴 16上 固定有大齿轮 11 , 所述的小锥齿轮 17与大锥齿轮 1相啮合， 小齿轮 10与大齿 轮 11相啮合。 其中， 小锥齿轮 17和大锥齿轮 1构成所述锥齿轮副； 小齿轮 10 和大齿轮 11构成所述直齿轮副。
小锥齿轮 17与大锥齿轮 1之间的齿数比为整数倍，小齿轮 10与大齿轮 11 的齿数比也为整数倍。 其中， 小锥齿轮 17与大锥齿轮 1的齿数比为 1 : 2或 1 : 3或 1 : 4， 所述小齿轮 10与大齿轮 11的齿数比为 1 : 2或 1 : 3或 1 : 4。
所述的一级减速器 3上连接有三级平衡重 4，二级减速器轴 15上连接有二 级平衡重 6， 三级减速器轴 16上通过曲柄 14连接有一级平衡重 13， 其中一级 平衡重 13的重量大于二级平衡重 6， 二级平衡重 6的重量大于三级平衡重 4。 上述各级平衡重的具体大小可以根据现场实际油井工况及使用的抽油机结构 尺寸计算得到。
所述抽油机还包括有动滑轮 12、 定滑轮 8和柔性绳 9。 所述的一级平衡重 13上固定有动滑轮 12， 其中动滑轮 12到三级减速器轴 16中心的距离可以根 据油井载荷调整， 所述三级减速器轴 16通过曲柄 14连接所述一级平衡重 13， 曲柄 14上有不同的连接位置， 动滑轮 12可以分别连接到这些位置， 以改变曲 柄半径。 支架 7的一端固定有定滑轮 8、 另一端固定有支座， 柔性绳 9的一端 固定在支座上， 另一端绕过动滑轮 12、 定滑轮 8后连接井口。
该抽油机工作时， 电机 2带动一级减速器 3转动， 一级减速器 3输出轴带 动三级平衡重 4运动， 形成三级平衡扭矩， 调整减速器 3输出轴做功； 一级减 速器 3输出轴通过锥齿轮副带动二级减速器轴 15转动，从而带动二级平衡重 6 作旋转运动， 形成二级平衡扭矩， 平衡扭矩波动； 二级减速器轴 15通过直齿 轮副带动三级减速器轴 16运动， 从而带动一级平衡重 B做旋转运动， 形成一 级平衡扭矩， 以平衡油井载荷； 柔性绳 9通过曲柄 14上动滑轮 12及井口定滑 轮 8与抽油杆柱、 井" f泵相连， 把旋转运动转化为井下泵往复运动。 其中， 电 机可以通常采用封闭式鼠笼型异步电动机。
图 2、 图 3与图 4为油井载荷扭矩经一级平衡、 二级平衡及三级平衡后的 各种扭矩波动曲线， 下面对其详细说明： 图 2中油井载荷扭矩 a与一级平衡扭 矩 b叠加得到一级平衡后净扭矩 c，可看出一级平衡后净扭矩 c存在扭矩负值， 且波动幅度较大； 图 3中一级平衡后净扭矩 c与二级平衡扭矩 d叠加后得到二 级平衡后净扭矩 e, 看出二级平衡后净扭矩 e已消除负值，且波动幅度也较小； 图 4中二级平衡后净扭矩 e与三级平衡扭矩 f叠加后得到三级平衡后净扭矩 g， 可看出三级平衡后净扭矩 g的扭矩波动进一步减小， 趋于平稳， 且曲柄旋转周 期内始终保持正值。 其中， 三级平衡扭矩 f周期为二级平衡扭矩 d周期的整数 倍， 其倍数即为大锥齿轮 1及小锥齿轮 17的齿数比， 二级平衡扭矩 d周期为 一级平 #f扭矩 b周期的整数倍， 其倍数为大齿轮 11与小齿轮 10的齿数比。 且 由于一级平衡重 13的重量大于二级平衡重 6，二级平衡重 6的重量大于三级平 衡重 4， 这使得扭矩波动曲线幅度变小。
终上所述， 该抽油机采用多级减速， 利用谐波叠加原理实现多级平衡， 多 级平衡轴平行交叉结合， 调相位， 实现了功率扭矩波动平稳， 从而降低了与功 率扭矩波动成正比例函数关系的热损失量， 进而提高了有效机械功和系统效 率， 减少了能量消耗。 并且该抽油机整体结构紧凑， 体积和重量小， 钢材消耗 少， 进一步减少了能量消耗。 可以理解的是， 以上实施方式仅仅是为了说明本发明的原理而采用的示例 性实施方式， 然而本发明并不局限于此。 对于本领域内的普通技术人员而言， 在不脱离本发明的精神和实质的情况下， 可以做出各种变型和改进， 这些变型 和改进也视为本发明的保护范围。

Claims

1. 一种多级減速多级平衡抽油机， 包括电动机（2)及与电动机（2)输 出轴相连的一级减速器（3) , 其特征在于： 所述的一级减速器（3)输出轴通 过锥齿轮副带动二级减速器轴（ 15 )转动， 二级减速器轴（ 15 )通过直齿轮副 带动三级减速器轴 （16)转动， 其中一级减速器（3)输出轴上连接有三级平 衡重（4)， 二级减速器轴（15)上连接有二级平衡重（6) , 三级减速器轴（16) 上通过曲柄 （14)连接有一级平衡重（13) 。
2. 根据权利要求 1 所述的多级减速多级平衡抽油机， 其特征在于： 所述 的一级减速器（3)输出轴上设有小锥齿轮（17) ， 所述的二级减速器轴（ 15) 上固定有大锥齿轮（1 )及小齿轮（10) ， 所述的三级减速器轴（16)上固定 有大齿轮（11 ) ， 所述的小锥齿轮（17) 与大锥齿轮（1)相啮合， 所述的小 齿轮（10)与大齿轮（11 )相啮合。
3. 根据权利要求 2所述的多级减速多级平衡抽油机， 其特征在于： 小锥 齿轮（17) 与大锥齿轮（1 ) 的齿数比为 1: 2或 1: 3或 1: 4, 小齿轮（10) 与大齿轮（ 11 ) 的齿数比为 1: 2或 1: 3或 1: 4。
4. 根据权利要求 2所述的多级减速多级平衡抽油机， 其特征在于： 所述 的一级减速器（3)为针形摆线减速器。
5. 根据权利要求 2 所述的多级减速多级平衡抽油机， 其特征在于： 所述 的一级减速器 （3)输出轴与二级减速器轴 （15)在同一水平面上且方向相互 垂直， 所述的三级减速器轴（16) 与一级减速器 （3)输出轴及二级减速器轴
( 15)在同一水平面内。
6. 根据权利要求 1 所述的多级减速多级平衡抽油机， 其特征在于： 一级 平衡重（13)的重量大于二级平衡重（6) , 二级平衡重（6) 的重量大于三级 平衡重 (4)。
7. 根据权利要求 1 6 之一所述的多级减速多级平衡抽油机， 其特征在 于： 该抽油机还包括支架（ 7 )、 动滑轮（ 12 )、 定滑轮（ 8 )和柔性绳（ 9 )， 所述动滑轮（12) 固定在一级平衡重（13)上， 定滑轮（8) 固定在支架（7) 的一端， 支架（7)的另一端固定有支座， 柔性绳（9)的一端固定在所述支座 上， 其另一端绕过动滑轮（12)及定滑轮（8)后连接井口。
PCT/CN2012/080958 2011-12-23 2012-09-04 多级减速多级平衡抽油机 WO2013091402A1 (zh)

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