WO2016161611A1 - 一种双重减载防气抽油泵 - Google Patents
一种双重减载防气抽油泵 Download PDFInfo
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- WO2016161611A1 WO2016161611A1 PCT/CN2015/076218 CN2015076218W WO2016161611A1 WO 2016161611 A1 WO2016161611 A1 WO 2016161611A1 CN 2015076218 W CN2015076218 W CN 2015076218W WO 2016161611 A1 WO2016161611 A1 WO 2016161611A1
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- 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
Definitions
- the invention relates to an oil pump in the field of oil production engineering, in particular to an oil pump with double load shedding and anti-gas lock function.
- the object of the present invention is to provide a pumping pump with double load shedding and anti-gas lock function, thereby realizing that the pumping unit load can be significantly reduced and the probability of the sucker rod breaking off can be reduced under the premise of ensuring the displacement of the pumping pump.
- the oil pump also has the function of anti-gas lock.
- the present invention provides a double load shedding gas pump, the double load shedding gas pump is provided with a lifting short section, and one end of the lifting short section is connected with a first pump cylinder and a second pump cylinder in turn.
- the second pump cylinder has an inner diameter larger than the first pump cylinder inner diameter, and the second pump cylinder is connected to a fixed valve at one end of the first pump cylinder; the first pump cylinder and the second pump cylinder
- the cavity is respectively nested with a first piston and a second piston that are axially slidable, the first piston and The second pistons are axially penetrated and fixedly connected to each other;
- the second piston is spaced apart from the fixed valve, and an oil reservoir is formed between the second piston, the fixed valve and the second pump cylinder;
- the inner fixed connection of the other end of the lifting short section is provided with an upstream movable hood and a valve seat, and the valve seat is located between the upstream movable hood and the first piston;
- sucker rod penetrating the lifting nip, the first piston and the second piston, the first piston and the second piston respectively in the first pump barrel and with the lifting and lowering of the sucker rod
- the second pump cylinder slides up and down, and the bottom end of the sucker rod is connected with a downstream moving valve, and the downstream moving valve can abut or separate from the bottom end of the large piston, and the sucker rod is also active.
- An upstream movable valve that can be opened and closed with the valve seat is sleeved.
- the lifting sub-block includes a compression joint and an outer sealing cartridge assembly that are sealingly connected to each other, the first pump cylinder passing through a sealing shaft head and nesting on the outer peripheral wall of the sealing shaft head The circlip is coupled to the outer seal deck assembly.
- the outer seal deck assembly is internally provided with a valve seat shorting, and the short ends of the valve seat are respectively connected to the valve seat and the sealing shaft head, and the sealing shaft
- the middle portion of the head and the shorted portion of the valve seat constitutes an axially penetrating passage, and the first piston can slide up and down along the passage.
- a sealing sleeve is disposed between the valve seat shorting and the outer sealing card seat assembly, and a bearing ring is sequentially arranged in the axial direction between the sealing sleeve and the valve seat. a seal ring and a retaining ring, the pressure ring being located adjacent to the valve seat side.
- the outer peripheral wall of the sealing shaft head is connected with a metal sealing ring, and the metal sealing ring seal is embedded in the inner peripheral wall of the outer sealing card seat assembly.
- a plurality of balance holes are provided on a peripheral wall of one end of the second pump cylinder connected to the first pump cylinder.
- the second pump barrel is connected to the fixed valve by a fixed valve short circuit.
- the double load shedding gas-proof pump of the invention has the following characteristics and advantages:
- the double load shedding anti-gas pump of the present invention due to the combination of the large piston (second piston) and the small piston (first piston), ensures that the displacement of the pump is the displacement of the single stroke of the large piston. Compared with the prior art oil pump that uses only a single large piston, the load of the oil pump is significantly reduced.
- the upstream moving valve is slidably connected to the sucker rod, and during the process of switching the upper and lower strokes of the oil pump, the crude oil pressure in the oil pipe above the oil pump is applied upstream.
- the moving valve acts on the lifting nipple through the valve seat, thereby greatly reducing the impact load on the sucker rod during the switching of the upper and lower strokes, thereby reducing The probability of breaking off the sucker rod reduces the daily maintenance cost of the pump.
- the double load-reducing anti-gas pump of the present invention is provided with a downstream movable valve capable of mechanically opening and closing a large piston at the lower end of the sucker rod, thereby ensuring that the large piston can be quickly opened and the gas in the piston is eliminated during the downstroke.
- the effect of pressure on the opening or closing of the downstream moving valve realizes the function of anti-gas lock.
- FIG. 1 is an assembled view of a double load shedding gas pump of the present invention.
- 6-valve short, 7-pressure ring, 8-seal sleeve, 9-seal ring, 10-station ring, 11-seal shaft head;
- 16-large pump cylinder (second pump cylinder), 17-balance hole, 18-size piston short circuit, 19-large piston (second piston);
- 20-fixed valve short circuit 21-fixed Verne cover, 22- Fix the inner rib of the versatile cover, 23-fix the ball of Verne;
- the oil pump has a lifting short joint, specifically, the lifting short joint comprises a pressing joint 1 and an outer sealing seat assembly 5 which are sealedly connected to each other, and the upper end portion of the pressing joint 1 is connected with the oil pipe, and the outer seal is sealed.
- the lower end of the deck assembly 5 is sequentially connected with a small pump cylinder 15 and a large pump cylinder 16, and the inner diameter of the large pump cylinder is larger than the inner diameter of the small pump cylinder. Further, the inner portion of the large pump cylinder and the small pump cylinder are respectively nested.
- the large piston 19 and the small piston 14 are movable in the axial direction, and the two pistons are fixedly connected by a large-sized piston short-circuit 18, and the large piston and the small piston are axially penetrated.
- a sucker rod 27 extends through the lifting nip and a middle portion of the two pistons, and a lower moving end portion of the sucker rod 27 is fixedly coupled to a downstream moving valve 26, and the downstream moving valve 26 can abut and seal the lower end portion of the large piston 19, and
- the connection and transmission relationship between the sucker rod 27 and other structures of the pumping unit are prior art, and are not described herein.
- the lower end of the large pump cylinder 16 is fixedly connected with a fixed valve, and the inside of the large pump cylinder 16 between the large piston 19 and the fixed valve constitutes an oil storage chamber 28, and the large pump cylinder 16 and the fixed valve are short-circuited by a fixed valve.
- the fixed valve includes a fixed Verne cover 21 connected to the fixed valve short 20, and the fixed Versail cover 21 is fixedly connected with a fixed Versail inner rib 22 and a fixed Versail
- the seat 24 in addition, the inner peripheral wall of the fixed Verne cover 21 is provided with a ring boss, one end of the fixed Versail seat 24 abuts against the boss, and the other end abuts against a fixed Verne seat pressure cap 25, the fixed valve
- the function of the fixed valve is that when the two pistons are in the upstroke, the oil reservoir 28 is subjected to a negative pressure, the fixed Versaille 23 is lifted up, and the oil outside the oil pump can enter the oil reservoir 28.
- the oil in the oil reservoir 28 is compressed, the fixed valve is closed, the downstream moving valve 26 is opened, and the oil in the oil reservoir 28 enters the inner cavity of the large and small pistons.
- the inner portion of the compression joint 1 is fixedly coupled with an upstream movable hood 2 and a valve seat 4, and the sucker rod 27 is movably sleeved with an upstream movable valve 3 that can be opened and closed with the valve seat 4.
- the small pump cylinder 15 is fixedly coupled to the outer seal deck assembly 5 via a seal shaft head 11 and a snap spring 13 nested outside the seal shaft head 11.
- the outer sealing seat assembly 5 is internally provided with a valve seat connecting the valve seat 4 and the sealing shaft head 11, and the middle portion of the sealing shaft head 11 and the valve seat shorting 6 constitute an axial through passage 29, and the small piston 14 It can slide along the channel 29.
- the downstream moving valve 26 closes the large piston 19, and the small piston 14 moves up along the passage 29.
- the upstream moving valve 3 is jacked up. The oil enters the oil pipe above the compression joint 1 and is discharged to the ground.
- a sealing sleeve 8 is arranged between the valve seat shorting 6 and the outer sealing card seat assembly 5, and the sealing sleeve 8 and the valve seat are short-circuited 6 in the axial direction.
- the pressure ring 7, the seal ring 9 and the retaining ring 10 are located on the side close to the valve seat 4.
- the outer peripheral wall of the sealing shaft head 11 is embedded with a metal sealing ring 12, and the outer peripheral wall of the metal sealing ring 12 is disposed on a tapered surface, and can be sealed and embedded in a boss provided on the outer sealing card seat assembly 5, thereby preventing The foreign matter enters the valve seat portion, and the above is a prior art and will not be described.
- the upper end portion of the large pump cylinder 16 is provided with a plurality of balance holes 17 in the circumferential direction, so that when the down stroke of the oil pump is performed, the external liquid can be replenished to the small piston 14 and the large The annulus between the pump cylinders 16 can be discharged through the balance holes 17 during the upper stroke of the oil pump.
- the sucker rod 27 drives the downstream moving valve 26 to close the large piston 19, and drives the large and small pistons to ascend.
- the oil pressure in the inner chamber of the two pistons Under the action, the upstream moving valve 3 is jacked up, and the oil passes through the upstream moving vent 2 and enters the oil pipe connected to the pressing joint 1 and is discharged to the ground. Since the oil pump of the present invention is designed with large and small pistons connected to each other, the displacement of the pump can be ensured as the displacement of the single stroke of the large piston, and the inner diameter of the oil pipe connected to the compression joint 1 is consistent with the inner diameter of the small piston.
- the suspension load of the pumping unit is mainly from the liquid column pressure in the upper end of the small piston, considering the annulus between the small piston and the large pump cylinder.
- the lower end surface 30 is subjected to the pressure of the external oil, but the pressure is much smaller than the liquid column pressure in the upper oil pipe. Therefore, in the case of ignoring the pressure, the oil pump of the present invention has the same pump diameter as in the prior art (ie, Compared with the ordinary pump of the large pump cylinder of the present invention, the load is significantly reduced.
- the definition of the large piston cross-sectional area is S1
- the small piston cross-sectional area is S2
- the load of the pump in the prior art is S1
- W1 (F1-F2) ⁇ S1
- F1 pumping depth pressure, that is, the oil pressure in the oil pipe corresponding to the height difference between the wellhead and the pumping pump
- F2 sinking pressure, that is, the height difference between the downhole liquid level and the pumping pump Corresponding oil pressure in the oil pipe;
- the large piston compresses the oil in the oil storage chamber 28, the fixed valve is closed, and at the same time, under the action of the external load of the oil pump, the sucker rod 27 drives the downstream moving valve 26 to be faster. Down, thereby opening the large piston, the oil in the oil reservoir 28 enters the passage 29 through the large and small piston lumens.
- the large piston reaches the lower stroke limit position (the upper and lower strokes of the sucker rod determine the upper and lower stroke limit positions of the piston), the downstream moving valve closes the large piston to complete a pumping cycle.
- sucker rod 27 mechanically drives the downstream moving valve 26 to open ensures that the large piston can be quickly opened, thereby eliminating the influence of the gas pressure in the piston on the opening or closing of the downstream moving valve in the prior art, and realizing the function of the anti-gas lock. .
- the double-load-loading anti-gas pump of the present invention due to the combination of the large piston and the small piston, ensures that the displacement of the pump is the single-stroke displacement of the large piston, and compared with In the prior art, in the case of a single large piston pump, the oil pressure in the upper end of the oil pump is lowered, and the load on the pump is lowered.
- the upstream moving valve is slidably connected to the sucker rod, and the crude oil pressure in the oil pipe above the oil pump is applied to the upstream moving valve when the oil pump is switched on the down stroke.
- the upper part and the valve seat act on the lifting short section, thereby greatly reducing the impact load on the sucker rod during the switching of the upper and lower strokes, reducing the probability of the sucking rod breaking off and the daily maintenance cost of the oil pump.
- the double load shedding gas-proof pump of the present invention is provided with a downstream movable valve capable of mechanically opening and closing the large piston at the lower end of the sucker rod, thereby ensuring that the large piston can be quickly opened and the gas in the piston is eliminated during the downstroke.
- the effect of pressure on the opening or closing of the downstream moving valve realizes the function of anti-gas lock.
Abstract
提供了一种双重减载防气抽油泵，适用于采油工程领域。该抽油泵设有提升短节，提升短节一端设有相连接的小泵筒(15)和大泵筒(16)，其内腔分别嵌套有能沿轴向滑动的小活塞(14)和大活塞(19)，该组合设置的两活塞保证了抽油泵的排量为大活塞排量，同时抽油泵的负载明显降低。提升短节另一端的内部固定连接有上游动凡尔罩(2)和一阀座(4)，一抽油杆(27)贯穿提升短节及两活塞，且抽油杆(27)的端部连接有能抵接并封闭大活塞(19)的下游动阀(26)，抽油杆(27)上还活动套接有能与阀座(4)配合启闭的上游动阀(3)。在抽油泵上、下冲程转换时，油管内的油液压力可作用于上游动阀，进而降低了对抽油杆的冲击载荷。此外，通过抽油杆能控制下游动阀的启闭，实现了防气锁的功能。
Description
本发明涉及采油工程领域的一种抽油泵，尤指一种具有双重减载及防气锁功能的抽油泵。
随着油田开发时间的增加，地层的能量不断的消耗，使得靠天然能量开采原油的效果越来越差。因此，不得不靠人工增加地层能量来开采原油。其中，稠油注空气催化氧化采油技术在采油现场应用效果比较理想，使得其应用范围越来越大。目前注空气采油催化氧化采油在下泵生产阶段主要采用加气锚防气或普通的防气泵生产，但是随着注气(汽)量的不断增加，伴生气体含量较高，使得气(汽)体对抽油泵效率影响越来越大，在抽油过程中经常会出现气锁的现象，使得抽油泵的泵效降低，进而影响原油的采出速度。
同时，由于在深井作业中产液量很大，抽油泵工作中在上、下行程转换的过程中作用在抽油杆上的冲击载荷较大，而使得抽油杆断脱的概率大大提高，尤其是光杆部分断脱后，在油层压力较大的情况下可能会造成井喷等污染环境事故的发生，从而使得原油生产中的日常维修工作量加大，单位原油成本提高。
因此，针对上述问题有必要提供一种能够有效解决抽油泵的气锁问题、并能在保证抽油泵排量的前提下，明显降低抽油机负荷的减载防气抽油泵。
发明内容
本发明的目的在于提供一种具有双重减载及防气锁功能的抽油泵，进而实现在保证抽油泵排量的前提下，能够明显降低抽油机负荷并降低抽油杆断脱概率，同时该抽油泵还具有防气锁的功能。
为此，本发明提出一种双重减载防气抽油泵，所述双重减载防气抽油泵设有一提升短节，所述提升短节一端依次连接有第一泵筒和第二泵筒，所述第二泵筒内径大于所述第一泵筒内径，所述第二泵筒远离所述第一泵筒的一端连接有固定阀；所述第一泵筒和所述第二泵筒内腔分别嵌套有能沿轴向滑动的第一活塞和第二活塞，所述第一活塞和
所述第二活塞轴向贯通且相互固定连接；
所述第二活塞与所述固定阀间隔设置，且所述第二活塞、所述固定阀及所述第二泵筒间构成一储油腔；
所述提升短节另一端的内部固定连接有上游动凡尔罩和一阀座，所述阀座位于所述上游动凡尔罩及所述第一活塞之间；
一抽油杆贯穿所述提升短节、所述第一活塞及第二活塞，所述第一活塞和所述第二活塞分别随所述抽油杆的升降而在所述第一泵筒和第二泵筒内上下滑动，且所述抽油杆的底端连接有下游动阀，所述下游动阀能与所述大活塞底端相抵接或相分离，所述抽油杆上还活动套接有能与所述阀座配合启闭的上游动阀。
在优选的实施方式中，所述提升短节包括相互密封连接的压紧接头和外密封卡座总成，所述第一泵筒通过一密封轴头及嵌套于所述密封轴头外周壁的卡簧与所述外密封卡座总成相连接。
在优选的实施方式中，所述外密封卡座总成内部设有一阀座短接，所述阀座短接的两端部分别连接所述阀座及所述密封轴头，所述密封轴头、所述阀座短接的中部构成轴向贯通的通道，所述第一活塞能沿所述通道上下滑动。
在优选的实施方式中，所述阀座短接与所述外密封卡座总成间设有一密封套，所述密封套与所述阀座短接间沿轴向依次设有承压环、密封环和固定环，所述承压环位于靠近所述阀座一侧。
在优选的实施方式中，所述密封轴头外周壁连接有金属密封环，所述金属密封环密封嵌卡于所述外密封卡座总成内周壁。
在优选的实施方式中，所述第二泵筒与所述第一泵筒相连接的一端的周壁上设有多个平衡孔。
在优选的实施方式中，所述第二泵筒通过一固定阀短接与所述固定阀相连接。
本发明的双重减载防气抽油泵与现有技术相比，具有以下特点及优点：
1、本发明的双重减载防气抽油泵，由于大活塞(第二活塞)及小活塞(第一活塞)的组合设置，保证了该抽油泵的排量为大活塞单次冲程的排量，且相较于现有技术中只采用单一大活塞的抽油泵而言，抽油泵的负载明显降低。
2、本发明的双重减载防气抽油泵，上游动阀活动套接于抽油杆上，在抽油泵上、下冲程转换的过程中，抽油泵上方油管内的原油压力施加在上游动阀上，进而通过阀座作用到提升短节上，从而大大降低了上、下冲程转换时对抽油杆的冲击载荷，进而降低
了抽油杆的断脱概率，降低了抽油泵的日常维护成本。
3、本发明的双重减载防气抽油泵，于抽油杆的下端设有能机械启闭大活塞的下游动阀，进而在下冲程时，保证了大活塞能够迅速打开，消除了活塞内气体压力对下游动阀开启或关闭的影响，实现了防气锁的功能。
图1为本发明双重减载防气抽油泵的组装图。
附图标号说明：
1-压紧接头，2-上游动凡尔罩，3-上游动阀，4-阀座，5-外密封卡座总成；
6-阀座短接，7-承压环，8-密封套，9-密封环，10-固定环，11-密封轴头；
12-金属密封环，13-卡簧，14-小活塞(第一活塞)，15-小泵筒(第一泵筒)；
16-大泵筒(第二泵筒)，17-平衡孔，18-大小活塞短接，19-大活塞(第二活塞)；20-固定阀短接，21-固定凡尔罩，22-固定凡尔罩内筋，23-固定凡尔球；
24-固定凡尔座，25-固定凡尔座压帽，26-下游动阀，27-抽油杆，28-储油腔；
29-通道，30-下端面。
为了对本发明的技术特征、目的和效果有更加清楚的理解，现结合附图说明本发明的具体实施方式。
如图1所示，为本发明双重减载防气抽油泵的组装图。其中，该抽油泵具有一提升短节，具体而言，提升短节包括相互密封连接的压紧接头1和外密封卡座总成5，压紧接头1的上端部与油管相连接，外密封卡座总成5的下端部依次连接有小泵筒15和大泵筒16，且大泵筒的内径大于小泵筒的内径，进一步地，大泵筒和小泵筒内腔分别嵌套有能沿轴向移动的大活塞19和小活塞14，两活塞间通过一大小活塞短接18而固定连接，且大活塞和小活塞轴向贯通。
一抽油杆27贯穿该提升短节及两活塞的中部，抽油杆27的下端部固定连接有下游动阀26，该下游动阀26能够抵接并密封大活塞19的下端部，此外，抽油杆27与抽油机其他结构的连接及传动关系为现有技术，容不赘述。
另外，大泵筒16的下端固定连接有一固定阀，且大活塞19与固定阀间的大泵筒16内部构成储油腔28，大泵筒16与固定阀间通过一固定阀短接20相连接，该固定阀
为现有技术，其简要结构如下：所述固定阀包括与固定阀短接20相连接的固定凡尔罩21，固定凡尔罩21内部固定连接有固定凡尔罩内筋22及固定凡尔座24，此外，该固定凡尔罩21内周壁设有一环凸台，固定凡尔座24一端顶抵于该凸台，另一端顶抵于一固定凡尔座压帽25，所述固定阀还设有能与固定凡尔座24配合启闭的固定凡尔球23。该固定阀的作用在于，当两活塞处于上冲程时，储油腔28受负压作用，固定凡尔球23被顶起，抽油泵外部的油液可进入储油腔28。当两活塞处于下冲程时，储油腔28内油液被压缩，固定阀关闭，下游动阀26打开，储油腔28内的油液进入大、小活塞内腔。
较佳的，压紧接头1的内部固定连接有一上游动凡尔罩2和阀座4，且抽油杆27活动套设有能与阀座4配合启闭的上游动阀3。
进一步地，小泵筒15通过一密封轴头11及嵌套于密封轴头11外部的卡簧13与外密封卡座总成5固定连接。同时，外密封卡座总成5内部设有一连接阀座4和密封轴头11的阀座短接，密封轴头11和阀座短接6的中部构成轴向贯通的通道29，小活塞14能沿所述通道29滑动。当两活塞处于上冲程时，下游动阀26封闭大活塞19，小活塞14沿通道29上移，此时，在两活塞内腔油液压力的作用下，上游动阀3被顶起，油液进入压紧接头1上方的油管内并排至地面。
为保证抽油泵稳定性与气密性，阀座短接6与外密封卡座总成5间设有一密封套8，且该密封套8与阀座短接6间沿轴向依次设有承压环7、密封环9以及固定环10，该承压环7位于靠近阀座4一侧。此外，密封轴头11外周壁嵌套有一金属密封环12，该金属密封环12外周壁呈锥面设置，并可密封嵌卡于外密封卡座总成5上设置的一凸台，从而防止外界杂质进入阀座部分，上述为现有技术，容不赘述。
为配合大小活塞在上、下冲程时与外界的压力平衡，大泵筒16的上端部周向设有多个平衡孔17，进而在抽油泵的下冲程时，外界液体可补充至小活塞14与大泵筒16间的环空，在抽油泵的上冲程时，环空内的液体可通过平衡孔17排出。
以下进一步结合附图说明本发明抽油泵的工作原理及其优点：
如图1所示，本发明的抽油泵在上冲程时，抽油杆27带动下游动阀26关闭大活塞19，并驱动大、小活塞上行，此时，在两活塞内腔油液压力的作用下，上游动阀3被顶起，油液经过上游动凡尔罩2而进入压紧接头1所连接的油管内，并排送至地面。由于本发明的抽油泵设计有相互连接的大、小活塞，因而可保证泵的排量为大活塞单次冲程的排量，同时，压紧接头1相连接的油管内径与小活塞的内径一致，由于抽油机驴头悬点载荷主要来源于小活塞上端油管内的液柱压力，考虑到小活塞与大泵筒间环空的
下端面30会受到外界油液的压力，但该压力远远小于上方油管内的液柱压力，因此，在忽略该压力的情况下，本发明的抽油泵与现有技术中相同泵径(即本发明大泵筒泵径)的普通泵比较，载荷明显降低。其中，定义大活塞横截面积为S1，小活塞横截面积为S2，则现有技术中抽油泵的荷载：
W1＝(F1-F2)×S1，F1：泵挂深度压力，即井口与抽油泵的高度差所对应的油管内油液压力；F2：沉没压力，即井下液面与抽油泵的高度差所对应的油管内油液压力；
本发明抽油泵的荷载W2＝(F1-F2)×S2，因此，本发明与现有技术相比，其减载力即为W1-W2，进而实现了本发明的一重减载功能。
当抽油泵上、下冲程转换时，受压紧接头1上方油管内油液的重力作用，上游动阀3封闭阀座4，阀座4承载上方油液的压力，这样，即可较大地缓解上、下冲程转换时油管内油液对抽油杆27的冲击载荷，从而降低了抽油杆27断脱的概率以及抽油泵的日常维护及维修成本，实现了本发明的另一重减载功能。
在本发明抽油泵进入下冲程时，大活塞压缩储油腔28内的油液，固定阀关闭，同时，在抽油泵外加载荷的作用下，抽油杆27驱动下游动阀26以较快速度下行，从而打开大活塞，储油腔28内的油液通过大、小活塞内腔进入通道29。当大活塞到达下冲程极限位置时(抽油杆的上、下行程决定了活塞的上、下冲程极限位置)，下游动阀封闭大活塞，完成一个抽油周期。其中，抽油杆27机械驱动下游动阀26开启的方式保证了大活塞能够迅速打开，消除了现有技术中活塞内气体压力对下游动阀开启或关闭的影响，实现了防气锁的功能。
综上所述，本发明的双重减载防气抽油泵，由于大活塞及小活塞的组合设置，在保证了该抽油泵的排量为大活塞单次冲程排量的同时，且相较于现有技术中只采用单一大活塞的抽油泵而言，抽油泵上端油管内的油液压力降低，抽油泵的负载降低。
此外，本发明的双重减载防气抽油泵，上游动阀活动套接于抽油杆上，在抽油泵上、下冲程转换时，抽油泵上方油管内的原油压力施加在上游动阀上，进而通过阀座作用到提升短节上，从而大大降低了上、下冲程转换时对抽油杆的冲击载荷，降低了抽油杆的断脱概率及抽油泵的日常维护成本。
同时，本发明的双重减载防气抽油泵，于抽油杆的下端设有能机械启闭大活塞的下游动阀，进而在下冲程时，保证了大活塞能够迅速打开，消除了活塞内气体压力对下游动阀开启或关闭的影响，实现了防气锁的功能。
以上所述仅为本发明示意性的具体实施方式，并非用以限制本发明的范围。任何
本领域的技术人员，在不脱离本发明的原则和构思的前提下所作的等同变化与修改，均应属于本发明的保护范围。
Claims (7)
- 一种双重减载防气抽油泵，其特征在于，所述双重减载防气抽油泵设有一提升短节，所述提升短节一端依次连接有第一泵筒和第二泵筒，所述第二泵筒内径大于所述第一泵筒内径，所述第二泵筒远离所述第一泵筒的一端连接有固定阀；所述第一泵筒和所述第二泵筒内腔分别嵌套有能沿轴向滑动的第一活塞和第二活塞，所述第一活塞和所述第二活塞轴向贯通且相互固定连接；所述第二活塞与所述固定阀间隔设置，且所述第二活塞、所述固定阀及所述第二泵筒间构成一储油腔；所述提升短节另一端的内部固定连接有上游动凡尔罩和一阀座，所述阀座位于所述上游动凡尔罩及所述第一活塞之间；一抽油杆贯穿所述提升短节、所述第一活塞及第二活塞，所述第一活塞和所述第二活塞分别随所述抽油杆的升降而在所述第一泵筒和第二泵筒内上下滑动，且所述抽油杆的底端连接有下游动阀，所述下游动阀能与所述大活塞底端相抵接或相分离，所述抽油杆上还活动套接有能与所述阀座配合启闭的上游动阀。
- 如权利要求1所述的双重减载防气抽油泵，其特征在于，所述提升短节包括相互密封连接的压紧接头和外密封卡座总成，所述第一泵筒通过一密封轴头及嵌套于所述密封轴头外周壁的卡簧与所述外密封卡座总成相连接。
- 如权利要求2所述的双重减载防气抽油泵，其特征在于，所述外密封卡座总成内部设有一阀座短接，所述阀座短接的两端部分别连接所述阀座及所述密封轴头，所述密封轴头、所述阀座短接的中部构成轴向贯通的通道，所述第一活塞能沿所述通道上下滑动。
- 如权利要求3所述的双重减载防气抽油泵，其特征在于，所述阀座短接与所述外密封卡座总成间设有一密封套，所述密封套与所述阀座短接间沿轴向依次设有承压环、密封环和固定环，所述承压环位于靠近所述阀座一侧。
- 如权利要求2所述的双重减载防气抽油泵，其特征在于，所述密封轴头外周壁连接有金属密封环，所述金属密封环密封嵌卡于所述外密封卡座总成内周壁。
- 如权利要求1所述的双重减载防气抽油泵，其特征在于，所述第二泵筒与所述第一泵筒相连接的一端的周壁上设有多个平衡孔。
- 如权利要求1所述的双重减载防气抽油泵，其特征在于，所述第二泵筒通过一固定阀短接与所述固定阀相连接。
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