CN203248132U - Crank type reversing buffer device for bumping unit - Google Patents
Crank type reversing buffer device for bumping unit Download PDFInfo
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- CN203248132U CN203248132U CN 201320278585 CN201320278585U CN203248132U CN 203248132 U CN203248132 U CN 203248132U CN 201320278585 CN201320278585 CN 201320278585 CN 201320278585 U CN201320278585 U CN 201320278585U CN 203248132 U CN203248132 U CN 203248132U
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Abstract
The utility model provides a crank type reversing buffer device for a bumping unit. The crank type reversing buffer device for the bumping unit comprises upper bumping blocks, lower bumping blocks, sliding rails which are used for enabling the upper bumping blocks and the lower bumping blocks to slide, fixed pulleys and crank buffer pieces, wherein the upper bumping blocks and the fixed pulleys are fixed at the upper portion of a truss of the bumping unit, the crank buffer pieces and the lower bumping blocks are arranged at the lower portion of the truss of the bumping unit, the upper bumping blocks are connected with the crank buffer pieces through steel wire ropes or first pull rods, and the lower bumping blocks are connected to an upper portion pull rod device through steel wire ropes or pull rods. According to the crank type reversing buffer device for the bumping unit, buffer energy can be converted into reversing starting energy, not like a variable-frequency type reversing buffer device, reactance is not needed, buffer energy is not converted into heat which is consumed for nothing, additional energy is used for increasing starting torque when the crank type reversing buffer device is started, green conversion is achieved, energy is saved, emission is reduced, and energy consumption cost is reduced. The crank type reversing buffer device for the bumping unit is mechanical overall, simple in structure, small in the number of parts, high in reliability, free of parts which are machined in a high-precision mode, and low in manufacturing cost.
Description
Technical field
The utility model relates to a kind of buffer, relates in particular to a kind of crank-type reversing buffering mechanism for oil pumper.
Background technology
Vertical oil-pumping machine has a lot of advantages with respect to traditional beam pumping unit, as improving oil recovery efficiency, increases oil production rate; Reduce wear, improve sucker rod and oil well pump life-span; Discharge capacity is stable, and dynamic loading is little, and accident is few; Smooth running, fatigue stress is low, and stress-number of cycles is few etc.Adopt long stroke oil pumping mode, the actual loss of plunger stroke of oil pump plunger piston less can be improved discharge coefficient and the coefficient of fullness of oil well pump, improves oil recovery efficiency, increases oil production rate, the reduction cost for oil production.But also there are some short slabs in vertical oil-pumping machine, and the problem of wherein commutation buffering is exactly an outstanding problem, also is one of major obstacle that runs in the extension process.
Vertical oil pumper is at the switch operation of top dead centre, lower dead center, need sucker rod, counterweight to move fully in the opposite direction, because the weight of sucker rod, counterweight is large, inertia is very large, and lot of energy is all wanted in stopping and starting of commutation, can cause the very large impact of transmission mechanism, various part lifes are reduced, motor constantly repeats generating, starting state always, and electrical network is constantly impacted, and the inefficiency of equipment, serious wear, power consumption are large.Present solution mainly contains two kinds, but the situation after reality is used is unsatisfactory.
As shown in Figure 1, the chain type vertical oil-pumping machine is to use now maximum vertical oil-pumping machines, and reversing mode is as shown below, and in fact the head of crank shaft is serving as a specific links of path chain, and its circular shaft part inserts apparatus for suspension, can rotate in apparatus for suspension.Apparatus for suspension can be along the guide rail transverse shifting in coming and going frame.Crank shaft is made shuttling movement with path chain, when the circular arc portion that moves to path chain when crank shaft is sprocket part, it continues to drive round frame and moves upward, drive simultaneously apparatus for suspension along the guide rail transverse shifting, arriving the round frame change of peak after crank drive direction moves downward, drive simultaneously apparatus for suspension and continue transverse shifting along guide rail, come and go the again down stroke of relative static realization oil pumper of frame and apparatus for suspension behind the vertical component of chain until crank throw runs to.
The frequency conversion reversing motor adopts the operation of inverter control motor, and the rotating excitation field of different frequency is provided by frequency converter during commutation, and accurately direction and the speed of controlled motion realize buffering and the commutation of oil pumper.
The main shortcoming of existing two kinds of technology is as follows:
Chain type oil pump, commutation occurs in the scope of upper sprocket wheel, lower sprocket, and upper sprocket wheel, lower sprocket are to be arranged vertically, and the buffer distance of the process of commutation is the radius of sprocket wheel, because sprocket wheel can not be done too greatly, causes buffer distance too little, impacts large; Chain is Flexible Transmission, mechanism's volume is large, lubricated difficulty, wear block, maintenance and replacing difficulty, after the wearing and tearing, can produce vibration and noise, and make the variation of chain generation length, the degree of tightness of chain and lower sprocket is engaged in constantly add during the crack changes, buffering effect is further reduced, the mode of occupation of complete machine is worsened, and very large potential safety hazard is arranged.Because these shortcomings, once added in history air bag and assist buffering, but every fault rate over thousand times, make that air bag is very fast to be abandoned.
The frequency conversion reversing motor; in theory; the frequency conversion reversing motor can be realized best commutation action of giving; but the problem of this mode bothers more; adopt electric means to slow down by force; and frequent starting; electrical control system is complicated; be difficult to adapt to adverse circumstances; the maintenance and repair technical requirements is high, and the buffering energy is that the heating by electrical equipment consumes the heat radiation difficulty; life-span is very short; often cause stopping accident, and the use of big-power transducer, electrical network is produced very large high frequency pollute; affect the running of other equipment, these shortcomings descend the occupation rate of market of this oil pumper year by year.
With this, the problems referred to above are the problems that should pay attention to and solve in the design and production use procedure of oil pumper.
Summary of the invention
The purpose of this utility model provides a kind of crank-type reversing buffering mechanism for oil pumper and has solved oil pumper in use, counterweight is at top dead centre, down near the reversing impact problem of the position point, the energy of damping of shocks is passed through the accumulation of energy of crank bolster, discharge during commutation, realized the recycling of impact energy, turn waste into wealth, make in whole commutation process, the power output substantially constant of motor makes transmission system and dynamical system smooth working, impacts little.
Technical solution of the present utility model is:
A kind of crank-type reversing buffering mechanism for oil pumper, comprise collision block, lower collision block, be used for the slideway that upper collision block and lower collision block slide, fixed pulley and crank bolster, described upper collision block and fixed pulley are located at oil pumper truss top, described crank bolster and lower collision block are located at the bottom of oil pumper truss, described upper collision block is by wire rope one connecting crank bolster, described upper collision block also is connected with an end of wire rope two, the other end of described wire rope two is walked around described fixed pulley and is connected lower collision block, described crank bolster comprises that cross swings joint, galianconism, axis of rotation, long-armed and the buffering counterweight, described cross swings the end that joint is located at galianconism, a described long-armed end connects galianconism, the described long-armed other end connects the buffering counterweight, and described galianconism and long-armed junction are provided with axis of rotation.
Preferably, be provided with counterweight between described upper collision block and lower collision block, described counterweight is by the wire rope connecting with pumping rod, described wire rope has been walked around head sheave, the both sides of described counterweight respectively are provided with a pair of upper collision block, and every pair of described upper collision block is connected by connector, and an end of described wire rope one connects described connector, the other end of described wire rope one connects described crank bolster, and the both sides of described counterweight respectively are provided with a pair of lower collision block.
Preferably, described galianconism and long-armed formation " V " type, described axis of rotation is located on the oil pumper truss.
Preferably, the centre bore of described cross swing joint passes the wire rope one for the connecting crank bolster, and the two ends that described cross swings joint are installed in the galianconism by roller bearing.
Preferably, the two ends of described buffering counterweight are provided with adjustable collision block.
Preferably, described buffering counterweight is provided with and regulates the buffering balancing weight.
Preferably, described crank bolster also comprises for the flexible limit piece that limits crank bolster pendulum angle.
Preferably, described counterweight is provided with inserts, and described inserting is located at respectively the contact surface of counterweight and upper collision block, counterweight and lower collision block, and described upper collision block and lower collision block are equipped with and the described adaptive chamfered groove of inserting.
Preferably, described inserting made by high-abrasive material.
Preferably, the end of described wire rope one, wire rope two is provided with for the chuck of adjusting rope capacity.
Preferably, described slideway is located on the oil pumper truss, is provided with in the described slideway be used to the roller that reduces upper collision block and lower collision block sliding friction.
Preferably, the both sides, middle part of described wire rope one are provided with for keeping wire rope one straight-line support roller.
A kind of crank-type reversing buffering mechanism for oil pumper of the utility model, be used for to solve the commutation buffer problem of vertical oil-pumping machine and design, by adopting a crank bolster to connect sucker rod and the counterweight of vertical oil-pumping machine, top dead centre at oil pumper, before bottom dead center, inertia to sucker rod and counterweight carries out buffer deceleration, utilize cleverly the structure of crank bolster, make the mild increase of oil pumper decelerative force, utilize simultaneously the structure of crank bolster to the accumulation of energy of buffering counterweight, after commutation, discharge the potential energy of savings, make commutation process steady, reduce power to the impact of driving means for oil pumping unit, improve the life-span, make electrical network steady, minimizing in steering procedure to the impact of main motor, can be equipped with less motor and reduction box, reducing the oil pumper manufacturing cost is purpose, realizes that oil extraction in oil field is energy-saving and cost-reducing.
The crank bolster that this kind is used for the crank-type reversing buffering mechanism of oil pumper comprises that cross swings joint, galianconism, axis of rotation, long-armed and buffering counterweight, the crank bolster is installed on the oil pumper truss by axis of rotation, the crank bolster can be done oscillating motion as the center, the border, two ends that swings at the crank bolster arranges the flexible limit piece, play the security insurance effect, can not clash into during normal operation, if bump, the buffering balancing weight is regulated in increase and decrease, makes the equipment normal operation.
The centre bore that the cross of crank bolster swings joint penetrates wire rope one, and cross swings joint two ends cylinder and is installed in by roller bearing in the front fork of galianconism end, can be when the crank bolster swings rotational angle, the change in location of adaptation wire rope one.Retainer clip is installed in the end that swings collision block under joint, wire rope two connections at the cross that wire rope one passes, and guiding mechanism is set simultaneously, is used for adjusting when rope capacity changes.
A kind of crank-type reversing buffering mechanism for oil pumper of the utility model compares at the commutation buffer gear with the chain of main flow, frequency-changing vertical oil pumper, has following advantage:
1. this kind is used for the crank-type reversing buffering mechanism of oil pumper, all is mechanical device, and simple in structure, component are few, and reliability is high, does not have the high accuracy process component, and cost of manufacture is low;
2. the cushion effect adjustment utilizes the weight of crank bolster to increase and decrease to realize, adjusting operation carries out on ground, and safe ready can adapt to dissimilar oil wells to the different requirements of commutation buffering course;
3. the operating distance of the action of buffering is only relevant with the forearm change between the curve buffering with the distance of up and down slideway, and buffer distance is more much bigger than chain type, and buffering course is more steady;
4. buffer distance can be by at up and down slideway increase and decrease cushion block and adjust the steel cable clip position and carry out, and is simple and safe, can cooperate the demand of different cushioning effect distances;
5. swing to finish by the crank bolster owing to cushion effect, the cushion effect curve is a round and smooth sine curve, size is relevant with the pendulum angle of crank bolster with the weight of crank counterweight, during buffering by 0 to maximum, and commutation process is just in time opposite, consistent with the application of force process of oil pumper demand, realize mild seamless transitions;
6. galianconism and long-armed design utilize lever principle cleverly, make less crank bolster change into very large cushion effect, and enlargement of force is long-armed and the galianconism Length Ratio, have reduced the volume and weight of device;
7. can realize to cushion energy and be converted into commutation and start energy, not need as frequency conversion type, to utilize reactance, will cushion energy and be converted into heat and consume in vain, use again additional energy to strengthen staring torque during startup, realized green conversion, energy-saving and emission-reduction have reduced energy consumption cost;
8. because the conversion process of above-mentioned energy makes oil pumper when commutation, it is minimum that the motor Input torque fluctuation reduces to, and greatly reduces the peak-peak moment of torsion, makes the power of motor and reduction box can design littlely, reduced the cost of processing and manufacturing;
9. after the fluctuation of load of motor and transmission system reduced, the motion of each drive disk assembly was more steady, had reduced the wearing and tearing of equipment, had alleviated the maintaining cost.
Description of drawings
Fig. 1 is the structural representation of chain type vertical oil-pumping machine in the prior art;
Fig. 2 is the structural representation of the utility model embodiment;
Fig. 3 is the position structure schematic diagram of crank bolster among the utility model embodiment, upper collision block, lower collision block and fixed pulley;
Fig. 4 is the structural representation of crank bolster among the utility model embodiment;
Fig. 5 is another structural representation of crank bolster among the utility model embodiment;
Fig. 6 is the location diagram that cross swings joint and galianconism, roller bearing among the utility model embodiment;
Fig. 7 is counterweight among the utility model embodiment, the location diagram with upper collision block inserted;
Fig. 8 is the structural representation when counterweight upwards arrives the buffer area starting point among the utility model embodiment;
Fig. 9 is the structural representation of crank bolster and upper collision block when counterweight upwards arrives the buffer area starting point among the utility model embodiment, lower collision block;
Figure 10 is the structural representation of crank bolster and upper collision block when counterweight arrives top dead centre among the utility model embodiment, lower collision block;
Figure 11 is the explanation schematic diagram of long-armed pivot angle among the utility model embodiment;
Figure 12 is the change curve schematic diagram that lineoutofservice signal pull arrives top dead centre gradually among the utility model embodiment in counterweight;
Figure 13 is the structural representation of counterweight when top dead centre commutates among the utility model embodiment;
Figure 14 is the structural representation of counterweight crank bolster and upper collision block, lower collision block when top dead centre commutates among the utility model embodiment;
Figure 15 is the structural representation when counterweight arrives the buffer area starting point downwards among the utility model embodiment;
Figure 16 is the structural representation of buffering counterweight crank bolster and upper collision block, lower collision block when arriving the buffer area starting point downwards among the utility model embodiment;
Figure 17 is the structural representation of counterweight crank bolster and upper collision block, lower collision block when lower dead center commutates among the utility model embodiment;
Wherein: 1-crank bolster, the upper collision block of 2-, collision block under the 3-, 4-fixed pulley, 5-wire rope one, 6-wire rope two, 7-connector, 8-counterweight, the 9-sucker rod, 10-inserts, and the 11-cross swings joint, the 12-galianconism, the 13-axis of rotation, 14-is long-armed, 15-cushions counterweight, 16-roller bearing, the adjustable collision block of 17-, 18-regulates buffering balancing weight, 19-flexible limit piece, 20-head sheave.
The specific embodiment
Describe preferred embodiment of the present utility model in detail below in conjunction with accompanying drawing.
As shown in Figures 2 and 3, present embodiment provides a kind of crank-type reversing buffering mechanism for oil pumper, comprise collision block 2, lower collision block 3, be used for the slideway that upper collision block 2 and lower collision block 3 slide, fixed pulley 4 and crank bolster 1, described upper collision block 2 and fixed pulley 4 are located at oil pumper truss top, described crank bolster 1 and lower collision block 3 are located at the bottom of oil pumper truss, described upper collision block 2 is by wire rope one 5 connecting crank bolsters 1, described upper collision block 2 also is connected with an end of wire rope 26, the other end of described wire rope 26 is walked around described fixed pulley 4 and is connected lower collision block 3, described upper collision block 2 and 3 of lower collision blocks are provided with counterweight 8, described counterweight 8 is by wire rope connecting with pumping rod 9, described wire rope has been walked around head sheave 20, the both sides of described counterweight 8 respectively are provided with a pair of upper collision block 2, every pair of described upper collision block 2 is connected by connector 7, one end of described wire rope 1 connects described connector 7, the other end of described wire rope 1 connects described crank bolster 1, and the both sides of described counterweight 8 respectively are provided with a pair of lower collision block 3.The end of described wire rope 1, wire rope 26 is provided with for the chuck of adjusting rope capacity.Described slideway is located on the oil pumper truss, is provided with in the described slideway be used to the roller that reduces upper collision block 2 and lower collision block 3 sliding frictions.
As shown in Figure 4 and Figure 5, described crank bolster 1 comprises that cross swings joint 11, galianconism 12, axis of rotation 13, long-armed 14 and buffering counterweight 15, described cross swings the end that joint 11 is located at galianconism 12, an end of described long-armed 14 connects galianconism 12, described long-armed 14 the other end connects buffering counterweight 15, described galianconism 12 and long-armed 14 junction are provided with axis of rotation 13, and described axis of rotation 13 is located at the oil pumper truss.Described crank bolster 1 also comprises for the flexible limit piece 19 that limits crank bolster 1 pendulum angle.
Described galianconism 12 and long-armed 14 forms on " V " type.The two ends of described buffering counterweight 15 are provided with adjustable collision block 17 described buffering counterweights 15 and are provided with adjusting buffering balancing weight 18.As shown in Figure 6, the centre bore of described cross swing joint 11 passes the wire rope 1 for connecting crank bolster 1, and the two ends that described cross swings joint 11 are installed in the galianconism 12 by roller bearing 16.
As shown in Figure 7, described counterweight 8 is provided with inserts 10, described 10 contact surfaces of being located at respectively counterweight 8 and upper collision block 2, counterweight 8 and lower collision block 3 of inserting, and described upper collision block 2 and lower collision block 3 are equipped with and the described 10 adaptive chamfered grooves of inserting.Described inserting 10 made by high-abrasive material.Insert 10 counterweight 8 setting, insert 10 and the contact surface of chamfered groove form a guiding angle, make contact process more steady because the contact portion operating frequency is high, insert 10 so adopt high-abrasive material to make, after wearing and tearing are excessive, change, reduce maintenance cost.
A kind of crank-type reversing buffering mechanism for oil pumper of present embodiment, be used for to solve the commutation buffer problem of vertical oil-pumping machine and design, by adopting a crank bolster 1 to connect sucker rod 9 and the counterweight 8 of vertical oil-pumping machine, top dead centre at oil pumper, before bottom dead center, inertia to sucker rod 9 and counterweight 8 carries out buffer deceleration, utilize cleverly the structure of crank bolster 1, make the mild increase of oil pumper decelerative force, utilize simultaneously the structure of crank bolster 1 to 15 accumulation of energys of buffering counterweight, after commutation, discharge the potential energy of savings, make commutation process steady, reduce power to the impact of driving means for oil pumping unit, improve the life-span, make electrical network steady, minimizing in steering procedure to the impact of main motor, can be equipped with less motor and reduction box, reducing the oil pumper manufacturing cost is purpose, realizes that oil extraction in oil field is energy-saving and cost-reducing.
This kind is used for the crank-type reversing buffering mechanism of oil pumper, slideway is installed on the oil pumper truss, for in the slideway that reduces to rub roller being housed, upper collision block 2 and lower collision block 3 can move up and down along slideway, and upper collision block 2 vertical directions motion can spur crank bolster 1 and swing around axis of rotation 13.Lower collision block 3 is connected to the other end of upper collision block 2 by wire rope 26, middlely turns to by a fixed pulley 4, and during instantly collision block 3 vertical directions motion, collision block 2 in the pulling, so also can make 1 swing of crank bolster.
The crank bolster 1 that this kind is used for the crank-type reversing buffering mechanism of oil pumper comprises that cross swings joint 11, galianconism 12, axis of rotation 13, long-armed 14 and buffering counterweight 15, crank bolster 1 is installed on the oil pumper truss by axis of rotation 13, crank bolster 1 can be done oscillating motion as the center, the border, two ends that swings at crank bolster 1 arranges flexible limit piece 19, play the security insurance effect, can not clash into during normal operation, if bump, buffering balancing weight 18 is regulated in increase and decrease, makes the equipment normal operation.
The centre bore that the cross of crank bolster 1 swings joint 11 penetrates wire rope 1, cross swings joint 11 two ends cylinders and is installed in the front fork of galianconism 12 ends by roller bearing 16, can be when crank bolster 1 swings rotational angle, adapt to the change in location of wire rope 1.Retainer clip is installed in the end that swings collision block 3 under joint 11, wire rope 26 connections at the cross that wire rope 1 passes, and guiding mechanism is set simultaneously, is used for adjusting when rope capacity changes.
This kind is used for the crank-type reversing buffering mechanism of oil pumper, because the wire rope pattern is adopted in the coupling part, when collision block contacts, only stressed in the load of wire rope own, then from 0 weight, progressively draw again crank bolster 1 principle, wire rope itself also plays cushioning effect, so avoided the noise that causes because of bump in when contact.
The course of work is described as follows:
A working cycles of vertical oil-pumping machine, can divide according to the stop place, sucker rod 9 lower dead center (counterweight 8 top dead centres) → sucker rod 9 ascending motions (counterweight 8 descending motions) → sucker rod 9 top dead centres (counterweight 8 lower dead center) → sucker rod 9 descending motions (counterweight 8 ascending motions) → sucker rod 9 lower dead center (counterweight 8 top dead centres), in the most of stroke that rises and descend, sucker rod 9 and counterweight 8 are in the uniform speed motion state, but at sucker rod 9 lower dead center (counterweight 8 top dead centres), near sucker rod 9 top dead centres (counterweight 8 lower dead center), need an acceleration, the buffering course that slows down, this process is steady, the work that oil pumper ability is stable, otherwise body and transmission system all can be subject to shock and vibration, cause the damage of component, energy consumption increases.
A kind of crank-type reversing buffering mechanism for oil pumper of present embodiment, solved near the reversing impact problem of oil pumper position sucker rod 9 lower dead center (counterweight 8 top dead centres), sucker rod 9 top dead centres (counterweight 8 lower dead center), the energy of damping of shocks is passed through 1 accumulation of energy of crank bolster, discharge during commutation, realized the recycling of impact energy, turned waste into wealth.In commutation process, the power output basic guarantee of motor is constant, makes transmission system and dynamical system smooth working, impacts little.
As shown in Figure 8, sucker rod 9 and counterweight 8 be in the uniform motion stage of up-down stroke, and polished rod eye and the counterweight 8 moving beam of buffering of all getting along well contacts, and at this moment the crank-type reversing buffering mechanism is not worked.
As shown in Figure 9 and Figure 10, the buffer stage of counterweight 8 when top: buffering counterweight 15 arrives the lower contact surface of the same collision block 2, enter the buffering incipient stage, buffer system begins stressed, enter buffer stage, rising along with counterweight 8, upper collision block 2 is because buffering counterweight 15 is risen by effect simultaneously, galianconism 12 tie points that drive crank bolster 1 by wire rope rise, 1 beginning of crank bolster is done oscillating motion along axis of rotation 13, the 15 stressed increasings along with crank bolster 1 pendulum angle of buffering counterweight increase gradually, until arrive the top dead centre of buffering counterweight 15, and 15 stop motions of buffering counterweight, crank bolster 1 also swings to the design maximum angle, oil pumper arrives on-position, and transmission mechanism begins switch operation.
Such as Figure 11 and shown in Figure 12, according to mechanical knowledge, a near sinusoidal functional relation is arranged: F=KSin θ between the stressed pendulum angle with crank bolster 1 of buffer rope, wherein, F is the steel cable pulling force, and θ is pivot angle, and K is with buffering counterweight 15, galianconism 12, long-armed 14 relevant proportionality constants.The application of force process of whole buffering is carrying out gently by sine relation, wire rope stressed since 0, increase gradually, be KSin θ max to the maximum, the potential energy that at this moment cushions counterweight 15 storages reaches maximum, is M*G*L*Sin θ max*Tg θ max, wherein, M is buffering counterweight 15 quality, and G is acceleration of gravity, and L is long-armed 14 length.
Such as Figure 13 and shown in Figure 14, the startup stage of the commutation of counterweight 8 when top: counterweight 8 begins counter motion from top dead centre, whole sucker rod 9, counterweight 8, head sheave 20 inertia systems are from static setting in motion, the power source that starts is divided into two-way, it at first is motor force, and another road, the potential energy of the crank bolster 1 of putting aside when being buffer release, total amount is M*G*L*Sin θ max*Tg θ max, and the stack of two-way power makes inertia system begin counter motion, along with the increase of movement velocity, θ reducing gradually, the driving force that crank bolster 1 provides reduces gradually according to function KSin θ, until to 0, startup is finished, withdraw from the driving process, at this moment remaining motor force only, system enters the uniform motion stage, and the commutation start-up course finishes.
Such as Figure 15 and shown in Figure 16, the buffer stage of counterweight 8 when the bottom: counterweight 8 arrives the bottom, and the upper surface contact with lower collision block 3 enters the bottom buffering incipient stage, and buffer system begins stressed; Along with the continuation of counterweight 8 is descending, promoting lower collision block 3 moves downward, drive upper collision block 2 and move upward by wire rope 26, fixed pulley 4, upper collision block 2 drives 1 beginning of crank bolster by wire rope 26 and does oscillating motion along axis of rotation 13, the 15 stressed increasings along with crank bolster 1 pendulum angle of buffering counterweight increase gradually, until arrive the lower dead center of buffering counterweight 15, buffering counterweight 15 stops, and crank bolster 1 also swings to the design maximum angle.
As shown in figure 17, counterweight 8 is near lower dead center the time, the motion of crank bolster 1 with stressing conditions the buffer stage situation during with above-mentioned counterweight 8 top similar.
The startup stage of the commutation of counterweight 8 when the bottom: counterweight 8 begins counter motion from lower dead center, whole sucker rod 9, counterweight 8, head sheave 20 inertia systems are from static setting in motion, the power source that starts is divided into two-way, it at first is motor force, another road discharges the potential energy of crank bolster 1, the stack of two-way power makes inertia system begin counter motion, carrying out along with motion, the angle theta of crank bolster 1 and vertical direction reducing gradually, the driving force that crank bolster 1 provides reduces gradually according to function KSin θ, until to 0, startup is finished, and withdraws from the driving process, at this moment remaining motor force only, oil pumper enters the uniform motion stage, and the commutation start-up course finishes.
A kind of crank-type reversing buffering mechanism for oil pumper of present embodiment compares at the commutation buffer gear with the chain of main flow, frequency-changing vertical oil pumper, has following advantage:
1. this kind is used for the crank-type reversing buffering mechanism of oil pumper, all is mechanical device, and simple in structure, component are few, and reliability is high, does not have the high accuracy process component, and cost of manufacture is low;
2. the cushion effect adjustment utilizes the weight of crank bolster to increase and decrease to realize, adjusting operation carries out on ground, and safe ready can adapt to dissimilar oil wells to the different requirements of commutation buffering course;
3. the operating distance of the action of buffering is only relevant with the little arm lengths apart from the crank-type buffer of up and down slideway, and buffer distance is more much bigger than chain type, and buffering course is more steady;
4. buffer distance can carry out with adjustment retainer clip position by increase and decrease cushion block at up and down slideway, and is simple and safe, can cooperate the demand of different cushioning effect distances.
5. swing to finish by the crank bolster owing to cushion effect, the cushion effect curve is a round and smooth sine curve, size is relevant with the pendulum angle of crank bolster with the locus that moving beam arrives, during buffering by 0 to maximum, and commutation process is just in time opposite, consistent with the application of force process of oil pumper demand, realize mild seamless transitions;
6. galianconism and long-armed design utilize lever principle cleverly, make less crank bolster change into very large cushion effect, and enlargement of force is long-armed and the galianconism Length Ratio, have reduced the volume and weight of device;
7. can realize to cushion energy and be converted into commutation and start energy, not need as frequency conversion type, to utilize reactance, will cushion energy and be converted into heat and consume in vain, use again additional energy to strengthen staring torque during startup, realized green conversion, energy-saving and emission-reduction have reduced energy consumption cost;
8. because the conversion process of above-mentioned energy makes oil pumper when commutation, it is minimum that the motor Input torque fluctuation reduces to, and greatly reduces the peak-peak moment of torsion, makes the power of motor and reduction box can design littlely, reduced the cost of processing and manufacturing;
9. after the fluctuation of load of motor and transmission system reduced, the motion of each drive disk assembly was more steady, had reduced the wearing and tearing of equipment, had alleviated the maintaining cost.
Claims (11)
1. crank-type reversing buffering mechanism that is used for oil pumper, it is characterized in that: comprise collision block (2), lower collision block (3), be used for the slideway that upper collision block (2) and lower collision block (3) slide, fixed pulley (4) and crank bolster (1), described upper collision block (2) and fixed pulley (4) are located at oil pumper truss top, described crank bolster (1) and lower collision block (3) are located at the bottom of oil pumper truss, described upper collision block (2) is by wire rope one (5) connecting crank bolster (1), described lower collision block (2) also is connected with an end of wire rope two (6), the other end of described wire rope two (6) is walked around described fixed pulley (4) and is connected lower collision block (3), described crank bolster (1) comprises that cross swings joint (11), galianconism (12), axis of rotation (13), long-armed (14) and buffering counterweight (15), described cross swings the end that joint (11) is located at galianconism (12), one end of described long-armed (14) connects galianconism (12), the other end of described long-armed (14) connects buffering counterweight (15), and the junction of described galianconism (12) and long-armed (14) is provided with axis of rotation (13).
2. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1, it is characterized in that: be provided with counterweight (8) between described upper collision block (2) and lower collision block (3), described counterweight (8) is by wire rope connecting with pumping rod (9), described wire rope has been walked around head sheave (20), the both sides of described counterweight (8) respectively are provided with a pair of upper collision block (2), every pair of described upper collision block (2) is connected by connector (7), one end of described wire rope one (5) connects described connector (7), the other end of described wire rope one (5) connects described crank bolster (1), and the both sides of described counterweight (8) respectively are provided with a pair of lower collision block (3).
3. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1 is characterized in that: described galianconism (12) and long-armed (14) form " V " type, and described axis of rotation (13) is located on the oil pumper truss.
4. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1, it is characterized in that: the centre bore of described cross swing joint (11) passes the wire rope one (5) for connecting crank bolster (1), and the two ends that described cross swings joint (11) are installed in the galianconism (12) by roller bearing (16).
5. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1, it is characterized in that: the two ends of described buffering counterweight (15) are provided with adjustable collision block (17).
6. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1 is characterized in that: described buffering counterweight (15) is provided with regulates buffering balancing weight (18).
7. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 1 is characterized in that: described crank bolster (1) also comprises for the flexible limit piece (19) that limits crank bolster (1) pendulum angle.
8. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 2, it is characterized in that: described counterweight (8) is provided with insert (10), described inserting (10) is located at respectively the contact surface of counterweight (8) and upper collision block (2), counterweight (8) and lower collision block (3), and described upper collision block (2) and lower collision block (3) are equipped with the chamfered groove adaptive with described inserting (10).
9. the crank-type reversing buffering mechanism for oil pumper as claimed in claim 8, it is characterized in that: described inserting (10) made by high-abrasive material.
10. such as each described crank-type reversing buffering mechanism for oil pumper of claim 1-8, it is characterized in that: the end of described wire rope one (5), wire rope two (6) is provided with for the chuck of adjusting rope capacity.
11. such as each described crank-type reversing buffering mechanism for oil pumper of claim 1-8, it is characterized in that: described slideway is located on the oil pumper truss, is provided with in the described slideway be used to the roller that reduces upper collision block (2) and lower collision block (3) sliding friction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320278585 CN203248132U (en) | 2013-05-21 | 2013-05-21 | Crank type reversing buffer device for bumping unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320278585 CN203248132U (en) | 2013-05-21 | 2013-05-21 | Crank type reversing buffer device for bumping unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203248132U true CN203248132U (en) | 2013-10-23 |
Family
ID=49374578
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320278585 Withdrawn - After Issue CN203248132U (en) | 2013-05-21 | 2013-05-21 | Crank type reversing buffer device for bumping unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203248132U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233706A (en) * | 2013-05-21 | 2013-08-07 | 江苏圣乐机械有限公司 | Crank-type reversing buffer device for pumping unit |
| CN106639988A (en) * | 2017-03-17 | 2017-05-10 | 董少明 | Single-reversing oil pumping unit with triangular chains |
| CN110329875A (en) * | 2019-08-12 | 2019-10-15 | 伊塞克电梯有限公司 | A kind of steering Lian Shengqi for wirerope and load |
-
2013
- 2013-05-21 CN CN 201320278585 patent/CN203248132U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103233706A (en) * | 2013-05-21 | 2013-08-07 | 江苏圣乐机械有限公司 | Crank-type reversing buffer device for pumping unit |
| CN106639988A (en) * | 2017-03-17 | 2017-05-10 | 董少明 | Single-reversing oil pumping unit with triangular chains |
| CN110329875A (en) * | 2019-08-12 | 2019-10-15 | 伊塞克电梯有限公司 | A kind of steering Lian Shengqi for wirerope and load |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20131023 Effective date of abandoning: 20141015 |
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| RGAV | Abandon patent right to avoid regrant |