WO2015135400A1 - A switching reciprocating incomplete non-circular gear transmission box and a transmission mechanism thereof - Google Patents
A switching reciprocating incomplete non-circular gear transmission box and a transmission mechanism thereof Download PDFInfo
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- WO2015135400A1 WO2015135400A1 PCT/CN2015/071166 CN2015071166W WO2015135400A1 WO 2015135400 A1 WO2015135400 A1 WO 2015135400A1 CN 2015071166 W CN2015071166 W CN 2015071166W WO 2015135400 A1 WO2015135400 A1 WO 2015135400A1
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- switching
- circular gear
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 139
- 230000007246 mechanism Effects 0.000 title claims abstract description 43
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H27/00—Step-by-step mechanisms without freewheel members, e.g. Geneva drives
- F16H27/04—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement
- F16H27/08—Step-by-step mechanisms without freewheel members, e.g. Geneva drives for converting continuous rotation into a step-by-step rotary movement with driving toothed gears with interrupted toothing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/42—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with gears having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/08—Profiling
- F16H55/084—Non-circular rigid toothed member, e.g. elliptic gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
- F16H2003/008—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths comprising means for selectively driving countershafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H35/00—Gearings or mechanisms with other special functional features
- F16H2035/003—Gearings comprising pulleys or toothed members of non-circular shape, e.g. elliptical gears
Definitions
- the invention relates to a switching reciprocating incomplete non-circular gearbox and a transmission mechanism thereof, which are used for various mechanical mechanisms that require continuous rotational movement of an input shaft and reciprocal switching of a rotating direction of an output shaft.
- the invention belongs to the field of mechanical equipment and can be applied to the reciprocating commutation and transmission mechanism of the mechanical equipment in the light industrial machinery industry or the oil drilling industry.
- the beam pumping unit which is the main equipment of oil drilling equipment, is famous for its special working environment suitable for all weather in the field. At the same time, it has simple structure, less wearing parts, solid and durable, high reliability and easy operation. The advantages of convenient maintenance and low maintenance cost have always dominated the oil production equipment.
- the traditional beam pumping unit has high energy consumption and heavy weight. It is difficult to achieve long stroke and low stroke pumping. In the oil pumping production, the accident of the sucker rod is increased, and the pumping pump row is increased. The amount is reduced.
- the vertical pumping unit with no beam is a typical representative. It has the advantage of eliminating the energy-consuming transmission link of the beam pumping unit using a four-bar linkage mechanism to convert the rotary motion into a linear motion.
- the movement law of the vertical pumping unit is to use a wide belt or chain to make a clockwise and counterclockwise reciprocating rotary rotation motion under the driving guidance of the drum and the roller or the sprocket, thereby driving the sucker rod and the oil pump.
- the underground crude oil is pumped to the ground.
- Different types of vertical pumping units have different strokes and strokes.
- the vertical pumping unit reverses the up and down strokes, there is only a short time shifting movement, and 90% of the stroke length is
- the straight motion is straight up and down, so the dynamic load is small, and the weight of the switchboard is small, only one-third to one-half of the beam pumping unit.
- the stroke is increased by increasing the height of the gantry.
- the vertical pumping unit is easy to realize long stroke, the stroke of the long stroke pumping unit is lower, the acceleration of the motion system is greatly reduced, the inertia load is small, the inertia load is greatly reduced, and the performance of the pumping unit is greatly improved.
- this vertical pumping unit also has its Achilles heel: First, the reversing mechanism of the vertical chain pumping unit has a high failure rate and is easy to be damaged. The second is the motor reversing inverter of the vertical belt pumping unit. The cost is high and it is difficult to handle the harsh working environment around the clock. Therefore, it has been difficult to replace the beam pumping unit on a large scale.
- the vertical pumping unit not only has the advantages of reliable and durable reversing of the beam pumping unit, but also reduces the manufacturing cost and adapts to the harsh environmental conditions of working around the clock. in this way, The short life and unreliable weakness of the vertical pumping unit's reversing parts can be effectively and completely changed, so that this vertical pumping unit with obvious technical advantages is more suitable for various complicated working conditions and environments.
- the problem to be solved by the present invention is to propose an input shaft continuous rotation and an output shaft in the The incomplete non-circular gearbox and its transmission mechanism that can perform the rotary motion according to the specific shifting law while reciprocally switching the rotation direction achieve the effect of the motor frequency conversion commutation.
- the invention relates to a switching reciprocating incomplete non-circular gear transmission, comprising an input shaft 1 and an active switching incomplete non-circular gear on the input shaft, a first transmission shaft and a first on the first transmission shaft Slave switching the incomplete non-circular gear 4 and the first spur gear, the second transmission shaft, and the second driven switching incomplete non-circular gear and the second spur gear, the box body and the cover on the second transmission shaft,
- the first driven switching incomplete non-circular gear, the second driven switching incomplete non-circular gear are located on both sides of the active switching incomplete non-circular gear and are mounted side by side, the first driven switching incomplete non-circular gear
- the second slave switch is incomplete.
- the rotational speed of the non-circular gear changes from slow to fast, constant speed, fast to slow, and then to the switching direction.
- the input shaft 1 and the active switching on it are incomplete non-circular
- the gear rotates 360 degrees in a clockwise or counterclockwise direction the first transmission shaft and the second transmission shaft are simultaneously rotated once in a counterclockwise, clockwise or clockwise, counterclockwise sequence;
- the active switching incompletely non-circular gear in the switching reciprocating incomplete non-circular gearbox rotates clockwise and begins to intermesh with the toothed portion of the second driven switching incomplete non-circular gear, the second The second spur gear with the incompletely non-circular gear and the coaxial power connection starts to rotate counterclockwise, the first spur gear meshed with the second spur gear and the first slave connected to the first spur gear Switching incomplete non-circular gears to make clockwise rotation, when actively switching incomplete non-circular gears and When the second slave switches the incomplete non-circular gear meshing and rotates 180 degrees clockwise, the second transmission shaft and the second driven switching incomplete non-circular gear and the second spur gear located thereon rotate counterclockwise once.
- the first transmission shaft and the first driven switching incomplete non-circular gear and the first spur gear thereon are rotated clockwise once;
- the above-mentioned switching reciprocating incomplete non-circular gear transmission has a pitch curve of two arcs of 60 degrees, a constant velocity zone of 60 degrees, and a toothlessness of 180 degrees.
- the configuration of the pattern region; the uniform velocity region in the pitch curve 28 of the active switching incomplete non-circular gear is located in the toothed portion corresponding to the large arc R1 region; the toothless curve in the pitch curve of the active switching incomplete non-circular gear
- the pattern area 31 corresponds to the small arc R2 area; the center line of the active switching incomplete non-circular gear passes through a slot in the middle of the uniform speed zone; the number of teeth of the active switching incomplete non-circular gear is Even number, the number of slots is odd;
- the pitch curves of the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear are both changed by two angles of 60 degrees, and one arc is a constant speed zone of 180 degrees, a toothless zone with a curvature of 60 degrees;
- the uniform velocity zone in the section curve of the first driven switch incomplete non-circular gear and the second slave switch incomplete non-circular gear is located a tooth-shaped portion corresponding to the small arc R2 region;
- a first driven switching incomplete non-circular gear and a second driven switching incomplete non-circular gear rotating center line passing through a tooth of a middle portion of the uniform velocity zone;
- the first driven switching incomplete non-circular gear and the second The number of teeth of the incomplete non-circular gear is odd, and the number of slots is even.
- the above-mentioned switching reciprocating non-circular gear transmission, the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear, and the second driven switching incomplete non-circular gear rotating center "O", is a large circle
- R1 is a radius of a large arc area of a pitch curve of the pitch curve of the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear, and the second driven switching incomplete non-circular gear;
- R2 is a radius of a small arc area of the pitch curve of the pitch curve of the incomplete non-circular gear that actively switches the incomplete non-circular gear, the first driven switch incomplete non-circular gear, and the second driven switch incomplete non-circular gear;
- ⁇ is an integral part of the shifting section curve of the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear are in their respective complete The corresponding angle within the curve coordinate system.
- the tooth thickness of the deformation switching tooth of the active switching incomplete non-circular gear 5 is three times the tooth thickness of the adjacent tooth, and the full height of the tooth of the deformation switching tooth is adjacent thereto
- the full height of the gear teeth is 1.0 times to 1.65 times, and the shape of the tooth top line segment of the deformation switching tooth is parallel with the adjacent curve line segment, and the tooth profile of the deformation switching tooth is still the involute tooth profile.
- the deformation of the cogging groove has a cogging thickness which is adjacent to the wheel 3 times the thickness of the tooth groove, the tooth groove depth of the deformation switching tooth groove is 1.0 times to 1.75 times the tooth groove depth of the adjacent tooth tooth, and the shape of the line segment of the root line of the deformation switching tooth groove is adjacent thereto
- the section line segments are parallel.
- the invention also provides a transmission mechanism, the transmission mechanism comprising:
- the input shaft of the above-mentioned switching reciprocating incomplete non-circular gearbox can be connected with a coupling of one or more of a sprocket, a pulley, and various gear mechanisms through a coupling to implement a power input;
- the output shaft of the above-mentioned switching reciprocating incomplete non-circular gear transmission is connected to the third transmission shaft and the third spur gear, the fourth transmission shaft and the fourth spur gear located thereon through the coupling, thereby realizing the power Output
- the output shaft of the above-mentioned switching reciprocating incomplete non-circular gear transmission can also be connected to one or a combination of a sprocket system, a pulley train or a sprocket, a pulley, a cylindrical gear train through a coupling, thereby realizing power output.
- the present invention further provides a vertical pumping unit in which the reversing mechanism of the sucker rod of the vertical pumping unit is mounted with the above-mentioned transmission mechanism.
- the existing vertical pumping unit is a kind of oil recovery machine that works in the field for many years.
- the commutation of the upper and lower strokes of the sucker rod is completed by the motor frequency conversion device.
- the electrical components in the motor frequency conversion device cannot be sustained for a long time.
- the harsh conditions caused by high temperature, low temperature, wind, rain, snow, thunder, lightning, and the longest one-time service life in China are only more than one year, which makes this kind of comparison with the beam pumping unit.
- the wide-scale promotion of vertical pumping units with energy-saving advantages has been seriously hindered.
- the vertical pumping unit has the shifting requirement in the up and down stroke. When the end of the sucker rod is close to the end of the up and down stroke, it is gradually decelerated to zero speed, and it is quickly reversed, and then gradually accelerates to the normal speed. This technical requirement is existing.
- the vertical pumping unit is completed by the programs and electrical components stored in the inverter, and there are still weak points that are difficult to adapt and the frequent equipment failures that occur throughout the day.
- One of the core technologies of the present invention is to solidify the motion law of the sucker rod of the vertical pumping unit on the shape and the tooth shape of the gear, so that the movement requirement of the main machine can be accurately realized in the rotary motion, and is completely free from any bad weather and
- the long-term use has the technical advantage of stable, accurate, safe and reliable shifting.
- the motor frequency conversion technology adopted by the existing vertical pumping unit has high manufacturing cost and puts forward a high technical level requirement for the operator of the oil production plant.
- the technology of the present invention adopts a mature gear manufacturing scheme, and completely eliminates the innate cause of the high failure rate of the vertical pumping unit from the host design stage, so that the manufacturing cost and the use cost of the vertical pumping unit are greatly increased. reduce;
- FIG. 1 is a schematic view of a switching reciprocating incomplete non-circular gearbox of the present invention
- FIG. 2 is a state diagram of the active switching of the incomplete non-circular gearbox of FIG. 1 in the clockwise rotation of the incomplete non-circular gear 5 at the initial 0 degree;
- FIG. 3 is a view showing a state in which the active switching incomplete non-circular gear 5 of the reciprocating incomplete non-circular gear transmission of FIG. 1 rotates clockwise at 180 degrees;
- Figure 5 is a transient state of the output rotation speed from the slow to the fast rotation when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
- Figure 7 is a transient state of the output rotation speed from the fast to the slow rotation when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
- Figure 9 is a transient state of the output rotation speed from the slow to the fast rotation when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- Figure 10 is a view showing an instantaneous state in which the output rotational speed is constant and the rapid rotation is performed when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- Figure 11 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- FIG. 12 is an instant when the active switching incomplete non-circular gear 5 is switched to the second driven switching incomplete non-circular gear 6 again, and another new reciprocating switching direction is started;
- Figure 13 is a schematic view of another switching reciprocating incomplete non-circular gearbox of the present invention.
- Figure 14 is a schematic view of still another switching reciprocating incomplete non-circular gearbox of the present invention.
- Figure 16 is a section curve 28 and a velocity distribution area of the active switching incomplete non-circular gear 5 of the present invention.
- 17 is a schematic switching incomplete non-circular gear 5 of the present invention, a first driven switching incomplete non-circular gear 4, a second driven switching incomplete non-circular gear 6 deformation switching gear teeth and a deformation switching tooth groove;
- Figure 18 is a schematic view showing the input and output transmission mechanism of the switching reciprocating incomplete non-circular gear transmission shown in Figure 1;
- Figure 19 is a schematic view of a vertical pumping unit equipped with the switching reciprocating incomplete non-circular gear transmission of the present invention and its transmission mechanism;
- the utility model relates to a switching reciprocating incomplete non-circular gearbox (Fig. 1) and a transmission mechanism thereof (Fig. 18), which can provide an input shaft continuous rotation output shaft in a clockwise, counterclockwise or counterclockwise, clockwise manner
- the rotation law reciprocally switches the function of the rotary rotation output (Fig. 1, Fig. 2, Fig. 3).
- the switching reciprocating incomplete non-circular gearbox is an input shaft 1 and an active switching incomplete non-circular gear 5 on the input shaft 1, a first transmission shaft 2, and on the first transmission shaft 2
- the output shaft 10 and the output shaft spur gear 9, the casing 11, and the cover 12 on the output shaft 10 are composed of components.
- FIG. 1 also shows an important function gear set, that is, a deformation switching gear, which can make the output shaft 10, the first transmission shaft 2, and the second transmission shaft 3 of the switching reciprocating incomplete non-circular gear transmission reciprocally switch.
- the composition of the group, which is driven by a driving gear, that is, the active switching of the incomplete non-circular gear 5 and the two driven switching incomplete non-circular gears, that is, the first driven switching incomplete non-circular gear 4, the second driven Switching is made up of incomplete non-circular gears 6.
- the active switching incomplete non-circular gear 5 is mounted on the input shaft 1
- the first driven switching incomplete non-circular gear 4 is mounted on the first transmission shaft 2
- the second driven switching incomplete non-circular gear 6 Mounted on the second transmission shaft 3
- the two driven switching incomplete non-circular gears are respectively mounted on both sides of the active switching incomplete non-circular gear 5 and are mounted side by side.
- FIG. 1 also shows that the first driven switching incomplete non-circular gear 4 is coaxially mounted and coaxially connected with the first spur gear 8, and the second driven switching incomplete non-circular gear 6 is the same as the second spur gear 7.
- the shaft is mounted and coaxially coupled, wherein the second spur gear 7 and the first spur gear 8 are in meshing engagement, and the output shaft spur gear 9 mounted on the output shaft 10 is meshed with the first spur gear 8 and is switched
- the reciprocating incomplete non-circular gear transmission transmits a rotary motion of the reciprocating switching direction.
- Figure 2 shows the state diagram of the active switching of the incomplete non-circular gear 5 at 0 degrees when the switching reciprocating incomplete non-circular gearbox is in operation after installation:
- the second driven switch is incomplete non-circular gear 6 and coaxial
- the second cylindrical gear 7 of the power connection starts to rotate counterclockwise, and the first circle meshes with the second spur gear 7
- the column gear 8 and the first driven switching incomplete non-circular gear 4 coaxially connected to the first spur gear 8 are rotated clockwise, and the spur gear 9 meshing with the clockwise rotating first spur gear 8 and the power The connected output shaft 10 simultaneously rotates counterclockwise.
- Figure 3 shows a state diagram of actively switching the incomplete non-circular gear 5 at 180 degrees:
- the first driven switching incomplete non-circular gear 4 is the same
- the first spur gear 8 of the shaft power connection rotates counterclockwise
- the second spur gear 7 meshing with the first spur gear 8 and the second driven switching incomplete non-circular gear coaxially connected with the first spur gear 7 6 clockwise rotation
- the output shaft spur gear 9 meshing with the counterclockwise rotating first spur gear 8 simultaneously rotates clockwise with the power output output shaft 10
- the second transmission shaft 3 and the second driven switching incomplete non-circular gear 6 and the second spur gear 7 and the output shaft thereon 10 and the output shaft spur gear 9 located thereon rotates clockwise once
- the first transmission shaft 2 and the first driven switching incomplete non-circular gear 4 and the first spur gear 8 thereon are rotated counterclockwise once
- Figure 5 is a diagram showing an instantaneous state in which the output rotational speed is rotated from slow to fast when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
- Figure 6 shows that the second driven switching incompletely non-circular gear 6 rotates counterclockwise and the output speed is uniform and fast. a transient state during rapid rotation
- Figure 7 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
- FIG. 8 shows an instantaneous state in which the active switching of the incomplete non-circular gear 5 is switched to the first driven switching incomplete non-circular gear 4;
- Figure 9 is a view showing an instantaneous state in which the output rotational speed is rotated from slow to fast when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- Figure 10 is a view showing an instantaneous state in which the output rotational speed is constant and the rapid rotation is performed when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- Figure 11 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
- Fig. 12 shows the moment when the active switching incomplete non-circular gear 5 is switched to the second driven switching incomplete non-circular gear 6 again, and the new output reciprocating switching rotary rotational motion starts again.
- Figure 13 illustrates another switching reciprocating incomplete non-circular gearbox of the present invention: when the main engine does not require a change in the rotational speed of the first drive shaft 2 or the second drive shaft 3, the output shaft 10 can be removed and located therein
- the upper output shaft spur gear 9 directly adopts the first transmission shaft 2 or the second transmission shaft 3 as an output shaft, so that the purpose of outputting the rotary motion of the reciprocating switching rotation direction can still be achieved.
- Figure 14 shows still another switching reciprocating incomplete non-circular gearbox of the present invention: when the main engine needs to add one or more output shafts in the switching reciprocating incomplete non-circular gearbox, we can One or more sets of "output shaft 10 and output shaft spur gear 9 above output shaft 10" are added, and the newly added output shaft spur gear 9 and the original output shaft spur gear 9 or second cylinder in the casing are added.
- the gears 7 mesh with each other to form an output function of the multi-axis multi-position output reciprocating switching rotation direction composed of the first transmission shaft 2, the second transmission shaft 3, and one or more output shafts 10.
- the specific implementation method of actively switching the incomplete non-circular gear 5 and the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6 is as follows:
- FIG. 15 and FIG. 16 respectively show the pitch curve patterns of the first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6, and the actively switching incomplete non-circular gear 5, which are large
- the arc R1 and the small arc R2 and the shifting section curve between R1 and R2 are composed;
- Figure 15 also shows that the first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6 has a pitch curve 33 of two shifting zones 35 having an angle of 60 degrees, and an arc of 180 a uniform velocity zone 37, a dentless zone 36 having a curvature of 60 degrees; the first driven switching incomplete non-circular gear 4, the second driven switching incomplete curve of the incomplete non-circular gear 6
- the zone 37 is located in the toothed portion corresponding to the small arc R2 region.
- the non-toothed area 36 in the pitch curve 33 of the first dynamic deformation switching gear 4 and the second driven switching incomplete non-circular gear 6 corresponds to the large arc R1 area;
- the second driven switching incomplete non-circular gear 6 has a rotation center line passing through one of the teeth of the middle portion of the constant velocity zone 37, and the first driven switching incomplete non-circular gear 4, the second The number of teeth of the incompletely non-circular gear 6 is odd, and the number of slots is even.
- Figure 16 shows that the pitch curve 28 of the active switching incomplete non-circular gear 5 is composed of two shifting zones 29 having a curvature of 60 degrees, a uniform velocity zone 30 having an arc of 60 degrees, and a lenticular zone of a curvature of 180 degrees. 31.
- the uniform velocity zone 30 in the pitch curve 28 of the active switching incomplete non-circular gear 5 is located in the toothed portion corresponding to the large arc R1 region.
- the non-toothed area 31 in the pitch curve 28 of the active non-revolving non-circular gear 5 corresponds to the small arc R2 area; the active center of the incomplete non-circular gear 5 processed according to the above-mentioned section curve passes through the uniform speed zone.
- a cogging in the middle of 30, and actively switching the number of teeth of the incomplete non-circular gear 5 is even Number, the number of slots is odd.
- FIG. 15 and FIG. 16 further show that the active switching of the incomplete non-circular gear 5 is similar to that of the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6, but The values of their regional parameters are not identical. Since the switching reciprocating incomplete non-circular gearbox has a variety of load variations and motion requirements, the pitch curve 28 of the incompletely non-circular gear 5 and the first slave switching incomplete non-circular gear 4 and the second are actively switched. The pitch curve 33 of the driven incompletely non-circular gear 6 also has diversity, and also determines the active switching of the incomplete non-circular gear 5 and the first driven switching incomplete non-circular gear 4, and the second driven switching is not The complete non-circular gear 6 is also versatile.
- FIG. 16 further illustrate the design principle and method of actively switching the incomplete non-circular gear and the driven switching incomplete non-circular gear. It can be seen that the active switching incomplete non-circular gear 5 or the first driven switching is not The complete non-circular gear 4, the second driven switching incomplete non-circular gear 6 has a center of rotation "O", which is the geometric center of the large arc R1 and the small arc R2;
- R1 is a pitch curve 28 for actively switching the incomplete non-circular gear 5 or switching the gear 4 from the first dynamic deformation,
- the second slave switches the radius of the large arc area of the node curve 33 of the incomplete non-circular gear 6;
- R2 is a radius of a small arc area of the pitch curve 33 of the pitch curve 33 of the first switch or the incomplete non-circular gear 6;
- ⁇ is the shifting zone 29 curve 32 of the active switching incomplete non-circular gear 5, the first driven switching incomplete non-circular gear 4, and the second driven switching incomplete non-circular gear 6 on the shifting section 35 curve 34 The angle at which any point corresponds within its respective complete pitch coordinate system.
- Fig. 17 shows that the active switching incomplete non-circular gear 5 processed on the numerically controlled machine tool has two shifting portions 29, and each of the shifting portions 29 has a deformation switching tooth 39 near the end of the edentulous type region 31.
- the first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6 of the two shifting regions 35 near the end of the edentulous type region 36 each has a deformation switching tooth groove 38;
- the technical requirement of the deformation switching tooth 39 for actively switching the incomplete non-circular gear 5 is that the tooth thickness of the deformation switching tooth 39 is three times the tooth thickness of the adjacent gear tooth, and the full height of the tooth of the deformation switching tooth 39 is the adjacent wheel thereof.
- the shape of the top line segment of the deformation switching tooth 39 is parallel to the section curve line adjacent thereto, and the tooth profile of the deformation switching tooth 39 is still an involute profile;
- the technical requirement of processing the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6 to change the tooth slot 38 is that the tooth gap thickness of the deformation switching tooth groove 38 is adjacent thereto 3 times the thickness of the tooth cogging, the total height of the tooth gap of the deformation switching tooth groove 38 is 1.0 times to 1.75 times the full height of the tooth groove adjacent thereto, and the shape of the line of the tooth root line of the deformation switching tooth groove 38 Parallel to the section line segment adjacent to it.
- the reciprocating incomplete non-circular gear transmission can be operated, and the switching reciprocating incomplete non-circular gear transmission is in two rotation directions: clockwise and counterclockwise.
- the output speed also has the characteristics of speed change from slow to fast, constant speed, fast to slow, and then to the switching direction.
- the switching reciprocating incomplete non-circular gear transmission shown in FIG. 18 and its transmission mechanism are powered by switching the reciprocating incomplete non-circular gear transmission, and the output shaft 10 or the first transmission shaft 2 and the second transmission shaft 3 a third transmission shaft 21 and a third spur gear 13 thereon, a fourth transmission shaft 15 and a fourth spur gear 14 located thereon, a fifth transmission shaft 16 that is power-connected to the input shaft 1, and a pulley 17 located thereon a sixth input shaft 18 and a pulley 19 located thereon, a belt 20 located above the pulley 17 and the pulley 18;
- the input shaft 1 can also be connected with the sprocket or various gear mechanisms or any combination of sprocket, pulley, and various gear mechanisms through the coupling and the fifth transmission shaft 16;
- Figure 18 further shows that we can use one or more sets of "third spur gear 13, fourth spur gear 14, fourth output shaft 15, third drive shaft 21" and the switching reciprocating incomplete non-circular gear shifting
- the first transmission shaft 2 or the second transmission shaft 3 or the output shaft 10 of the box or the respective shaft ends of the first transmission shaft 2, the second transmission shaft 3, and the output shaft 10 are simultaneously connected with a single shaft or a plurality of shafts (for example, The power connection is made by passing the shaft end of one or more third transmission shafts 21 through the coupling with the first transmission shaft 2 or the second transmission shaft 3 or the output shaft 10 or simultaneously.
- the shaft ends of the first transmission shaft 2, the second transmission shaft 3, and the output shaft 10 are connected to realize a single-axis output reciprocating switching rotation motion or a multi-axis multi-position output reciprocating switching rotation motion.
- the third spur gear 13 and the fourth spur gear 14 in the transmission mechanism can also be replaced by other sprocket or pulley or spur gear train or any combination of sprocket, pulley and spur gear train.
- the vertical pumping unit shown in Fig. 19 removes the existing transmission and reversing mechanism of the vertical pumping unit based on the existing vertical pumping unit, and retains the existing vertical pumping unit.
- the frame 23, the sucker rod 24, the belt 25, the counterweight 26, the drum 27 and the like, and the switching reciprocating incomplete non-circular gear transmission of the present invention and the transmission mechanism thereof can be configured to have a switching up and down stroke direction The new vertical pumping unit.
- the specific installation method is:
- the shaft end of the fifth transmission shaft 16 in the transmission mechanism is coupled to the shaft end portion of the input shaft 1 of the switching reciprocating incompletely non-circular gear transmission through the coupling, and the shaft end portion of the sixth transmission shaft 18 is
- the shaft end of the motor 22 is connected by a coupling, so that any combination of the sprocket or the pulley or the gear mechanism or the sprocket, the pulley and the gear mechanism on the fifth transmission shaft 16 and the sixth transmission shaft 18 can be normally operated.
- the novel vertical pumping unit equipped with the switching reciprocating incomplete non-circular gear transmission and its transmission mechanism adopts a switching reciprocating incomplete non-circular gear transmission according to the invention, and a reversing mechanism thereof
- the transmission mechanism not only retains the shifting characteristics of the up and down stroke of the vertical pumping unit, but also overcomes the technical difficulties of the conventional vertical pumping unit motor frequency conversion and reversing function, and the long-term unreliable use in all weather.
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Abstract
A switching reciprocating incomplete non-circular gear transmission box comprises a driving switching incomplete non-circular gear (5), a first driven switching incomplete non-circular gear (4), a second driven switching incomplete non-circular gear (6), a cylindrical gear train, a box body (11) and a box cover (12). The transmission box is a power transmitting device, wherein an output shaft (10) can clockwise and anticlockwise switch the rotation direction in a reciprocating mode at the changeable speed, when an input shaft (1) rotates continuously. The driving switching incomplete non-circular gear comprises two deformed switching teeth (39), and the driven switching incomplete non-circular gears comprise two deformed switching tooth grooves (38) respectively. The section curve of the driving switching incomplete non-circular gear and the section curves of the driven switching incomplete non-circular gears can present various technical characteristics according to different main machine loads and movement requirements. The transmission box can output speed-change motion with the rotation direction switched in a reciprocating mode by one single shaft or multiple shafts and can replace some mechanical or electric control reversing mechanism.
Description
本发明涉及一种切换往复不完整非圆齿轮变速箱及其传动机构,其用于需要输入轴连续旋转运动和输出轴往复切换旋转方向的各类机械机构。本发明属于机械设备领域,可应用于轻工机械行业或石油钻采行业机械设备的往复换向及传动机构。The invention relates to a switching reciprocating incomplete non-circular gearbox and a transmission mechanism thereof, which are used for various mechanical mechanisms that require continuous rotational movement of an input shaft and reciprocal switching of a rotating direction of an output shaft. The invention belongs to the field of mechanical equipment and can be applied to the reciprocating commutation and transmission mechanism of the mechanical equipment in the light industrial machinery industry or the oil drilling industry.
许多机械设备都需要往复循环旋转的动作,有些机械设备还需要多轴多位置输出往复切换旋转方向的机构,如轻工行业的烟草机械、饮料机械,包装机械、粮油机械、印刷机械等。目前,一些重工机械设备也迫切需要这类机构,如石油钻采行业的立式抽油机就是其中一个典型案例。传统的往复切换旋转方向的机械机构,较为复杂,寿命和可靠性好的结构形式不多。下面我们以石油钻采行业的立式抽油机作为一个经典案例加以分析。Many mechanical devices require reciprocating cyclic rotation. Some mechanical devices also require multi-axis multi-position output to switch the direction of rotation, such as tobacco machinery, beverage machinery, packaging machinery, grain and oil machinery, printing machinery, etc. in the light industry. At present, some heavy machinery and equipment are also in urgent need of such institutions, such as the vertical pumping unit in the oil drilling industry is one of the typical cases. The traditional mechanical mechanism for reciprocating the rotational direction is relatively complicated, and the structure with good life and reliability is not much. Below we analyze the vertical pumping unit of the oil drilling industry as a classic case.
众所周知,作为石油钻采设备主力装备的游梁式抽油机,以特别能适应野外全天候的恶劣工作环境而著称,同时其结构简单,易损件少,坚实耐用,可靠性强,操作简便,维修方便,维修费用低的优势,使其一直在采油设备中占据主导地位。As we all know, the beam pumping unit, which is the main equipment of oil drilling equipment, is famous for its special working environment suitable for all weather in the field. At the same time, it has simple structure, less wearing parts, solid and durable, high reliability and easy operation. The advantages of convenient maintenance and low maintenance cost have always dominated the oil production equipment.
随着井深和产量的不断增加,同时随着油井开采复杂情况的不断出现,如高粘度、多蜡、多沙、多气、水淹和强腐蚀等工况,使传统游梁式抽油机的许多问题明显显现出来,主要是游梁式抽油机的能耗高、重量大,难以实现长冲程、低冲次抽油,在抽油生产中抽油杆的事故增多,抽油泵的排量降低等。为了克服这些缺点,国内外许多厂家先后研制了前置式抽油机、异相曲柄抽油机、
空气平衡抽油机等,虽然克服了常规游梁式抽油机的一些缺点,但是仍没有脱离传统游梁式抽油机利用四连杆机构将旋转运动转化为往复直线运动的传动方式。这种四连杆机构的运动和受力特性使其在节能分析中饱受诟病,尤其是大马拉小车和副扭矩大的耗能问题不断被人们的科学实践所挑战,各类新型节能无游梁式抽油机因此也不断问世。With the increasing depth and production volume, and with the continuous emergence of complex oil wells, such as high viscosity, multi-wax, sand, gas, flooding and strong corrosion, the traditional beam pumping unit Many problems have become apparent. The main reason is that the beam pumping unit has high energy consumption and heavy weight. It is difficult to achieve long stroke and low stroke pumping. In the oil pumping production, the accident of the sucker rod is increased, and the pumping pump row is increased. The amount is reduced. In order to overcome these shortcomings, many domestic and foreign manufacturers have developed front-mounted pumping units, out-of-phase crank pumping units,
Air balance pumping units, etc., have overcome some of the shortcomings of conventional beam pumping units, but still do not deviate from the traditional beam pumping unit to convert the rotary motion into a reciprocating linear motion using a four-bar linkage mechanism. The motion and force characteristics of this four-bar linkage mechanism have made it criticized in energy-saving analysis. In particular, the energy consumption problem of large horse-drawn carriages and large torques is constantly being challenged by people's scientific practice. The beam pumping unit is therefore constantly coming out.
上个世纪80年代以后,各采油设备生产厂家相继研发了新一代高效节能型抽油机,纠正了上述机型的大部分问题,各种无游梁式抽油机相继开始生产并投入采油工地使用,无游梁的立式抽油机就是其中的典型代表。它的优点是取消了游梁式抽油机使用四连杆机构将旋转运动转化为直线运动的耗能传动环节。立式抽油机的运动规律是使用一种宽幅皮带或链条在滚筒和滚轮或链轮的驱动引导下做顺时针、逆时针往复切换旋向的旋转运动,从而带动抽油杆和抽油泵将地下原油抽吸到地面上来,不同规格的立式抽油机有不同的冲程和冲次,当立式抽油机上下冲程换向期间才有短时间的变速运动,90%的冲程长度是直上直下的匀速运动,因而动载较小,总机重量小,只是游梁式抽油机的三分之一到二分之一。结构紧凑,占地面积小,特别适合做长冲程抽油机,加大冲程通过增加台架高度的方法完成。立式抽油机容易实现长冲程,长冲程抽油机的冲次较低,大大降低了运动***的加速度,惯性载荷小,惯性载荷大幅度下降,抽油机性能得到较大改善。但是,这种立式抽油机也有其致命弱点:其一是立式链条抽油机的换向机构故障率较高,易损坏,其二是立式皮带抽油机的电机换向变频器成本高,且难以胜任全天候的恶劣工作环境。所以,至今难以大规模的替代游梁式抽油机。After the 1980s, various oil production equipment manufacturers have successively developed a new generation of high-efficiency energy-saving pumping units, which have corrected most of the problems of the above-mentioned models. Various non-beam pumping units have started production and put into production sites. The vertical pumping unit with no beam is a typical representative. It has the advantage of eliminating the energy-consuming transmission link of the beam pumping unit using a four-bar linkage mechanism to convert the rotary motion into a linear motion. The movement law of the vertical pumping unit is to use a wide belt or chain to make a clockwise and counterclockwise reciprocating rotary rotation motion under the driving guidance of the drum and the roller or the sprocket, thereby driving the sucker rod and the oil pump. The underground crude oil is pumped to the ground. Different types of vertical pumping units have different strokes and strokes. When the vertical pumping unit reverses the up and down strokes, there is only a short time shifting movement, and 90% of the stroke length is The straight motion is straight up and down, so the dynamic load is small, and the weight of the switchboard is small, only one-third to one-half of the beam pumping unit. Compact structure and small footprint, it is especially suitable for long-stroke pumping units. The stroke is increased by increasing the height of the gantry. The vertical pumping unit is easy to realize long stroke, the stroke of the long stroke pumping unit is lower, the acceleration of the motion system is greatly reduced, the inertia load is small, the inertia load is greatly reduced, and the performance of the pumping unit is greatly improved. However, this vertical pumping unit also has its Achilles heel: First, the reversing mechanism of the vertical chain pumping unit has a high failure rate and is easy to be damaged. The second is the motor reversing inverter of the vertical belt pumping unit. The cost is high and it is difficult to handle the harsh working environment around the clock. Therefore, it has been difficult to replace the beam pumping unit on a large scale.
寻找一种机械的换向机构,使立式抽油机既具备游梁式抽油机换向可靠耐用的优势,又同时可以降低制造成本,适应全天候工作的恶劣环境条件。如此,
立式抽油机换向部件寿命短、不可靠的弱点就可以得到有效彻底的改变,从而使这种具有明显技术优势的立式抽油机更加适应各种复杂的工作条件和环境。Looking for a mechanical reversing mechanism, the vertical pumping unit not only has the advantages of reliable and durable reversing of the beam pumping unit, but also reduces the manufacturing cost and adapts to the harsh environmental conditions of working around the clock. in this way,
The short life and unreliable weakness of the vertical pumping unit's reversing parts can be effectively and completely changed, so that this vertical pumping unit with obvious technical advantages is more suitable for various complicated working conditions and environments.
发明内容Summary of the invention
工业领域内有许多机械设备因为各种原因希望将现有电机变频换向结构,改为齿轮箱传动换向的结构,本发明所要解决的问题在于提出了一种输入轴连续旋转、输出轴在按照特定的变速规律做旋转运动的同时又可往复切换旋转方向的不完整非圆齿轮变速箱及其传动机构,达到了电机变频换向的效果。There are many mechanical equipments in the industrial field. For various reasons, it is desirable to change the existing motor frequency conversion structure to the gear box transmission commutation structure. The problem to be solved by the present invention is to propose an input shaft continuous rotation and an output shaft in the The incomplete non-circular gearbox and its transmission mechanism that can perform the rotary motion according to the specific shifting law while reciprocally switching the rotation direction achieve the effect of the motor frequency conversion commutation.
本发明提出的一种切换往复不完整非圆齿轮变速箱,包括输入轴1以及位于该输入轴上的主动切换不完整非圆齿轮、第一传动轴以及位于该第一传动轴上的第一从动切换不完整非圆齿轮4和第一圆柱齿轮、第二传动轴以及位于该第二传动轴上的第二从动切换不完整非圆齿轮和第二圆柱齿轮、箱体和箱盖,所述第一从动切换不完整非圆齿轮、第二从动切换不完整非圆齿轮位于所述主动切换不完整非圆齿轮的两边且并排啮合安装,第一从动切换不完整非圆齿轮、第二从动切换不完整非圆齿轮的旋转速度变化是从慢到快、匀速快速、从快到慢、再到切换旋向,当输入轴1以及位于其上的主动切换不完整非圆齿轮按照顺时针或逆时针方向每旋转360度时,第一传动轴和第二传动轴则同时按照逆时针、顺时针或顺时针、逆时针的顺序各旋转一次;The invention relates to a switching reciprocating incomplete non-circular gear transmission, comprising an input shaft 1 and an active switching incomplete non-circular gear on the input shaft, a first transmission shaft and a first on the first transmission shaft Slave switching the incomplete non-circular gear 4 and the first spur gear, the second transmission shaft, and the second driven switching incomplete non-circular gear and the second spur gear, the box body and the cover on the second transmission shaft, The first driven switching incomplete non-circular gear, the second driven switching incomplete non-circular gear are located on both sides of the active switching incomplete non-circular gear and are mounted side by side, the first driven switching incomplete non-circular gear The second slave switch is incomplete. The rotational speed of the non-circular gear changes from slow to fast, constant speed, fast to slow, and then to the switching direction. When the input shaft 1 and the active switching on it are incomplete non-circular When the gear rotates 360 degrees in a clockwise or counterclockwise direction, the first transmission shaft and the second transmission shaft are simultaneously rotated once in a counterclockwise, clockwise or clockwise, counterclockwise sequence;
所述一种切换往复不完整非圆齿轮变速箱中的主动切换不完整非圆齿轮顺时针旋转并开始与第二从动切换不完整非圆齿轮的有齿形部分进入相互啮合时,第二从动切换不完整非圆齿轮与同轴动力连接的第二圆柱齿轮开始作逆时针旋转,与第二圆柱齿轮啮合的第一圆柱齿轮以及与第一圆柱齿轮同轴动力连接的第一从动切换不完整非圆齿轮做顺时针旋转,当主动切换不完整非圆齿轮与第
二从动切换不完整非圆齿轮啮合并顺时针旋转了180度时,第二传动轴以及位于其上的第二从动切换不完整非圆齿轮和第二圆柱齿轮则逆时针旋转了一次,第一传动轴以及位于其上的第一从动切换不完整非圆齿轮、第一圆柱齿轮则顺时针旋转了一次;The active switching incompletely non-circular gear in the switching reciprocating incomplete non-circular gearbox rotates clockwise and begins to intermesh with the toothed portion of the second driven switching incomplete non-circular gear, the second The second spur gear with the incompletely non-circular gear and the coaxial power connection starts to rotate counterclockwise, the first spur gear meshed with the second spur gear and the first slave connected to the first spur gear Switching incomplete non-circular gears to make clockwise rotation, when actively switching incomplete non-circular gears and
When the second slave switches the incomplete non-circular gear meshing and rotates 180 degrees clockwise, the second transmission shaft and the second driven switching incomplete non-circular gear and the second spur gear located thereon rotate counterclockwise once. The first transmission shaft and the first driven switching incomplete non-circular gear and the first spur gear thereon are rotated clockwise once;
当所述切换往复不完整非圆齿轮变速箱中的主动切换不完整非圆齿轮继续顺时针旋转并开始与第一从动切换不完整非圆齿轮的有齿形部分进入相互啮合时,第一从动切换不完整非圆齿轮与同轴动力连接的第一圆柱齿轮均作逆时针旋转,与第一圆柱齿轮啮合的第二圆柱齿轮以及与第二圆柱齿轮同轴动力连接的第二从动切换不完整非圆齿轮做顺时针旋转,当主动切换不完整非圆齿轮与第一从动切换不完整非圆齿轮啮合并顺时针继续旋转了180度时,第二传动轴以及位于其上的第二从动切换不完整非圆齿轮和第二圆柱齿轮顺时针旋转了一次,第一传动轴以及位于其上的第一从动切换不完整非圆齿轮、第一圆柱齿轮则逆时针旋转了一次。When the active switching incomplete non-circular gear in the switching reciprocating incomplete non-circular gearbox continues to rotate clockwise and begins to intermesh with the toothed portion of the first driven incompletely non-circular gear, the first The driven switching incomplete non-circular gear and the coaxially connected first spur gear rotate counterclockwise, the second spur gear meshing with the first spur gear and the second slave connected coaxially with the second spur gear Switching the incomplete non-circular gear to rotate clockwise, when the active switching incomplete non-circular gear meshes with the first driven incomplete non-circular gear and continues to rotate 180 degrees clockwise, the second drive shaft and the second drive shaft The second driven switching incomplete non-circular gear and the second spur gear rotate clockwise once, and the first transmission shaft and the first driven switching incomplete non-circular gear thereon and the first spur gear rotate counterclockwise once.
所述切换往复不完整非圆齿轮变速箱中的输出轴以及位于该输出轴上的输出轴圆柱齿轮,所述输出轴圆柱齿轮与所述第一圆柱齿轮或与第二圆柱齿轮啮合,或采用2组输出轴以及位于其上的输出轴圆柱齿轮同时与第一圆柱齿轮和第二圆柱齿轮啮合。Switching an output shaft in the reciprocating incomplete non-circular gearbox and an output shaft spur gear on the output shaft, the output shaft spur gear meshing with the first spur gear or the second spur gear, or The two sets of output shafts and the output shaft spur gears thereon are simultaneously meshed with the first spur gear and the second spur gear.
上述切换往复不完整非圆齿轮变速箱,所述主动切换不完整非圆齿轮的节曲线由二个弧度为60度的变速区、一个弧度为60度的匀速区、一个弧度为180度无齿型区构成;所述主动切换不完整非圆齿轮的节曲线28中的匀速区位于有齿形部分,对应大圆弧R1区域;所述主动切换不完整非圆齿轮的节曲线中的无齿型区31对应小圆弧R2区域;所述主动切换不完整非圆齿轮的中心线通过匀速区中间的一个齿槽;所述主动切换不完整非圆齿轮的齿数是
偶数,齿槽数是奇数;The above-mentioned switching reciprocating incomplete non-circular gear transmission has a pitch curve of two arcs of 60 degrees, a constant velocity zone of 60 degrees, and a toothlessness of 180 degrees. The configuration of the pattern region; the uniform velocity region in the pitch curve 28 of the active switching incomplete non-circular gear is located in the toothed portion corresponding to the large arc R1 region; the toothless curve in the pitch curve of the active switching incomplete non-circular gear The pattern area 31 corresponds to the small arc R2 area; the center line of the active switching incomplete non-circular gear passes through a slot in the middle of the uniform speed zone; the number of teeth of the active switching incomplete non-circular gear is
Even number, the number of slots is odd;
上述切换往复非圆齿轮变速箱,所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的节曲线均由二个角度为60度的变速区、一个弧度为180度的匀速区、一个弧度为60度的无齿型区构成;所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的节曲线中的匀速区位于有齿形部分,对应小圆弧R2区域;所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的节曲线中的无齿形区对应大圆弧R1区域;第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的旋转中心线通过匀速区中段部位的一个轮齿;所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的齿数是奇数,齿槽数则是偶数;In the above-mentioned switching reciprocating non-circular gear transmission, the pitch curves of the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear are both changed by two angles of 60 degrees, and one arc is a constant speed zone of 180 degrees, a toothless zone with a curvature of 60 degrees; the uniform velocity zone in the section curve of the first driven switch incomplete non-circular gear and the second slave switch incomplete non-circular gear is located a tooth-shaped portion corresponding to the small arc R2 region; the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear in the pitch curve corresponding to the large arc R1 region; a first driven switching incomplete non-circular gear and a second driven switching incomplete non-circular gear rotating center line passing through a tooth of a middle portion of the uniform velocity zone; the first driven switching incomplete non-circular gear and the second The number of teeth of the incomplete non-circular gear is odd, and the number of slots is even.
上述切换往复非圆齿轮变速箱,所述主动切换不完整非圆齿轮、第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的旋转中心“O”,是大圆弧R1和小圆弧R2的几何中心;The above-mentioned switching reciprocating non-circular gear transmission, the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear, and the second driven switching incomplete non-circular gear rotating center "O", is a large circle The geometric center of the arc R1 and the small arc R2;
所述主动切换不完整非圆齿轮与第一从动切换不完整非圆齿轮或第二从动切换不完整非圆齿轮啮合运转时,当从动切换不完整非圆齿轮啮合运行至匀速区时,其传动比I符合公式:When the active switching incomplete non-circular gear meshes with the first driven switching incomplete non-circular gear or the second driven switching incomplete non-circular gear, when the driven switching is incomplete non-circular gear meshing operation to the uniform velocity region , its transmission ratio I conforms to the formula:
I=R1/R2,I=R1/R2,
I的取值区间是:最大数值为Imax=R1:最小数值为Imin=1/R1;The value range of I is: the maximum value is Imax=R1: the minimum value is Imin=1/R1;
所述主动切换不完整非圆齿轮变速区的节曲线、第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮变速区的节曲线的数学表达式F(α)均符合公式:The mathematical expression F(α) of the pitch curve of the active switching incomplete non-circular gear shifting section, the first driven switching incomplete non-circular gear, and the second driven switching incomplete non-circular gear shifting section Match the formula:
F(α)=R1*sin(α)/R2;F(α)=R1*sin(α)/R2;
其中:
among them:
R1为主动切换不完整非圆齿轮的节曲线、第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的节曲线的大圆弧区域的半径;R1 is a radius of a large arc area of a pitch curve of the pitch curve of the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear, and the second driven switching incomplete non-circular gear;
R2为主动切换不完整非圆齿轮的节曲线、第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的节曲线的小圆弧区域的半径;R2 is a radius of a small arc area of the pitch curve of the pitch curve of the incomplete non-circular gear that actively switches the incomplete non-circular gear, the first driven switch incomplete non-circular gear, and the second driven switch incomplete non-circular gear;
α为主动切换不完整非圆齿轮的变速区节曲线、第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的变速区节曲线上的任意一点在其各自完整的节曲线坐标系内对应的角度。α is an integral part of the shifting section curve of the active switching incomplete non-circular gear, the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear are in their respective complete The corresponding angle within the curve coordinate system.
上述切换往复不完整非圆齿轮变速箱,所述主动切换不完整非圆齿轮的2个变速区靠近无齿型区的端部各有一个变形切换齿;所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的2个变速区靠近无齿型区的端部各有一个变形切换齿齿槽。Switching the reciprocating incomplete non-circular gear transmission, wherein the two shifting regions of the active switching incomplete non-circular gear have a deformation switching tooth near the end of the edentulous type region; the first slave switching is incomplete The two gear shifting regions of the circular gear and the second driven switching incomplete non-circular gear have a deformation switching tooth groove adjacent to the end portion of the edentulous type region.
上述切换往复不完整非圆齿轮变速箱,所述主动切换不完整非圆齿轮5的变形切换齿的齿厚是与其相邻轮齿齿厚的3倍,变形切换齿的齿全高是与其相邻轮齿齿全高的1.0倍至1.65倍,变形切换齿的齿顶线线段形状和与其相邻的节曲线线段平行,该变形切换齿的齿廓仍是渐开线齿廓。The above-mentioned switching reciprocating incomplete non-circular gear transmission, the tooth thickness of the deformation switching tooth of the active switching incomplete non-circular gear 5 is three times the tooth thickness of the adjacent tooth, and the full height of the tooth of the deformation switching tooth is adjacent thereto The full height of the gear teeth is 1.0 times to 1.65 times, and the shape of the tooth top line segment of the deformation switching tooth is parallel with the adjacent curve line segment, and the tooth profile of the deformation switching tooth is still the involute tooth profile.
上述切换往复不完整非圆齿轮变速箱,所述第一从动切换不完整非圆齿轮和第二从动切换不完整非圆齿轮的变形切换齿齿槽的齿槽厚度是与其相邻的轮齿齿槽厚度的3倍,变形切换齿齿槽的齿槽深度是与其相邻的轮齿齿槽深度的1.0倍至1.75倍,变形切换齿齿槽的齿根线的线段形状和与其相邻的节曲线线段平行。The above-mentioned switching reciprocating incomplete non-circular gear transmission, the first driven switching incomplete non-circular gear and the second driven switching incomplete non-circular gear, the deformation of the cogging groove has a cogging thickness which is adjacent to the wheel 3 times the thickness of the tooth groove, the tooth groove depth of the deformation switching tooth groove is 1.0 times to 1.75 times the tooth groove depth of the adjacent tooth tooth, and the shape of the line segment of the root line of the deformation switching tooth groove is adjacent thereto The section line segments are parallel.
本发明还提出的一种传动机构,所述一种传动机构,包括:The invention also provides a transmission mechanism, the transmission mechanism comprising:
上述切换往复不完整非圆齿轮变速箱;第三传动轴以及位于其上的第三圆柱齿轮;第四传动轴以及位于其上的第四圆柱齿轮;还包括联轴器、
链轮系、皮带轮系、圆柱齿轮系;Switching the reciprocating incomplete non-circular gearbox; the third drive shaft and the third spur gear located thereon; the fourth drive shaft and the fourth spur gear located thereon; further comprising a coupling,
Sprocket system, pulley system, cylindrical gear system;
上述切换往复不完整非圆齿轮变速箱的输入轴可与链轮、皮带轮、各类齿轮机构中的一个或多个的组合通过联轴器连接后实施动力输入;The input shaft of the above-mentioned switching reciprocating incomplete non-circular gearbox can be connected with a coupling of one or more of a sprocket, a pulley, and various gear mechanisms through a coupling to implement a power input;
上述切换往复不完整非圆齿轮变速箱的输出轴通过联轴器与第三传动轴以及位于其上的第三圆柱齿轮、第四传动轴以及位于其上的第四圆柱齿轮连接,从而实现动力输出;The output shaft of the above-mentioned switching reciprocating incomplete non-circular gear transmission is connected to the third transmission shaft and the third spur gear, the fourth transmission shaft and the fourth spur gear located thereon through the coupling, thereby realizing the power Output
上述切换往复不完整非圆齿轮变速箱的输出轴通过联轴器还可与链轮系、皮带轮系或链轮、皮带轮、圆柱齿轮系中之一或组合连接,从而实现动力输出。The output shaft of the above-mentioned switching reciprocating incomplete non-circular gear transmission can also be connected to one or a combination of a sprocket system, a pulley train or a sprocket, a pulley, a cylindrical gear train through a coupling, thereby realizing power output.
本发明还进一步提出了一种立式抽油机,所述立式抽油机的抽油杆上下往复的换向机构是安装了上述的一种传动机构。The present invention further provides a vertical pumping unit in which the reversing mechanism of the sucker rod of the vertical pumping unit is mounted with the above-mentioned transmission mechanism.
本发明的上述技术方案与现有技术相比具有以下优点:The above technical solution of the present invention has the following advantages compared with the prior art:
现有立式抽油机是长年累月全天候的在野外作业的一种采油机械,其抽油杆上下行程的换向是依靠电机变频装置完成的,这种电机变频装置内的电器元部件无法长期承受高温、低温、刮风、下雨、下雪、打雷、闪电造成的恶劣工况,在我国一次性使用寿命最长的也仅仅一年多,使这种与游梁式抽油机相比具有节能优势的立式抽油机在各地的广泛推广受得了严重阻碍。与此相反,本发明核心技术“切换往复不完整非圆齿轮变速箱”的几乎所有零部件均由金属制成,尤其是关键传动零件均由齿轮构成,彻底摒弃了对温度、湿度、磁场等最为敏感的电器元器件,先天性的具备了在各种恶劣工况下工作的刚度、强度和可靠性,从而彻底扭转了立式抽油机在全天候工况下短寿命不可靠的劣势状态,使立式抽油机具备了无可替代的高寿命、高可靠性的技术优势;The existing vertical pumping unit is a kind of oil recovery machine that works in the field for many years. The commutation of the upper and lower strokes of the sucker rod is completed by the motor frequency conversion device. The electrical components in the motor frequency conversion device cannot be sustained for a long time. The harsh conditions caused by high temperature, low temperature, wind, rain, snow, thunder, lightning, and the longest one-time service life in China are only more than one year, which makes this kind of comparison with the beam pumping unit. The wide-scale promotion of vertical pumping units with energy-saving advantages has been seriously hindered. In contrast, almost all the components of the core technology of the present invention "switching the reciprocating incomplete non-circular gearbox" are made of metal, especially the key transmission parts are composed of gears, completely eliminating the temperature, humidity, magnetic field, etc. The most sensitive electrical components, congenitally have the rigidity, strength and reliability of working under various harsh conditions, thus completely reversing the short-life unreliable disadvantage of the vertical pumping unit under all-weather conditions. The vertical pumping unit has the technical advantages of irreplaceable high life and high reliability;
立式抽油机上下行程中有变速要求,抽油杆端部接近上下行程端点时,要逐渐减速至零速,并迅速换向,再逐渐加速至正常速度,这一技术要求在现有
立式抽油机上是依靠变频器里储存的程序和电器元器件完成的,对全天候仍然存在难以适应的弱点和由此产生的频发的设备故障。本发明的核心技术之一就是将立式抽油机抽油杆的运动规律固化在齿轮的形状和齿形上,使其在旋转运动中准确的实现主机运动要求,完全不受任何恶劣天气和长期使用的影响,具备了变速稳定、准确、安全、可靠的技术优势。The vertical pumping unit has the shifting requirement in the up and down stroke. When the end of the sucker rod is close to the end of the up and down stroke, it is gradually decelerated to zero speed, and it is quickly reversed, and then gradually accelerates to the normal speed. This technical requirement is existing.
The vertical pumping unit is completed by the programs and electrical components stored in the inverter, and there are still weak points that are difficult to adapt and the frequent equipment failures that occur throughout the day. One of the core technologies of the present invention is to solidify the motion law of the sucker rod of the vertical pumping unit on the shape and the tooth shape of the gear, so that the movement requirement of the main machine can be accurately realized in the rotary motion, and is completely free from any bad weather and The long-term use has the technical advantage of stable, accurate, safe and reliable shifting.
现有立式抽油机采用的电机变频技术,制造成本较高,对采油厂的操作人员提出了较高的技术水平要求。与此相反,本发明技术由于采用了成熟的齿轮制造方案,而且从主机设计阶段就彻底消除了立式抽油机故障率高的先天原因,使立式抽油机的制造成本和使用成本大大降低;The motor frequency conversion technology adopted by the existing vertical pumping unit has high manufacturing cost and puts forward a high technical level requirement for the operator of the oil production plant. In contrast, the technology of the present invention adopts a mature gear manufacturing scheme, and completely eliminates the innate cause of the high failure rate of the vertical pumping unit from the host design stage, so that the manufacturing cost and the use cost of the vertical pumping unit are greatly increased. reduce;
由于本发明技术采用了非圆齿轮制造技术,巧妙的利用非圆齿轮的偏心结构,并将其非圆齿轮偏心的重力势能转化成使抽油杆向上的动能,使本发明技术具备了节省能源的技术特征。这一节能技术优势在现有的立式抽油机中是完全不具备的。Since the technology of the present invention adopts the non-circular gear manufacturing technology, the eccentric structure of the non-circular gear is skillfully utilized, and the eccentric gravitational potential energy of the non-circular gear is converted into the kinetic energy of the sucker rod upward, so that the technology of the present invention saves energy. Technical characteristics. This energy-saving technology advantage is completely absent in the existing vertical pumping unit.
图1是本发明的一种切换往复不完整非圆齿轮变速箱的简图;1 is a schematic view of a switching reciprocating incomplete non-circular gearbox of the present invention;
图2是图1中切换往复不完整非圆齿轮变速箱的主动切换不完整非圆齿轮5顺时针旋转在起始0度时的状态图;2 is a state diagram of the active switching of the incomplete non-circular gearbox of FIG. 1 in the clockwise rotation of the incomplete non-circular gear 5 at the initial 0 degree;
图3是图1中切换往复不完整非圆齿轮变速箱的主动切换不完整非圆齿轮5顺时针旋转在180度时的状态图;3 is a view showing a state in which the active switching incomplete non-circular gear 5 of the reciprocating incomplete non-circular gear transmission of FIG. 1 rotates clockwise at 180 degrees;
图4是主动切换不完整非圆齿轮5向第二从动切换不完整非圆齿轮6切换的瞬时状态;4 is an instantaneous state in which the active switching incomplete non-circular gear 5 is switched to the second driven switching incomplete non-circular gear 6;
图5是第二从动切换不完整非圆齿轮6逆时针旋转时输出转速由慢到快旋转过程中的一个瞬时状态;
Figure 5 is a transient state of the output rotation speed from the slow to the fast rotation when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
图6是第二从动切换不完整非圆齿轮6逆时针旋转时输出转速匀速、快速旋转过程中的一个瞬时状态;6 is a transient state of the output speed constant speed and rapid rotation when the second slave switches the incomplete non-circular gear 6 to rotate counterclockwise;
图7是第二从动切换不完整非圆齿轮6逆时针旋转时输出转速由快到慢旋转过程中的一个瞬时状态;Figure 7 is a transient state of the output rotation speed from the fast to the slow rotation when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
图8是主动切换不完整非圆齿轮5向第一从动切换不完整非圆齿轮4切换的瞬时状态;8 is an instantaneous state in which the active switching incomplete non-circular gear 5 is switched to the first driven switching incomplete non-circular gear 4;
图9是第一从动切换不完整非圆齿轮4逆时针旋转时输出转速由慢到快旋转过程中的一个瞬时状态;Figure 9 is a transient state of the output rotation speed from the slow to the fast rotation when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图10示出了第一从动切换不完整非圆齿轮4逆时针旋转时输出转速匀速、快速旋转过程中的一个瞬时状态;Figure 10 is a view showing an instantaneous state in which the output rotational speed is constant and the rapid rotation is performed when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图11示出了第一从动切换不完整非圆齿轮4逆时针旋转时输出转速由快到慢旋转过程中的一个瞬时状态;Figure 11 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图12是主动切换不完整非圆齿轮5再次向第二从动切换不完整非圆齿轮6切换的瞬间,又一次新的往复切换旋向的运动开始了;FIG. 12 is an instant when the active switching incomplete non-circular gear 5 is switched to the second driven switching incomplete non-circular gear 6 again, and another new reciprocating switching direction is started;
图13是本发明的另一种切换往复不完整非圆齿轮变速箱的简图;Figure 13 is a schematic view of another switching reciprocating incomplete non-circular gearbox of the present invention;
图14是本发明的又一种切换往复不完整非圆齿轮变速箱的简图;Figure 14 is a schematic view of still another switching reciprocating incomplete non-circular gearbox of the present invention;
图15是本发明的第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线33和速度分布区域;15 is a section curve 33 and a velocity distribution area of the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6 of the present invention;
图16是本发明的主动切换不完整非圆齿轮5的节曲线28和速度分布区域;Figure 16 is a section curve 28 and a velocity distribution area of the active switching incomplete non-circular gear 5 of the present invention;
图17是本发明的主动切换不完整非圆齿轮5、第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的变形切换齿轮齿和变形切换齿齿槽;17 is a schematic switching incomplete non-circular gear 5 of the present invention, a first driven switching incomplete non-circular gear 4, a second driven switching incomplete non-circular gear 6 deformation switching gear teeth and a deformation switching tooth groove;
图18是图1所示切换往复不完整非圆齿轮变速箱附加上其输入、输出传动机构的简图;
Figure 18 is a schematic view showing the input and output transmission mechanism of the switching reciprocating incomplete non-circular gear transmission shown in Figure 1;
图19是安装了本发明切换往复不完整非圆齿轮变速箱及其传动机构的立式抽油机的简图;Figure 19 is a schematic view of a vertical pumping unit equipped with the switching reciprocating incomplete non-circular gear transmission of the present invention and its transmission mechanism;
图中,1-输入轴,2-第一传动轴,3-第二传动轴,4-第一从动切换不完整非圆齿轮,5-主动切换不完整非圆齿轮,6-第二从动切换不完整非圆齿轮,7-第二圆柱齿轮,8-第一圆柱齿轮,9-输出轴圆柱齿轮,10-输出轴,11-箱体,12-箱盖,13-第三圆柱齿轮,14-第四圆柱齿轮,15-第四传动轴,16-第五传动轴,17-皮带轮,18-第六输入轴,19-皮带轮,20-皮带,21-第三传动轴,22-电机,23-机架,24-抽油杆,25-皮带,26-平衡重,27-滚筒,28-主动切换不完整非圆齿轮的节曲线、29-主动切换不完整非圆齿轮的变速区、30-主动切换不完整非圆齿轮的匀速区、31-主动切换不完整非圆齿轮的无齿型区、32-主动切换不完整非圆齿轮变速区的节曲线F(α);33-从动切换不完整非圆齿轮的节曲线、34-从动切换不完整非圆齿轮的变速区节曲线F(α)、35-从动切换不完整非圆齿轮的变速区、36-从动切换不完整非圆齿轮的无齿型区、37-从动切换不完整非圆齿轮的匀速区;38-变形切换齿齿槽,39-变形切换齿,40-切换往复不完整非圆齿轮变速箱及减速机;In the figure, 1-input shaft, 2-first transmission shaft, 3-second transmission shaft, 4-first driven switching incomplete non-circular gear, 5-active switching incomplete non-circular gear, 6-second slave Inverted non-round gear, 7-second spur gear, 8-first spur gear, 9-output shaft spur gear, 10-output shaft, 11-box, 12-box cover, 13-third spur gear , 14-fourth cylindrical gear, 15-fourth transmission shaft, 16-fifth transmission shaft, 17-pulley, 18-sixth input shaft, 19-pulley, 20-belt, 21-third transmission shaft, 22- Motor, 23-rack, 24-sucker rod, 25-belt, 26-balance weight, 27-roller, 28-active switching incomplete non-circular gear section curve, 29-active switching incomplete non-circular gear shifting Zone, 30-active switching unsteady non-circular gear uniform velocity zone, 31-active switching incomplete non-circular gear toothless zone, 32-active switching incomplete non-circular gear shifting zone curve F(α); 33 - Slave switching incomplete non-circular gear section curve, 34-slave switching incomplete non-circular gear shifting section curve F(α), 35-slave switching incomplete non-circular gear shifting zone, 36-slave move Switching the non-toothed zone of the incomplete non-circular gear, 37-slave switching the uniform velocity zone of the incomplete non-circular gear; 38-deformation switching tooth groove, 39-deformation switching tooth, 40-switching reciprocating incomplete non-circular gear shifting Box and reducer;
本发明所述的一种切换往复不完整非圆齿轮变速箱(图1)及其传动机构(图18),可以提供输入轴连续旋转输出轴按顺时针、逆时针或逆时针、顺时针的旋转规律往复切换旋向旋转输出的功能(图1、图2、图3)。The utility model relates to a switching reciprocating incomplete non-circular gearbox (Fig. 1) and a transmission mechanism thereof (Fig. 18), which can provide an input shaft continuous rotation output shaft in a clockwise, counterclockwise or counterclockwise, clockwise manner The rotation law reciprocally switches the function of the rotary rotation output (Fig. 1, Fig. 2, Fig. 3).
作为一个实施例,我们将其安装在石油钻采行业的立式抽油机上(图19),实现了换向可靠、精确便捷,大幅度提高了立式抽油机的性能。下面我们结合该实施例对本发明做更进一步的详细描述。As an example, we installed it on the vertical pumping unit of the oil drilling industry (Fig. 19), which achieved reliable commutation, accuracy and convenience, and greatly improved the performance of the vertical pumping unit. The invention will be further described in detail below with reference to this embodiment.
切换往复不完整非圆齿轮变速箱的具体实施方式:
Specific implementation of switching a reciprocating incomplete non-circular gearbox:
图1示出了切换往复不完整非圆齿轮变速箱是由输入轴1以及位于该输入轴1上的主动切换不完整非圆齿轮5、第一传动轴2以及位于该第一传动轴2上的第一从动切换不完整非圆齿轮4和第一圆柱齿轮8、第二传动轴3以及位于该第二传动轴3上的第二从动切换不完整非圆齿轮6和第二圆柱齿轮7、输出轴10以及位于该输出轴10上的输出轴圆柱齿轮9、箱体11、箱盖12等零部件构成的。1 shows that the switching reciprocating incomplete non-circular gearbox is an input shaft 1 and an active switching incomplete non-circular gear 5 on the input shaft 1, a first transmission shaft 2, and on the first transmission shaft 2 The first driven switching incomplete non-circular gear 4 and the first spur gear 8, the second transmission shaft 3, and the second driven switching incomplete non-circular gear 6 and the second spur gear on the second transmission shaft 3 7. The output shaft 10 and the output shaft spur gear 9, the casing 11, and the cover 12 on the output shaft 10 are composed of components.
同时,图1也示出了使这种切换往复不完整非圆齿轮变速箱的输出轴10、第一传动轴2、第二传动轴3能够往复切换旋向的重要功能齿轮组即变形切换齿轮组的构成,它是由1个主动齿轮也就是主动切换不完整非圆齿轮5和2个从动切换不完整非圆齿轮也就是第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6所构成的。主动切换不完整非圆齿轮5是安装在输入轴1之上,第一从动切换不完整非圆齿轮4是安装在第一传动轴2之上,第二从动切换不完整非圆齿轮6安装在第二传动轴3之上,这2个从动切换不完整非圆齿轮分别安装在主动切换不完整非圆齿轮5的两边且并排啮合安装。Meanwhile, FIG. 1 also shows an important function gear set, that is, a deformation switching gear, which can make the output shaft 10, the first transmission shaft 2, and the second transmission shaft 3 of the switching reciprocating incomplete non-circular gear transmission reciprocally switch. The composition of the group, which is driven by a driving gear, that is, the active switching of the incomplete non-circular gear 5 and the two driven switching incomplete non-circular gears, that is, the first driven switching incomplete non-circular gear 4, the second driven Switching is made up of incomplete non-circular gears 6. The active switching incomplete non-circular gear 5 is mounted on the input shaft 1, the first driven switching incomplete non-circular gear 4 is mounted on the first transmission shaft 2, and the second driven switching incomplete non-circular gear 6 Mounted on the second transmission shaft 3, the two driven switching incomplete non-circular gears are respectively mounted on both sides of the active switching incomplete non-circular gear 5 and are mounted side by side.
图1还示出了第一从动切换不完整非圆齿轮4与第一圆柱齿轮8同轴安装并同轴动力连接,第二从动切换不完整非圆齿轮6与第二圆柱齿轮7同轴安装并同轴动力连接,其中,第二圆柱齿轮7与第一圆柱齿轮8相互啮合安装,安装在输出轴10之上的输出轴圆柱齿轮9则与第一圆柱齿轮8相互啮合并向切换往复不完整非圆齿轮变速箱之外传输往复切换旋向的旋转运动。FIG. 1 also shows that the first driven switching incomplete non-circular gear 4 is coaxially mounted and coaxially connected with the first spur gear 8, and the second driven switching incomplete non-circular gear 6 is the same as the second spur gear 7. The shaft is mounted and coaxially coupled, wherein the second spur gear 7 and the first spur gear 8 are in meshing engagement, and the output shaft spur gear 9 mounted on the output shaft 10 is meshed with the first spur gear 8 and is switched The reciprocating incomplete non-circular gear transmission transmits a rotary motion of the reciprocating switching direction.
图2示出了安装完毕后的这种切换往复不完整非圆齿轮变速箱工作时主动切换不完整非圆齿轮5在0度时的状态图:Figure 2 shows the state diagram of the active switching of the incomplete non-circular gear 5 at 0 degrees when the switching reciprocating incomplete non-circular gearbox is in operation after installation:
当主动切换不完整非圆齿轮5顺时针旋转并开始与第二从动切换不完整非圆齿轮6的有齿形部分进入相互啮合时,第二从动切换不完整非圆齿轮6与同轴动力连接的第二圆柱齿轮7开始作逆时针旋转,与第二圆柱齿轮7啮合的第一圆
柱齿轮8以及与第一圆柱齿轮8同轴动力连接的第一从动切换不完整非圆齿轮4做顺时针旋转,与顺时针旋转的第一圆柱齿轮8相互啮合的圆柱齿轮9则和动力连接的输出轴10同时做逆时针旋转。当主动切换不完整非圆齿轮5与从动切换不完整非圆齿轮6啮合并顺时针旋转了180度时,第二传动轴3和位于其上的第二从动切换不完整非圆齿轮6和第二圆柱齿轮7、输出轴10以及位于其上的输出轴圆柱齿轮9逆时针旋转了一次,第一传动轴2以及位于其上的第一从动切换不完整非圆齿轮4、第一圆柱齿轮8则顺时针旋转了一次。When the active switching incomplete non-circular gear 5 rotates clockwise and begins to intermesh with the toothed portion of the second driven switching incomplete non-circular gear 6, the second driven switch is incomplete non-circular gear 6 and coaxial The second cylindrical gear 7 of the power connection starts to rotate counterclockwise, and the first circle meshes with the second spur gear 7
The column gear 8 and the first driven switching incomplete non-circular gear 4 coaxially connected to the first spur gear 8 are rotated clockwise, and the spur gear 9 meshing with the clockwise rotating first spur gear 8 and the power The connected output shaft 10 simultaneously rotates counterclockwise. When the active switching incomplete non-circular gear 5 meshes with the driven switching incomplete non-circular gear 6 and rotates 180 degrees clockwise, the second transmission shaft 3 and the second driven switching incomplete non-circular gear 6 located thereon And the second spur gear 7, the output shaft 10 and the output shaft spur gear 9 located thereon rotate counterclockwise once, the first transmission shaft 2 and the first driven switching incomplete non-circular gear 4 located thereon, the first The spur gear 8 is rotated clockwise once.
图3示出了主动切换不完整非圆齿轮5在180度时的状态图:Figure 3 shows a state diagram of actively switching the incomplete non-circular gear 5 at 180 degrees:
当主动切换不完整非圆齿轮5继续顺时针旋转并开始与第一从动切换不完整非圆齿轮4的有齿形部分进入相互啮合时,第一从动切换不完整非圆齿轮4与同轴动力连接的第一圆柱齿轮8均作逆时针旋转,与第一圆柱齿轮8啮合的第二圆柱齿轮7以及与第一圆柱齿轮7同轴动力连接的第二从动切换不完整非圆齿轮6做顺时针旋转,与逆时针旋转的第一圆柱齿轮8相互啮合的输出轴圆柱齿轮9则与动力连接的输出轴10同时做顺时针旋转,当主动切换不完整非圆齿轮5与第一从动切换不完整非圆齿轮4啮合并顺时针继续旋转了180度后,第二传动轴3以及位于其上的第二从动切换不完整非圆齿轮6和第二圆柱齿轮7、输出轴10和位于其上的输出轴圆柱齿轮9顺时针旋转了一次,第一传动轴2以及位于其上的第一从动切换不完整非圆齿轮4、第一圆柱齿轮8则逆时针旋转了一次。When the active switching incomplete non-circular gear 5 continues to rotate clockwise and begins to intermesh with the toothed portion of the first driven switching incomplete non-circular gear 4, the first driven switching incomplete non-circular gear 4 is the same The first spur gear 8 of the shaft power connection rotates counterclockwise, the second spur gear 7 meshing with the first spur gear 8 and the second driven switching incomplete non-circular gear coaxially connected with the first spur gear 7 6 clockwise rotation, the output shaft spur gear 9 meshing with the counterclockwise rotating first spur gear 8 simultaneously rotates clockwise with the power output output shaft 10, when actively switching the incomplete non-circular gear 5 and the first After the driven switching incomplete non-circular gear 4 meshes and continues to rotate 180 degrees clockwise, the second transmission shaft 3 and the second driven switching incomplete non-circular gear 6 and the second spur gear 7 and the output shaft thereon 10 and the output shaft spur gear 9 located thereon rotates clockwise once, and the first transmission shaft 2 and the first driven switching incomplete non-circular gear 4 and the first spur gear 8 thereon are rotated counterclockwise once. .
图4示出了主动切换不完整非圆齿轮5向第二从动切换不完整非圆齿轮6切换的瞬时状态;4 shows an instantaneous state in which the active switching of the incomplete non-circular gear 5 to the second driven switching incomplete non-circular gear 6 is switched;
图5示出了第二从动切换不完整非圆齿轮6逆时针旋转时输出转速由慢到快旋转过程中的一个瞬时状态;Figure 5 is a diagram showing an instantaneous state in which the output rotational speed is rotated from slow to fast when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
图6示出了第二从动切换不完整非圆齿轮6逆时针旋转时输出转速匀速、快
速旋转过程中的一个瞬时状态;Figure 6 shows that the second driven switching incompletely non-circular gear 6 rotates counterclockwise and the output speed is uniform and fast.
a transient state during rapid rotation;
图7示出了第二从动切换不完整非圆齿轮6逆时针旋转时输出转速由快到慢旋转过程中的一个瞬时状态;Figure 7 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the second driven switching incomplete non-circular gear 6 rotates counterclockwise;
图8示出了主动切换不完整非圆齿轮5向第一从动切换不完整非圆齿轮4切换的瞬时状态;FIG. 8 shows an instantaneous state in which the active switching of the incomplete non-circular gear 5 is switched to the first driven switching incomplete non-circular gear 4;
图9示出了第一从动切换不完整非圆齿轮4逆时针旋转时输出转速由慢到快旋转过程中的一个瞬时状态;Figure 9 is a view showing an instantaneous state in which the output rotational speed is rotated from slow to fast when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图10示出了第一从动切换不完整非圆齿轮4逆时针旋转时输出转速匀速、快速旋转过程中的一个瞬时状态;Figure 10 is a view showing an instantaneous state in which the output rotational speed is constant and the rapid rotation is performed when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图11示出了第一从动切换不完整非圆齿轮4逆时针旋转时输出转速由快到慢旋转过程中的一个瞬时状态;Figure 11 is a view showing an instantaneous state in which the output rotational speed is rotated from fast to slow when the first driven switching incomplete non-circular gear 4 rotates counterclockwise;
图12示出了主动切换不完整非圆齿轮5再次向第二从动切换不完整非圆齿轮6切换的瞬间,又一次新的输出往复切换旋向的旋转运动开始了。Fig. 12 shows the moment when the active switching incomplete non-circular gear 5 is switched to the second driven switching incomplete non-circular gear 6 again, and the new output reciprocating switching rotary rotational motion starts again.
图13示出了本发明的另一种切换往复不完整非圆齿轮变速箱:当主机不需要第一传动轴2或第二传动轴3的转速进行变化时,可以去除输出轴10和位于其上的输出轴圆柱齿轮9,直接采用第一传动轴2或第二传动轴3作为输出轴,这样仍可达到输出往复切换旋向的旋转运动的目的。Figure 13 illustrates another switching reciprocating incomplete non-circular gearbox of the present invention: when the main engine does not require a change in the rotational speed of the first drive shaft 2 or the second drive shaft 3, the output shaft 10 can be removed and located therein The upper output shaft spur gear 9 directly adopts the first transmission shaft 2 or the second transmission shaft 3 as an output shaft, so that the purpose of outputting the rotary motion of the reciprocating switching rotation direction can still be achieved.
图14示出了本发明的又一种切换往复不完整非圆齿轮变速箱:当主机需要在所述切换往复不完整非圆齿轮变速箱内再添加一个或若干个输出轴时,我们可以再增加一套或几套“输出轴10以及位于输出轴10之上的输出轴圆柱齿轮9”,并且使新增添的输出轴圆柱齿轮9与箱体内原有的输出轴圆柱齿轮9或第二圆柱齿轮7相互啮合,构成由第一传动轴2、第二传动轴3、一个或多个输出轴10共同组成的多轴多位置输出往复切换旋转方向的输出功能。
Figure 14 shows still another switching reciprocating incomplete non-circular gearbox of the present invention: when the main engine needs to add one or more output shafts in the switching reciprocating incomplete non-circular gearbox, we can One or more sets of "output shaft 10 and output shaft spur gear 9 above output shaft 10" are added, and the newly added output shaft spur gear 9 and the original output shaft spur gear 9 or second cylinder in the casing are added. The gears 7 mesh with each other to form an output function of the multi-axis multi-position output reciprocating switching rotation direction composed of the first transmission shaft 2, the second transmission shaft 3, and one or more output shafts 10.
主动切换不完整非圆齿轮5和第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的具体实施方法:The specific implementation method of actively switching the incomplete non-circular gear 5 and the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6 is as follows:
图2和图3还示出了主动切换不完整非圆齿轮5和第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6在切换往复不完整非圆齿轮变速箱内装配完毕后的排列状态。2 and 3 also show the active switching of the incomplete non-circular gear 5 and the first driven switching incomplete non-circular gear 4, and the second driven switching incomplete non-circular gear 6 in the switching reciprocating incomplete non-circular gear shifting Arrangement status after assembly in the box.
图15和图16分别示出了第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6、主动切换不完整非圆齿轮5的节曲线形态,它们是由大圆弧R1和小圆弧R2以及位于R1、R2之间的变速区节曲线组成的;15 and FIG. 16 respectively show the pitch curve patterns of the first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6, and the actively switching incomplete non-circular gear 5, which are large The arc R1 and the small arc R2 and the shifting section curve between R1 and R2 are composed;
图15还示出了第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线33均由二个角度为60度的变速区35、一个弧度为180度的匀速区37、一个弧度为60度的无齿型区36构成;该第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线33中的匀速区37位于有齿形部分,对应小圆弧R2区域。同时该从第一动变形切换齿轮4、第二从动切换不完整非圆齿轮6的节曲线33中的无齿形区36对应大圆弧R1区域;按照上述节曲线加工完毕的第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的旋转中心线通过匀速区37中段部位的一个轮齿,而且第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的齿数是奇数,齿槽数则是偶数。Figure 15 also shows that the first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6 has a pitch curve 33 of two shifting zones 35 having an angle of 60 degrees, and an arc of 180 a uniform velocity zone 37, a dentless zone 36 having a curvature of 60 degrees; the first driven switching incomplete non-circular gear 4, the second driven switching incomplete curve of the incomplete non-circular gear 6 The zone 37 is located in the toothed portion corresponding to the small arc R2 region. At the same time, the non-toothed area 36 in the pitch curve 33 of the first dynamic deformation switching gear 4 and the second driven switching incomplete non-circular gear 6 corresponds to the large arc R1 area; the first slave processed according to the above-mentioned section curve Dynamically switching the incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6 has a rotation center line passing through one of the teeth of the middle portion of the constant velocity zone 37, and the first driven switching incomplete non-circular gear 4, the second The number of teeth of the incompletely non-circular gear 6 is odd, and the number of slots is even.
图16则示出了主动切换不完整非圆齿轮5的节曲线28是由二个弧度为60度的变速区29、一个弧度为60度的匀速区30、一个弧度为180度无齿型区31构成;该主动切换不完整非圆齿轮5的节曲线28中的匀速区30位于有齿形部分,对应大圆弧R1区域。同时该主动切换不完整非圆齿轮5的节曲线28中的无齿型区31对应小圆弧R2区域;按照上述节曲线加工完毕的主动切换不完整非圆齿轮5的旋转中心线通过匀速区30中间的一个齿槽,而且主动切换不完整非圆齿轮5的齿数是偶
数,齿槽数是奇数。Figure 16 shows that the pitch curve 28 of the active switching incomplete non-circular gear 5 is composed of two shifting zones 29 having a curvature of 60 degrees, a uniform velocity zone 30 having an arc of 60 degrees, and a lenticular zone of a curvature of 180 degrees. 31. The uniform velocity zone 30 in the pitch curve 28 of the active switching incomplete non-circular gear 5 is located in the toothed portion corresponding to the large arc R1 region. At the same time, the non-toothed area 31 in the pitch curve 28 of the active non-revolving non-circular gear 5 corresponds to the small arc R2 area; the active center of the incomplete non-circular gear 5 processed according to the above-mentioned section curve passes through the uniform speed zone. a cogging in the middle of 30, and actively switching the number of teeth of the incomplete non-circular gear 5 is even
Number, the number of slots is odd.
图15和图16进一步示出:主动切换不完整非圆齿轮5与第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线形态是相似的,但其各区域参数数值却不是完全相同的。由于所述切换往复不完整非圆齿轮变速箱负载变化形式和运动要求具有多样性,因此主动切换不完整非圆齿轮5的节曲线28和第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线33也具有多样性,同时也就决定了主动切换不完整非圆齿轮5和第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6也具有多样性。15 and FIG. 16 further show that the active switching of the incomplete non-circular gear 5 is similar to that of the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6, but The values of their regional parameters are not identical. Since the switching reciprocating incomplete non-circular gearbox has a variety of load variations and motion requirements, the pitch curve 28 of the incompletely non-circular gear 5 and the first slave switching incomplete non-circular gear 4 and the second are actively switched. The pitch curve 33 of the driven incompletely non-circular gear 6 also has diversity, and also determines the active switching of the incomplete non-circular gear 5 and the first driven switching incomplete non-circular gear 4, and the second driven switching is not The complete non-circular gear 6 is also versatile.
图15和图16还进一步示出了主动切换不完整非圆齿轮和从动切换不完整非圆齿轮的设计原理和方法,可以看出主动切换不完整非圆齿轮5或第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的旋转中心“O”,是大圆弧R1和小圆弧R2的几何中心;15 and FIG. 16 further illustrate the design principle and method of actively switching the incomplete non-circular gear and the driven switching incomplete non-circular gear. It can be seen that the active switching incomplete non-circular gear 5 or the first driven switching is not The complete non-circular gear 4, the second driven switching incomplete non-circular gear 6 has a center of rotation "O", which is the geometric center of the large arc R1 and the small arc R2;
主动切换不完整非圆齿轮5与第一从动切换不完整非圆齿轮4或第二从动切换不完整非圆齿轮6啮合运转时,当从动切换不完整非圆齿轮啮合运行至匀速区时,其传动比I符合公式:When the active switching incomplete non-circular gear 5 is meshed with the first driven switching incomplete non-circular gear 4 or the second driven switching incomplete non-circular gear 6, when the driven switching is incomplete non-circular gear meshing operation to the uniform velocity region When the transmission ratio I meets the formula:
I=R1/R2,I=R1/R2,
I的取值区间是:最大数值为Imax=R1,最小数值为Imin=1/R1;The value range of I is: the maximum value is Imax=R1, and the minimum value is Imin=1/R1;
所述主动切换不完整非圆齿轮5的变速区29的节曲线32或第一从动切换不完整非圆齿轮4、第二从The pitch curve 32 of the shifting zone 29 of the active switching incomplete non-circular gear 5 or the first driven switching incomplete non-circular gear 4, the second slave
动变形切换齿轮6的变速区35的节曲线34的数学表达式F(α)符合公式:The mathematical expression F(α) of the pitch curve 34 of the shifting region 35 of the dynamic deformation switching gear 6 conforms to the formula:
F(α)=R1*sin(α)/R2;F(α)=R1*sin(α)/R2;
其中:among them:
R1为主动切换不完整非圆齿轮5的节曲线28或从第一动变形切换齿轮4、第
二从动切换不完整非圆齿轮6的节曲线33的大圆弧区域的半径;R1 is a pitch curve 28 for actively switching the incomplete non-circular gear 5 or switching the gear 4 from the first dynamic deformation,
The second slave switches the radius of the large arc area of the node curve 33 of the incomplete non-circular gear 6;
R2为主动切换不完整非圆齿轮5的节曲线28或第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的节曲线33的小圆弧区域的半径;R2 is a radius of a small arc area of the pitch curve 33 of the pitch curve 33 of the first switch or the incomplete non-circular gear 6;
α为主动切换不完整非圆齿轮5的变速区29节曲线32、第一从动切换不完整非圆齿轮4和第二从动切换不完整非圆齿轮6的变速区35节曲线34上的任意一点在其各自完整的节曲线坐标系内对应的角度。α is the shifting zone 29 curve 32 of the active switching incomplete non-circular gear 5, the first driven switching incomplete non-circular gear 4, and the second driven switching incomplete non-circular gear 6 on the shifting section 35 curve 34 The angle at which any point corresponds within its respective complete pitch coordinate system.
图17示出了在数控机床上加工完毕的主动切换不完整非圆齿轮5有2个变速区29,该变速区29靠近无齿型区31的端部各有一个变形切换齿39,在所述第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的2个变速区35靠近无齿型区36的端部各有一个变形切换齿齿槽38;Fig. 17 shows that the active switching incomplete non-circular gear 5 processed on the numerically controlled machine tool has two shifting portions 29, and each of the shifting portions 29 has a deformation switching tooth 39 near the end of the edentulous type region 31. The first driven switching incomplete non-circular gear 4, the second driven switching incomplete non-circular gear 6 of the two shifting regions 35 near the end of the edentulous type region 36 each has a deformation switching tooth groove 38;
加工主动切换不完整非圆齿轮5的变形切换齿39的技术要求是:变形切换齿39的齿厚是与其相邻轮齿齿厚的3倍,变形切换齿39的齿全高是与其相邻轮齿齿全高的1.0倍至1.65倍,变形切换齿39的齿顶线线段形状和与其相邻的节曲线线段平行,该变形切换齿39的齿廓仍是渐开线齿廓;The technical requirement of the deformation switching tooth 39 for actively switching the incomplete non-circular gear 5 is that the tooth thickness of the deformation switching tooth 39 is three times the tooth thickness of the adjacent gear tooth, and the full height of the tooth of the deformation switching tooth 39 is the adjacent wheel thereof. The shape of the top line segment of the deformation switching tooth 39 is parallel to the section curve line adjacent thereto, and the tooth profile of the deformation switching tooth 39 is still an involute profile;
加工第一从动切换不完整非圆齿轮4、第二从动切换不完整非圆齿轮6的变形切换齿齿槽38的技术要求是:变形切换齿齿槽38的齿槽厚度是与其相邻的轮齿齿槽厚度的3倍,变形切换齿齿槽38的齿槽全高是与其相邻的轮齿齿槽全高的1.0倍至1.75倍,变形切换齿齿槽38的齿根线的线段形状和与其相邻的节曲线线段平行。The technical requirement of processing the first driven switching incomplete non-circular gear 4 and the second driven switching incomplete non-circular gear 6 to change the tooth slot 38 is that the tooth gap thickness of the deformation switching tooth groove 38 is adjacent thereto 3 times the thickness of the tooth cogging, the total height of the tooth gap of the deformation switching tooth groove 38 is 1.0 times to 1.75 times the full height of the tooth groove adjacent thereto, and the shape of the line of the tooth root line of the deformation switching tooth groove 38 Parallel to the section line segment adjacent to it.
上述切换不完整非圆齿轮组加工并组装完毕后,即可运转切换往复不完整非圆齿轮变速箱,此时的切换往复不完整非圆齿轮变速箱在顺时针和逆时针两个旋转方向上的输出速度也就具有了从慢到快、匀速快速、从快到慢、再到切换旋向的速度变化特征。
After the above-mentioned switching incomplete non-circular gear set is processed and assembled, the reciprocating incomplete non-circular gear transmission can be operated, and the switching reciprocating incomplete non-circular gear transmission is in two rotation directions: clockwise and counterclockwise. The output speed also has the characteristics of speed change from slow to fast, constant speed, fast to slow, and then to the switching direction.
切换往复不完整非圆齿轮变速箱及其传动机构的实施方法:The implementation method of switching the reciprocating incomplete non-circular gear transmission and its transmission mechanism:
图18所示的切换往复不完整非圆齿轮变速箱及其传动机构是由切换往复不完整非圆齿轮变速箱、与输出轴10或第一传动轴2、第二传动轴3动力连接的第三传动轴21以及位于其上的第三圆柱齿轮13、第四传动轴15以及位于其上的第四圆柱齿轮14、与输入轴1动力连接的第五传动轴16以及位于其上的皮带轮17、第六输入轴18以及位于其上的皮带轮19、位于皮带轮17和皮带轮18之上的皮带20组成;The switching reciprocating incomplete non-circular gear transmission shown in FIG. 18 and its transmission mechanism are powered by switching the reciprocating incomplete non-circular gear transmission, and the output shaft 10 or the first transmission shaft 2 and the second transmission shaft 3 a third transmission shaft 21 and a third spur gear 13 thereon, a fourth transmission shaft 15 and a fourth spur gear 14 located thereon, a fifth transmission shaft 16 that is power-connected to the input shaft 1, and a pulley 17 located thereon a sixth input shaft 18 and a pulley 19 located thereon, a belt 20 located above the pulley 17 and the pulley 18;
图18还示出了第三圆柱齿轮13和第四圆柱齿轮14是相互啮合的关系,第三传动轴21的任意一端,均可采用联轴器与输出轴10或第一传动轴2、第二传动轴3的轴端部实施动力连接。输入轴1与第五传动轴16也是采用联轴器相互连接的;18 also shows that the third spur gear 13 and the fourth spur gear 14 are in meshing relationship, and either end of the third transmission shaft 21 can be used with the coupling and the output shaft 10 or the first transmission shaft 2, The shaft ends of the two transmission shafts 3 are electrically connected. The input shaft 1 and the fifth transmission shaft 16 are also connected to each other by a coupling;
其中,输入轴1还可以与链轮或各类齿轮机构或链轮、皮带轮、各类齿轮机构的任意组合通过联轴器与第五传动轴16实现动力连接;Wherein, the input shaft 1 can also be connected with the sprocket or various gear mechanisms or any combination of sprocket, pulley, and various gear mechanisms through the coupling and the fifth transmission shaft 16;
图18进一步示出了我们可以用一套或多套“第三圆柱齿轮13、第四圆柱齿轮14、第四输出轴15、第三传动轴21”与所述切换往复不完整非圆齿轮变速箱的第一传动轴2或第二传动轴3或输出轴10或同时与第一传动轴2、第二传动轴3、输出轴10的各个轴端实施单轴或多轴的动力连接(如图16中虚线所示),其动力连接的方法是将一个或多个第三传动轴21的轴端通过联轴器与第一传动轴2或第二传动轴3或输出轴10或同时与第一传动轴2、第二传动轴3、输出轴10的各个轴端相连接,即可实现单轴输出往复切换旋向的旋转运动或多轴多位置输出往复切换旋向的旋转运动。该传动机构中的第三圆柱齿轮13、第四圆柱齿轮14还可以用其他链轮或皮带轮或圆柱齿轮系或链轮、皮带轮、圆柱齿轮系的任意组合所替代。Figure 18 further shows that we can use one or more sets of "third spur gear 13, fourth spur gear 14, fourth output shaft 15, third drive shaft 21" and the switching reciprocating incomplete non-circular gear shifting The first transmission shaft 2 or the second transmission shaft 3 or the output shaft 10 of the box or the respective shaft ends of the first transmission shaft 2, the second transmission shaft 3, and the output shaft 10 are simultaneously connected with a single shaft or a plurality of shafts (for example, The power connection is made by passing the shaft end of one or more third transmission shafts 21 through the coupling with the first transmission shaft 2 or the second transmission shaft 3 or the output shaft 10 or simultaneously. The shaft ends of the first transmission shaft 2, the second transmission shaft 3, and the output shaft 10 are connected to realize a single-axis output reciprocating switching rotation motion or a multi-axis multi-position output reciprocating switching rotation motion. The third spur gear 13 and the fourth spur gear 14 in the transmission mechanism can also be replaced by other sprocket or pulley or spur gear train or any combination of sprocket, pulley and spur gear train.
立式抽油机的具体实施方法:
The specific implementation method of the vertical pumping unit:
图19示出的立式抽油机是在现有的立式抽油机的基础上去除该立式抽油机已有的传动和换向机构,保留现有的立式抽油机的机架23、抽油杆24、皮带25、平衡重26、滚筒27等部件,并安装上本发明的切换往复不完整非圆齿轮变速箱及其传动机构,即可构成一种具有切换上下冲程方向的新型立式抽油机。The vertical pumping unit shown in Fig. 19 removes the existing transmission and reversing mechanism of the vertical pumping unit based on the existing vertical pumping unit, and retains the existing vertical pumping unit. The frame 23, the sucker rod 24, the belt 25, the counterweight 26, the drum 27 and the like, and the switching reciprocating incomplete non-circular gear transmission of the present invention and the transmission mechanism thereof can be configured to have a switching up and down stroke direction The new vertical pumping unit.
具体安装方法是:The specific installation method is:
将传动机构中的第五传动轴16的轴端部与切换往复不完整非圆齿轮变速箱的输入轴1的轴端部通过联轴器相连接,将第六传动轴18的轴端部与电机22的轴端部通过联轴器相连接,即可使位于第五传动轴16及第六传动轴18上的链轮或皮带轮或齿轮机构或链轮、皮带轮、齿轮机构的任意组合正常运转,实现立式抽油机的动力输入;The shaft end of the fifth transmission shaft 16 in the transmission mechanism is coupled to the shaft end portion of the input shaft 1 of the switching reciprocating incompletely non-circular gear transmission through the coupling, and the shaft end portion of the sixth transmission shaft 18 is The shaft end of the motor 22 is connected by a coupling, so that any combination of the sprocket or the pulley or the gear mechanism or the sprocket, the pulley and the gear mechanism on the fifth transmission shaft 16 and the sixth transmission shaft 18 can be normally operated. To realize the power input of the vertical pumping unit;
将切换往复不完整非圆齿轮变速箱及其传动机构的输出轴10或第一传动轴2或第二传动轴3的轴端部与第三传动轴21通过联轴器相连接,使位于第三传动轴21之上的第三圆柱齿轮13、位于第四传动轴15之上的第四圆柱齿轮14正确啮合,再将第四传动轴15的轴端部与原立式抽油机的部件滚筒27的轴端部通过联轴器连接,即可实现对立式抽油机的动力传导,并使这种新型立式抽油机正常运转。Connecting the output shaft 10 of the reciprocating incomplete non-circular gear transmission and the transmission mechanism thereof or the shaft end portion of the first transmission shaft 2 or the second transmission shaft 3 to the third transmission shaft 21 through the coupling, so as to be located at the The third spur gear 13 above the three transmission shaft 21, the fourth spur gear 14 above the fourth transmission shaft 15 are correctly meshed, and the shaft end of the fourth transmission shaft 15 and the components of the original vertical pumping unit The shaft end of the drum 27 is connected by a coupling, so that the power transmission of the opposite pumping unit can be realized, and the new vertical pumping unit can be operated normally.
这种安装了切换往复不完整非圆齿轮变速箱及其传动机构的新型立式抽油机,由于其换向机构采用了本发明所述的一种切换往复不完整非圆齿轮变速箱及其传动机构,既保留了立式抽油机上下行程的变速特点又使以往立式抽油机电机变频换向功能易损坏、全天候下长期使用不可靠等技术难点得以克服。The novel vertical pumping unit equipped with the switching reciprocating incomplete non-circular gear transmission and its transmission mechanism adopts a switching reciprocating incomplete non-circular gear transmission according to the invention, and a reversing mechanism thereof The transmission mechanism not only retains the shifting characteristics of the up and down stroke of the vertical pumping unit, but also overcomes the technical difficulties of the conventional vertical pumping unit motor frequency conversion and reversing function, and the long-term unreliable use in all weather.
显然,上述实施例仅仅是为清楚地说明所作的举例,而并非对实施方式的限定。对于所属领域的普通技术人员来说,在上述说明的基础上还可以根据主机设备的不同的需求做出其它不同形式的变化或变动。这里无需也无法对所有
的实施方式予以穷举。而由此所引伸出的显而易见的变化或变动仍处于本发明创造的保护范围之中。
It is apparent that the above-described embodiments are merely illustrative of the examples, and are not intended to limit the embodiments. For those of ordinary skill in the art, other different forms of changes or variations may be made based on the different needs of the host device based on the above description. No need and no for all here
The implementation of the implementation is exhaustive. Obvious changes or variations resulting therefrom are still within the scope of the invention.
Claims (11)
- 一种切换往复不完整非圆齿轮变速箱,包括输入轴(1)以及位于该输入轴(1)上的主动切换不完整非圆齿轮(5)、第一传动轴(2)以及位于该第一传动轴(2)上的第一从动切换不完整非圆齿轮(4)和第一圆柱齿轮(8)、第二传动轴(3)以及位于该第二传动轴(3)上的第二从动切换不完整非圆齿轮(6)和第二圆柱齿轮(7)、箱体(11)和箱盖(12),所述第一从动切换不完整非圆齿轮(4)、第二从动切换不完整非圆齿轮(6)位于所述主动切换不完整非圆齿轮(5)的两边且并排啮合安装,第一从动切换不完整非圆齿轮(4)、第二从动切换不完整非圆齿轮(6)的旋转速度变化是从慢到快、匀速快速、从快到慢、再到切换旋向,当输入轴(1)以及位于其上的主动切换不完整非圆齿轮(5)按照顺时针或逆时针方向每旋转360度时,第一传动轴(2)和第二传动轴(3)则同时按照逆时针、顺时针或顺时针、逆时针的顺序各旋转一次,A switching reciprocating incomplete non-circular gearbox includes an input shaft (1) and an active switching incomplete non-circular gear (5) located on the input shaft (1), a first transmission shaft (2), and a first driven switching incomplete non-circular gear (4) on a drive shaft (2) and a first spur gear (8), a second transmission shaft (3), and a second on the second transmission shaft (3) The second slave switches the incomplete non-circular gear (6) and the second spur gear (7), the box body (11) and the tank cover (12), and the first slave switchover incomplete non-circular gear (4), The second driven switching incomplete non-circular gear (6) is located on both sides of the active switching incomplete non-circular gear (5) and is mounted side by side, the first driven switching incomplete non-circular gear (4), the second driven The rotation speed of the incomplete non-circular gear (6) is changed from slow to fast, constant speed, fast to slow, and then to the switching direction. When the input shaft (1) and the active switching on it are incomplete non-circular When the gear (5) rotates 360 degrees in a clockwise or counterclockwise direction, the first transmission shaft (2) and the second transmission shaft (3) are simultaneously counterclockwise, clockwise or clockwise, counterclockwise. Once each rotation sequence,其特征在于:It is characterized by:主动切换不完整非圆齿轮(5)顺时针旋转并开始与第二从动切换不完整非圆齿轮(6)的有齿形部分进入相互啮合时,第二从动切换不完整非圆齿轮(6)与同轴动力连接的第二圆柱齿轮(7)开始作逆时针旋转,与第二圆柱齿轮(7)啮合的第一圆柱齿轮(8)以及与第一圆柱齿轮(8)同轴动力连接的第一从动切换不完整非圆齿轮(4)做顺时针旋转,当主动切换不完整非圆齿轮(5)与第二从动切换不完整非圆齿轮(6)啮合并顺时针旋转了180度时,第二传动轴(3)以及位于其上的第二从动切换不完整非圆齿轮(6)和第二圆柱齿轮(7)则逆时针旋转了一次,第一传动轴(2)以及位于其上的第一从动切换不完整非圆齿轮(4)、第一圆柱齿轮(8)则顺时针旋转了一次;Actively switching the incomplete non-circular gear (5) to rotate clockwise and begin to intermesh with the toothed portion of the second driven switching incomplete non-circular gear (6), the second driven switch incomplete non-circular gear ( 6) The second spur gear (7) connected to the coaxial power starts to rotate counterclockwise, the first spur gear (8) meshing with the second spur gear (7) and the coaxial power with the first spur gear (8) The first driven switch of the connection is not complete. The non-circular gear (4) rotates clockwise. When the active switch is incomplete, the non-circular gear (5) meshes with the second driven switch incomplete non-circular gear (6) and rotates clockwise. At 180 degrees, the second transmission shaft (3) and the second driven switching incomplete non-circular gear (6) and the second spur gear (7) located thereon are rotated counterclockwise once, the first transmission shaft ( 2) and the first driven switching incomplete non-circular gear (4) located thereon, the first spur gear (8) is rotated clockwise once;当主动切换不完整非圆齿轮(5)继续顺时针旋转并开始与第一从动切换不完整非圆齿轮(4)的有齿形部分进入相互啮合时,第一从动切换不完整非圆齿 轮(4)与同轴动力连接的第一圆柱齿轮(8)均作逆时针旋转,与第一圆柱齿轮(8)啮合的第二圆柱齿轮(7)以及与第二圆柱齿轮(7)同轴动力连接的第二从动切换不完整非圆齿轮(6)做顺时针旋转,当主动切换不完整非圆齿轮(5)与第一从动切换不完整非圆齿轮(4)啮合并顺时针继续旋转了180度时,第二传动轴(3)以及位于其上的第二从动切换不完整非圆齿轮(6)和第二圆柱齿轮(7)顺时针旋转了一次,第一传动轴(2)以及位于其上的第一从动切换不完整非圆齿轮(4)、第一圆柱齿轮(8)则逆时针旋转了一次。When the active switching incomplete non-circular gear (5) continues to rotate clockwise and begins to mesh with the toothed portion of the first driven incomplete non-circular gear (4), the first driven switching is incomplete and non-circular. Tooth The wheel (4) and the first spur gear (8) connected to the coaxial power are rotated counterclockwise, the second spur gear (7) meshing with the first spur gear (8) and the second spur gear (7) The second driven switch of the shaft power connection is not complete. The non-circular gear (6) rotates clockwise. When the active switch is incomplete, the non-circular gear (5) meshes with the first driven switch incomplete non-circular gear (4). When the hour hand continues to rotate 180 degrees, the second transmission shaft (3) and the second driven switching incomplete non-circular gear (6) and the second spur gear (7) located thereon rotate clockwise once, the first transmission The shaft (2) and the first driven switching incomplete non-circular gear (4) located thereon and the first spur gear (8) are rotated counterclockwise once.
- 根据权利要求1所述的切换往复不完整非圆齿轮变速箱,其特征在于,其还具有输出轴10以及位于该输出轴(10)上的输出轴圆柱齿轮(9),所述输出轴圆柱齿轮(9)与所述第一圆柱齿轮(8)或与第二圆柱齿轮(7)啮合,或采用2组输出轴(10)以及位于其上的输出轴圆柱齿轮(9)同时与第一圆柱齿轮(8)和第二圆柱齿轮(7)啮合。The switching reciprocating incomplete non-circular gear transmission according to claim 1, further comprising an output shaft 10 and an output shaft spur gear (9) on the output shaft (10), the output shaft cylinder The gear (9) meshes with the first spur gear (8) or with the second spur gear (7), or uses two sets of output shafts (10) and an output shaft spur gear (9) located thereon simultaneously with the first The spur gear (8) meshes with the second spur gear (7).
- 根据权利要求1所述的切换往复不完整非圆齿轮变速箱,其特征在于:The switching reciprocating incomplete non-circular gear transmission according to claim 1, wherein:所述主动切换不完整非圆齿轮(5)的节曲线(28)由二个弧度为60度的变速区(29)、一个弧度为60度的匀速区(30)、一个弧度为180度无齿型区(31)构成;所述主动切换不完整非圆齿轮(5)的节曲线(28)中的匀速区(30)位于有齿形部分,对应大圆弧R1区域;所述主动切换不完整非圆齿轮(5)的节曲线(28)中的无齿型区(31)对应小圆弧R2区域;主动切换不完整非圆齿轮(5)的中心线通过匀速区(30)中间的一个齿槽;所述主动切换不完整非圆齿轮(5)的齿数是偶数,齿槽数是奇数,The pitch curve (28) of the active switching incomplete non-circular gear (5) consists of two shifting zones (29) with a curvature of 60 degrees, a uniform velocity zone (30) with an arc of 60 degrees, and an arc of 180 degrees. The toothed zone (31) is configured; the uniform velocity zone (30) in the pitch curve (28) of the active switching incomplete non-circular gear (5) is located in the toothed portion corresponding to the large arc R1 region; the active switching The non-toothed zone (31) in the section curve (28) of the incomplete non-circular gear (5) corresponds to the small arc R2 zone; the center line of the actively switched incomplete non-circular gear (5) passes through the middle of the uniform velocity zone (30) One of the slots; the number of teeth of the inactive non-circular gear (5) is an even number, and the number of slots is an odd number.第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的节曲线(33)均由二个角度为60度的变速区(35)、一个弧度为180度的匀速区(37)、一个弧度为60度的无齿型区(36)构成;所述第一从动切换不完整非 圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的节曲线(33)中的匀速区(37)位于有齿形部分,对应小圆弧R2区域;所述第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的节曲线(33)中的无齿形区(36)对应大圆弧R1区域;第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的旋转中心线通过匀速区(37)中段部位的一个轮齿;所述第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的齿数是奇数,齿槽数则是偶数,The first follower switching incomplete non-circular gear (4) and the second follower switching incomplete non-circular gear (6) section curve (33) are both shifted by two angles of 60 degrees (35), one arc It is composed of a uniform speed zone (37) of 180 degrees and a toothless zone (36) with a curvature of 60 degrees; the first slave switching is incomplete The constant speed zone (37) in the pitch curve (33) of the circular gear (4) and the second driven switching incomplete non-circular gear (6) is located in the toothed portion corresponding to the small arc R2 region; the first slave The non-toothed area (36) in the pitch curve (33) of the incompletely non-circular gear (4) and the second driven switch incomplete non-circular gear (6) corresponds to the large arc R1 area; the first slave Switching the rotation center line of the incomplete non-circular gear (4) and the second driven switching incomplete non-circular gear (6) through one tooth of the middle portion of the constant velocity zone (37); the first slave switching is not complete The number of teeth of the circular gear (4) and the second driven incomplete non-circular gear (6) is odd, and the number of slots is even.所述主动切换不完整非圆齿轮(5)、第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的旋转中心“O”,是大圆弧R1和小圆弧R2的几何中心,The active switching incomplete non-circular gear (5), the first driven switching incomplete non-circular gear (4), and the second driven switching incomplete non-circular gear (6) have a center of rotation "O", which is a large circle The geometric center of the arc R1 and the small arc R2,主动切换不完整非圆齿轮(5)与第一从动切换不完整非圆齿轮(4)或第二从动切换不完整非圆齿轮(6)啮合运转时,当从动切换不完整非圆齿轮啮合运行至匀速区时,其传动比I符合公式:When the active switching incomplete non-circular gear (5) is meshed with the first driven switching incomplete non-circular gear (4) or the second driven switching incomplete non-circular gear (6), when the driven switching is incomplete non-circular When the gear meshes to the uniform speed zone, its gear ratio I conforms to the formula:I=R1/R2,I=R1/R2,I的取值区间是:最大数值为Imax=R1:最小数值为Imin=1/R1;The value range of I is: the maximum value is Imax=R1: the minimum value is Imin=1/R1;所述主动切换不完整非圆齿轮(5)变速区(29)的节曲线(32)、第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)变速区(35)的节曲线(34)的数学表达式F(α)均符合公式:The pitch curve (32) of the active switching incomplete non-circular gear (5) shifting zone (29), the first driven switching incomplete non-circular gear (4), and the second driven switching incomplete non-circular gear (6) The mathematical expression F(α) of the pitch curve (34) of the shifting zone (35) conforms to the formula:F(α)=R1*sin(α)/R2;F(α)=R1*sin(α)/R2;其中:among them:R1为主动切换不完整非圆齿轮(5)的节曲线(28)、第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的节曲线(33)的大圆弧区域的半径; R1 is a pitch curve (28) of the active switching incomplete non-circular gear (5), a first driven switching incomplete non-circular gear (4), and a second driven switching incomplete non-circular gear (6). 33) the radius of the large arc area;R2为主动切换不完整非圆齿轮(5)的节曲线(28)、第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的节曲线(33)的小圆弧区域的半径;R2 is a pitch curve (28) of the active switching incomplete non-circular gear (5), a first driven switching incomplete non-circular gear (4), and a second driven switching incomplete non-circular gear (6). 33) the radius of the small arc area;α为主动切换不完整非圆齿轮(5)的变速区(29)节曲线(32)、第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的变速区(35)节曲线(34)上的任意一点在其各自完整的节曲线坐标系内对应的角度。α is the shifting zone (29) curve (32) for actively switching the incomplete non-circular gear (5), the first driven switching incomplete non-circular gear (4), and the second driven switching incomplete non-circular gear (6) Any point on the shifting zone (35) section curve (34) is at a corresponding angle within its respective complete pitch curve coordinate system.
- 根据权利要求1-3之一所述的切换往复不完整非圆齿轮变速箱,其特征在于,在所述主动切换不完整非圆齿轮(5)的2个变速区(29)靠近无齿型区(31)的端部各有一个变形切换齿(39);在所述第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的2个变速区(35)靠近无齿型区(36)的端部各有一个变形切换齿齿槽(38)。Switching a reciprocating incomplete non-circular gearbox according to any one of claims 1 to 3, characterized in that the two shifting zones (29) of the actively switching the incomplete non-circular gear (5) are close to the edentulous type Each end of the zone (31) has a deformation switching tooth (39); two of the first driven switching incomplete non-circular gear (4) and the second driven switching incomplete non-circular gear (6) A shifting tooth groove (38) is formed in each of the ends of the shifting zone (35) adjacent to the toothless zone (36).
- 根据权利要求4所述的切换往复不完整非圆齿轮变速箱,其特征在于,所述主动切换不完整非圆齿轮(5)的变形切换齿(39)的齿厚是与其相邻轮齿齿厚的3倍,变形切换齿(39)的齿全高是与其相邻轮齿齿全高的1.0倍至1.65倍,变形切换齿(39)的齿顶线线段形状和与其相邻的节曲线线段平行,该变形切换齿(39)的齿廓仍是渐开线齿廓。The switching reciprocating incomplete non-circular gear transmission according to claim 4, wherein the tooth thickness of the deformation switching tooth (39) of the active switching incomplete non-circular gear (5) is an adjacent tooth thereof 3 times thicker, the full height of the tooth of the deformation switching tooth (39) is 1.0 times to 1.65 times of the full height of the tooth of the adjacent tooth, and the shape of the tooth line segment of the deformation switching tooth (39) is parallel to the curve line segment adjacent thereto. The tooth profile of the deformation switching tooth (39) is still an involute profile.
- 根据权利要求5所述的切换往复不完整非圆齿轮变速箱,其特征在于,所述第一从动切换不完整非圆齿轮(4)和第二从动切换不完整非圆齿轮(6)的变形切换齿齿槽(38)的齿槽厚度是与其相邻的轮齿齿槽厚度的3倍,变形切换齿齿槽(38)的齿槽深度是与其相邻的轮齿齿槽深度的1.0倍至1.75倍,变形切换齿齿槽(38)的齿根线的线段形状和与其相邻的节曲线线段平行。The switching reciprocating incomplete non-circular gear transmission according to claim 5, wherein said first driven switching incomplete non-circular gear (4) and said second driven switching incomplete non-circular gear (6) The deformation of the deformation tooth groove (38) is three times the thickness of the tooth groove adjacent thereto, and the groove depth of the deformation switching tooth groove (38) is the cogging depth of the adjacent tooth groove. 1.0 to 1.75 times, the shape of the line segment of the root line of the deformation switching tooth groove (38) is parallel to the section curve line adjacent thereto.
- 一种传动机构,其特征在于,该传动机构包含如权利要求1-6之一所述的切换往复不完整非圆齿轮变速箱。 A transmission mechanism, characterized in that the transmission mechanism comprises a switching reciprocating incomplete non-circular gear transmission according to any one of claims 1-6.
- 根据权利要求7所述的传动机构,其特征在于,该传动机构中的切换往复不完整非圆齿轮变速箱的输入轴(1)可与链轮、皮带轮、各类齿轮机构中的一个或多个的组合通过联轴器连接后实施动力输入。The transmission mechanism according to claim 7, wherein the input shaft (1) of the switching reciprocating incomplete non-circular gearbox in the transmission mechanism can be one or more of a sprocket, a pulley, and various gear mechanisms. The combination of the two is connected by a coupling and the power input is implemented.
- 根据权利要求7或8所述的传动机构,其特征在于,所述切换往复不完整非圆齿轮变速箱的输出轴(10)通过联轴器与第三传动轴21以及位于其上的第三圆柱齿轮13、第四传动轴15以及位于其上的第四圆柱齿轮14连接,从而实现动力输出。The transmission mechanism according to claim 7 or 8, wherein the output shaft (10) of the switching reciprocating incompletely non-circular gear transmission passes through the coupling and the third transmission shaft 21 and a third thereof The spur gear 13, the fourth transmission shaft 15, and the fourth spur gear 14 located thereon are connected to realize power output.
- 根据权利要求7或8所述的传动机构,其特征在于,所述切换往复不完整非圆齿轮变速箱的输出轴(10)通过联轴器与可与链轮系、皮带轮系或链轮、皮带轮、圆柱齿轮系中之一或组合连接,从而实现动力输出。The transmission mechanism according to claim 7 or 8, wherein the output shaft (10) of the switching reciprocating incomplete non-circular gear transmission passes through the coupling and the sprocket system, the pulley train or the sprocket, One of the pulleys and the cylindrical gear train or a combination is connected to realize the power output.
- 一种立式抽油机,其特征在于,其抽油杆上下往复的换向机构是安装了如权利要求7-10之一所述的传动机构。 A vertical pumping unit characterized in that the reversing mechanism for the sucker rod to reciprocate up and down is a transmission mechanism according to any one of claims 7-10.
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CN104121338A (en) * | 2014-03-14 | 2014-10-29 | 董剑 | Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof |
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EP1248697A1 (en) * | 2000-01-18 | 2002-10-16 | David A. Buck | Load equalizing power tong gear train |
CN101463889A (en) * | 2008-05-26 | 2009-06-24 | 北京锋源技术有限公司 | Non-circular gear transmission and its transmission mechanism |
CN102606685A (en) * | 2011-01-25 | 2012-07-25 | 徐州非圆机械科技有限公司 | Gearbox comprising non-circular gear, internal gear and planet differential gear train |
CN103527153A (en) * | 2013-10-25 | 2014-01-22 | 徐州非圆机械科技有限公司 | Non-circular gear up-down stroke automatic reversing pumping unit |
CN104121338A (en) * | 2014-03-14 | 2014-10-29 | 董剑 | Switching reciprocating incomplete non-circular gear speed changing box and transmitting mechanism thereof |
Cited By (4)
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CN110879910A (en) * | 2019-11-21 | 2020-03-13 | 燕山大学 | Closed non-circular gear pair with transmission ratio of Fourier series |
CN110879910B (en) * | 2019-11-21 | 2023-05-26 | 燕山大学 | Closed non-circular gear pair with transmission ratio of Fourier series |
CN112833141A (en) * | 2020-08-26 | 2021-05-25 | 辽宁石油化工大学 | Elliptic planetary gear train type elastic tooth roller peanut pickup device |
CN112833141B (en) * | 2020-08-26 | 2023-05-12 | 辽宁石油化工大学 | Elliptic planetary gear train type spring tooth roller peanut pickup device |
Also Published As
Publication number | Publication date |
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CN104121338B (en) | 2018-04-10 |
CN104121338A (en) | 2014-10-29 |
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