WO2015135400A1

WO2015135400A1 - A switching reciprocating incomplete non-circular gear transmission box and a transmission mechanism thereof

Info

Publication number: WO2015135400A1
Application number: PCT/CN2015/071166
Authority: WO
Inventors: 董剑; 荣世德; 吴序堂; 张瑞; 薛金元; 潘锋
Original assignee: 董剑; 潘辉
Priority date: 2014-03-14
Filing date: 2015-01-21
Publication date: 2015-09-17
Also published as: CN104121338A; CN104121338B

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

Switching reciprocating incomplete non-circular gearbox and its transmission mechanism

Technical field

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.

Background technique

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.

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.

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.

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.

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.

Summary of the invention

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.

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;

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;

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.

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.

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;

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.

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;

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,

The value range of I is: the maximum value is Imax=R1: the minimum value is Imin=1/R1;

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;

among them:

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;

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.

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.

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.

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.

The invention also provides a transmission mechanism, the transmission mechanism comprising:

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;

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 above technical solution of the present invention has the following advantages compared with the prior art:

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;

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. 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;

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.

BRIEF DESCRIPTION OF THE DRAWINGS:

1 is a schematic view of a switching reciprocating incomplete non-circular gearbox of the present invention;

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;

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;

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;

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;

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;

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;

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;

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;

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;

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;

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;

detailed description:

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).

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.

Specific implementation of switching a reciprocating incomplete non-circular gearbox:

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.

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.

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:

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.

Figure 3 shows a state diagram of actively switching the incomplete non-circular gear 5 at 180 degrees:

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. .

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;

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;

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:

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.

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. 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.

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.

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.

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;

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,

The value range of I is: the maximum value is Imax=R1, and the minimum value is Imin=1/R1;

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

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;

among them:

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;

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.

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.

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.

The implementation method of switching the reciprocating incomplete non-circular gear transmission and its transmission mechanism:

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;

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;

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;

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 specific implementation method of the vertical pumping unit:

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. To realize the power input of the vertical pumping unit;

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.

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.

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

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,

It is characterized by:

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;

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.
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).
The switching reciprocating incomplete non-circular gear transmission according to claim 1, wherein:

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.

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.

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,

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,

The value range of I is: the maximum value is Imax=R1: the minimum value is Imin=1/R1;

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;

among them:

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 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 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.
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).
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.
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.
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.
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.
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.
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.
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.