Swing rack-crankshaft switching mechanism
阅读说明:本技术 一种摆动齿条-曲轴转换机构 (Swing rack-crankshaft switching mechanism ) 是由 安里千 刘庆 王聪 于 2018-09-06 设计创作,主要内容包括:本发明的转换机构包括:曲轴、传动轴、传动齿轮、摆动齿条、驱动齿轮及驱动齿条等,曲轴的主轴颈和至少一根以上的传动轴安装在曲轴箱的两侧壁上,每一根传动轴上的传动齿轮与摆动齿条啮合,各摆动齿条一端部的齿条圆环安装在曲柄臂的连杆轴颈上,每个限位杆置于每一根摆动齿条的无齿背面上,各限位杆的两端部安装在各对限位扁杆的一端部,每对限位扁杆的限位圆环分别安装在传动齿轮两侧的传动轴上;延伸到附加缸体中的每根传动轴上安装数个驱动齿轮,每个驱动齿轮与驱动齿条啮合,定位杆置于每条驱动齿条的无齿背面上,每对定位圆环分别安装在驱动齿轮两侧的传动轴上,每根驱动齿条与活塞铰接,构成只有一付曲柄臂的多个汽缸的发动机组。(The conversion mechanism of the present invention includes: the main journal of the crankshaft and at least more than one transmission shaft are arranged on two side walls of the crankcase, the transmission gear on each transmission shaft is meshed with the swing rack, a rack ring at one end of each swing rack is arranged on a connecting rod journal of a crank arm, each limiting rod is arranged on the non-tooth back surface of each swing rack, two ends of each limiting rod are arranged at one end of each pair of limiting flat rods, and the limiting rings of each pair of limiting flat rods are respectively arranged on the transmission shafts at two sides of the transmission gear; each transmission shaft extending into the additional cylinder body is provided with a plurality of driving gears, each driving gear is meshed with a driving rack, the positioning rods are arranged on the back face without teeth of each driving rack, each pair of positioning rings are respectively arranged on the transmission shafts on two sides of the driving gear, and each driving rack is hinged with the piston to form the engine unit with a plurality of cylinders and only one pair of crank arms.)
1. A swing rack-crankshaft switching mechanism mainly comprises: only crankshaft (1), transmission shaft (4), drive gear (3), swing rack (2), drive gear (5) and drive rack (6) etc. of a pair of crank arm (102), its characterized in that: the main journal (101) and the plurality of transmission shafts (4) of the crankshaft (1) are arranged on two side walls of the crankcase (9), the axes (401) of the transmission shafts (4) are distributed on the circumference taking the axis (104) of the main journal (101) as the center at certain intervals, a transmission gear (3) coaxial with the transmission shaft is arranged on the cylindrical surface of each transmission shaft (4), the number of swing racks (2) equal to the number of the transmission gears (3) is respectively meshed with each transmission gear (3), a rack ring (200) of each swing rack (2) is arranged on a journal connecting rod (103) at the end part of a crank arm (102), and limiting mechanisms are arranged on each swing rack (2) and the transmission shafts (4) at two sides of the transmission gear (3) meshed with the swing rack; each transmission shaft (4) extends into an additional cylinder body (10) which is tightly attached to one side or two sides of a crank case (9), each driving gear (5) is coaxially arranged on the cylindrical surface of each transmission shaft (4) in the additional cylinder body (10), each driving gear (5) is meshed with a driving rack (6), and positioning mechanisms are arranged on each driving rack (6) and the transmission shafts (4) on two sides of the driving gear (5) meshed with the driving rack.
2. The oscillating rack-crankshaft switching mechanism of claim 1, wherein: the additional cylinder body (10) is provided with a plurality of cylinders (8) which are equal to the number of the driving gears (5), one end part or two end parts of each driving rack (6) are hinged with a piston (7) in the cylinder (8), and the engine unit with a plurality of cylinders (8) of only one pair of crankshafts (1) is formed.
3. The oscillating rack-crankshaft switching mechanism of claim 1, wherein: the rack ring (200) is arranged at one end of each swing rack (2), the effective length of each swing rack (2) is more than 2 times of the distance between the axis (104) of the main journal (101) and the axis (105) of the connecting rod journal (103), and the central line (204) of each rack ring (200) is collinear with the axis (105) of the connecting rod journal (103).
4. The oscillating rack-crankshaft switching mechanism of claim 1, wherein: a stop gear include: each limiting rod (12) is arranged on the toothless back surface (202) of each swinging rack (2), two end parts of each limiting rod (12) are respectively and rotatably arranged at one end part of each limiting flat rod (11), the other end parts of each limiting flat rod (11) are respectively limiting circular rings (111), the two limiting circular rings (111) are respectively arranged on the swinging racks (2) and transmission shafts (4) at two sides of the transmission gear (3) meshed with the swinging racks, the distance between the inner side surfaces of the limiting flat rods (11) at the two end parts of each limiting rod (12) is slightly larger than the width of the swinging racks (2) and the transmission gear (3) meshed with the swinging racks, the inner diameter of each limiting circular ring (111) is equal to the diameter of the transmission shafts (4), and the interval between the limiting rods (12) on the toothless back surface (202) of each swinging rack (2) and the reference circle (301) of the transmission gear (3) meshed with the swinging racks (2) is equal to the reference line (201) of the swinging racks (2) to zero Distance between tooth backs (202).
5. The oscillating rack-crankshaft switching mechanism of claim 1, wherein: one such positioning mechanism comprises: each positioning rod (14) is arranged on the toothless back surface (601) of the driving rack (6), two end parts of each positioning rod (14) are respectively and rotatably arranged at one end part of a pair of positioning flat rods (13), the other end parts of the pair of positioning flat rods (13) are respectively provided with a positioning ring (131), two positioning rings (131) are respectively arranged on the driving rack (6) and the transmission shafts (4) at two sides of the driving gear (5) meshed with the driving rack (6), the distance between the inner side surfaces of the limiting flat rods (13) at the two end parts of each positioning rod (14) is slightly larger than the width of the driving rack (6) and the driving gear (5) meshed with the driving rack (6), the diameter of each limiting ring (131) is equal to the diameter of the transmission shafts (4), and the interval between the positioning rod (14) on the toothless back surface (601) of each driving rack (6) and the reference circle (501) of the driving gear (5) meshed with the driving rack (6) is equal to the distance from the The distance between the faces (601).
6. The oscillating rack-crankshaft switching mechanism of claim 5, wherein: a plane passing through an axis (104) of the main journal (101) and an axis (105) of the connecting rod journal (103) is set to be a bisecting plane (107) of the crank arm (102), and when the bisecting plane (107) is tangent to a reference circle (301) of each transmission gear (3), a driving rack (6) driven by each driving gear (5) coaxial with the transmission gear (3) and a piston (7) at the end of the driving rack are at the top dead center or the bottom dead center.
7. The oscillating rack-and-crankshaft switching mechanism of claim 6, wherein: the shapes of the transmission shafts (4) are the same, the axis (401) of each transmission shaft (4) is parallel to the axis (104) of the main journal (101), the central angle corresponding to the circular arc between the axes (401) of two adjacent transmission shafts (4) on the circumference taking the axis (104) of the main journal (101) as the center is equal to or less than 180 degrees, the interval between the reference circle (301) of the transmission gear (3) on each transmission shaft (4) and the axis (104) of the main journal (101) is equal to or slightly larger than the distance between the axis (104) of the main journal (101) and the axis (105) of the connecting rod journal (103) and the length of the vertical line segment (205) from the central line (204) of the rack ring (200) on the swing rack (2) to the reference line (201) of the swing rack (2); by adjusting the distance between each transmission shaft (4) and the main journal (101), when a driving rack (6) driven by each driving gear (5) coaxial with each transmission gear (3) and a piston (7) at the top dead center start to move towards the bottom dead center, a dividing line (201) of the swinging rack (2) meshed with each transmission gear (3) is approximately orthogonal to a middle dividing plane (107) of the crank arm (102), namely, an included angle between the swinging rack (2) meshed with each transmission gear (3) and the crank arm (102) is approximately 90 degrees.
8. The oscillating rack-and-crankshaft switching mechanism of claim 8, wherein: a plurality of cylinder bodies (19) with plungers (15) are arranged on one side of a crankcase (9), one end or two ends of a driving rack (6) meshed with each driving gear (5) are connected with the plungers (15) in each cylinder body (19), and a main journal (101) of a crankshaft (1) outside the crankcase (9) is connected with a rotating shaft (18) of a power device (17) through a connecting mechanism (16) to form a water pump, a compressor and the like.
Technical Field
The invention relates to a mechanical device for converting reciprocating linear motion of a piston of an engine into circular motion of a crankshaft, in particular to a swing rack-crankshaft linkage conversion mechanism which replaces the existing crankshaft (handle) -connecting rod conversion mechanism.
Background
At present, a crankshaft (crank throw) connecting rod mechanism is generally adopted in a piston engine to carry out a machine for mutual conversion between linear reciprocating motion and circular motion, the design and the manufacture of the crankshaft connecting rod mechanism are very complete, but because the crankshaft (crank throw) connecting rod geometric mechanism and the stress state thereof are very complex, all parts are in a complex three-way stress state, and the piston engine has obvious defects in practical application and needs to be further improved and optimized:
1. theoretical analysis and practical application tests show that in a traditional crankshaft connecting rod mechanism, after gas in a cylinder is ignited, the maximum gas explosive force on a piston is converted into tangential force acting on the crank end of a crankshaft only by about twenty percent after twice decomposition, so that the torque output by the crankshaft is greatly reduced, and the power of an engine is reduced;
2. in a crankshaft (handle) connecting rod mechanism, gas pressure acting on a piston is decomposed into acting force along the axial direction of a connecting rod and lateral pressure acting on a cylinder wall in the direction perpendicular to the axial direction of a cylinder, so that the lateral friction force between the piston and the cylinder wall is increased, the lateral abrasion of the cylinder wall is accelerated, the piston cannot work due to cylinder clamping, and the service life of the cylinder is shortened;
3. the unbalanced rotary mass and the rotary motion generated by the swinging of the connecting rod in the crankshaft connecting rod mechanism cause inertia force, so that alternating impact force is generated on a piston, a cylinder wall and a rotary contact surface, uneven friction and impact among all parts are increased, the output power of an engine is influenced, and the engine generates larger vibration and noise.
In order to overcome the above-mentioned drawbacks of the conventional crankshaft-connecting rod mechanism, the present invention provides a swing rack-crankshaft switching mechanism.
Disclosure of Invention
According to the present invention, there is provided a swing rack-crankshaft switching mechanism comprising: only a pair of crank arms and the crankshaft of the end connecting rod journal thereof, a transmission shaft, a transmission gear, a swinging rack, a driving gear, a driving rack and the like, and is characterized in that: the main journal and a plurality of transmission shafts of the crankshaft are arranged on two side walls of the crankcase, the axes of the transmission shafts are distributed on the circumference taking the axis of the main journal as the center according to a certain interval, a transmission gear is coaxially arranged on the cylindrical surface of each transmission shaft, the swinging racks with the same number as the transmission gears are respectively meshed with the transmission gears, the rack ring of each swinging rack is arranged on the connecting rod journal of the crank arm, and a limiting mechanism is arranged on each swinging rack and the transmission shafts on two sides of the transmission gear meshed with the swinging rack; each transmission shaft extends into an additional cylinder body which is tightly attached to one side or two sides of the crankcase, each driving gear is coaxially installed on the cylindrical surface of each transmission shaft in the additional cylinder body, and a positioning mechanism is arranged on each driving rack and the transmission shafts on two sides of the driving gear meshed with the driving rack.
The invention provides a swing rack-crankshaft switching mechanism, wherein cylinders are arranged on an additional cylinder body, one end part or two end parts of each driving rack are hinged with a piston in the cylinder, and an engine unit with a plurality of cylinders of only one pair of crankshafts is formed.
The invention provides a swing rack-crankshaft conversion mechanism, wherein a rack ring is arranged at one end of each swing rack, the effective length of each swing rack is more than 2 times of the distance between the axis of a main journal and the axis of a connecting rod journal, and the central line of each rack ring is collinear with the axis of the connecting rod journal.
The invention provides a swing rack-crankshaft switching mechanism, wherein each limiting rod is arranged on the toothless back surface of a swing rack, two end parts of each limiting rod are respectively and rotatably arranged at one end part of a pair of limiting flat rods, the other end parts of the pair of limiting flat rods are respectively limiting circular rings, the two limiting circular rings are respectively arranged on a swing rack and transmission shafts at two sides of a transmission gear meshed with the swing rack, the distance between the inner side surfaces of the pair of limiting flat rods at the two end parts of each limiting rod is slightly larger than the width of the swing rack and the transmission gear meshed with the swing rack, the inner diameter of each limiting circular ring is equal to the diameter of the transmission shaft, and the interval between the limiting rod on the toothless back surface of each swing rack and a reference circle of the transmission gear meshed with the swing rack is equal to the distance between a reference line of the swing rack.
The invention provides a swing rack-crankshaft switching mechanism, wherein each positioning rod is arranged on the toothless back surface of a driving rack, two end parts of each positioning rod are respectively and rotatably arranged at one end part of a pair of positioning flat rods, the other end parts of the pair of positioning flat rods are respectively positioning circular rings, the two positioning circular rings are respectively arranged on transmission shafts at two sides of the driving rack and a driving gear meshed with the driving rack, the distance between the inner side surfaces of the positioning flat rods at two ends of each positioning rod is slightly larger than the width of the driving rack and the driving gear meshed with the driving rack, the inner diameter of each positioning circular ring is equal to the diameter of the transmission shaft, and the interval between the positioning rod on the toothless back surface of each driving rack and a reference circle of the driving gear meshed with the driving rack is equal to the distance between a reference line of the driving rack and.
The invention provides a swing rack-crankshaft switching mechanism, wherein a plane passing through the axis of a main journal and the axis of a connecting rod journal is set to be a bisecting plane of a crank arm, when the bisecting plane of the crank arm is tangent to a reference circle of each transmission gear, a driving rack driven by each driving gear coaxial with the transmission gear and a piston at the end of the driving rack are at the top dead center or the bottom dead center, and at the moment, an included angle between the bisecting plane of the crank arm and a reference line of each swing rack is close to 0 degree.
The invention provides a swing rack-crankshaft switching mechanism, wherein, the shapes of all transmission shafts are the same, the axes of all transmission shafts are parallel to the axis of a main journal, the central angle corresponding to the circular arc between the axes of two adjacent transmission shafts on the circumference taking the axis of the main journal as the center is equal to or less than 180 degrees, the interval between the reference circle of a transmission gear on each transmission shaft and the axis of the main journal is equal to or slightly larger than the distance between the axis of the main journal and the axis of a connecting rod journal and the length of the vertical line segment from the central line of a rack circular ring on the swing rack to the reference line of the swing rack; by adjusting the distance between each transmission shaft and the main journal, when the driving rack driven by each driving gear coaxial with each transmission gear and the piston at the top dead center start to move to the bottom dead center, the indexing line of the oscillating rack meshing with each pinion is close to orthogonal to the median plane of the crank arm, the included angle between the swinging rack meshed with each transmission gear and the crank arm is close to 90 degrees, at the moment, if gas in the cylinder where the piston is located explodes, the gas explosion force acting on the piston is converted into tangential force acting on a connecting rod journal by means of the driving rack, the driving gear rotating anticlockwise, the transmission gear and the swinging rack in an almost equivalent mode, the connecting rod journal drives the crankshaft to output maximum torque, and model machine experiments show that the maximum torque output by the conversion mechanism is increased by more than 2 times compared with the maximum torque output by a traditional crankshaft-connecting rod mechanism.
The present invention provides a swing rack-crankshaft switching mechanism, wherein, a plurality of cylinder bodies with plungers are arranged on one side of a crankcase, one end part or two end parts of a driving rack meshed with each driving gear are connected with the plungers in the cylinder bodies, and a main journal of a crankshaft outside the crankcase is connected with a rotating shaft of a power device through a connecting mechanism to form a water pump, a compressor, etc.
The swing rack-crankshaft switching mechanism provided by the invention realizes the mutual conversion of linear reciprocating motion and rotary circular motion, has more reasonable power transmission and motion mode conversion, overcomes the inherent defects in a crank throw connecting rod mechanism, and has the following main advantages:
1. in the rack and guide groove-crankshaft switching mechanism of the invention, when the driving rack driven by each driving gear coaxial with each transmission gear and the piston at the top dead center thereof start to move towards the bottom dead center, the included angle between the swinging rack meshed with each transmission gear and the crank arm is close to 90 degrees, at this time, if gas in the cylinder explodes, the maximum gas explosion force acted on the piston is converted into a tangential force on a connecting rod journal which does rotary motion by virtue of the nearly equivalent values of each driving rack, each driving gear, each transmission gear, the swinging rack and the like on each transmission shaft, the crankshaft outputs the maximum torque, theoretical calculation shows that the maximum torque output by the crankshaft is increased by more than 3 times than the maximum torque output by the traditional crankshaft-connecting rod mechanism, model machine experiments show that the maximum torque output by the crankshaft is increased by at least 2 times than the maximum torque output by the traditional crankshaft-connecting rod mechanism, therefore, the conversion efficiency of the conversion mechanism can be greatly improved compared with that of the traditional crankshaft-connecting rod mechanism;
2. in the conversion mechanism, the reciprocating linear motion of each piston is directly converted into the tangential force of the rotation of the crank arm by means of each driving rack, each driving gear, each transmission gear and the swinging rack, so that the lateral pressure between the piston and the cylinder wall of the cylinder caused by the transmission of the connecting rod in the traditional crankshaft-connecting rod mechanism and the abrasion of the cylinder wall caused by the lateral pressure are thoroughly eliminated, and the service life of the cylinder can be prolonged;
3. in the conversion mechanism, each pair of transmission shafts can be provided with a plurality of driving gears, driving racks and cylinders, so that an engine unit with only one crank throw (crank) and ultrahigh power can be formed, a large number of crank throws (cranks) are saved, and the conversion efficiency is improved;
4. in the conversion mechanism, the radius of the transmission gear and the radius of the driving gear can be changed according to design requirements, and the rotating diameter of the crankshaft can be smaller than or larger than the stroke of the piston, so that the explosive force of gas in the cylinder can be more reasonably utilized, and the mechanical efficiency of the conversion mechanism is improved;
5. the crankshaft, the swing rack, the transmission gear and the like are arranged in a single crankcase, are not affected by high temperature generated by gas explosion in the cylinder, and the service life of main parts of the conversion mechanism is prolonged.
The structure of the invention can also be used for machines which convert rotary motion into reciprocating linear motion in any form, such as piston type oil, gas, water pumps, piston type compressors and the like.
Drawings
FIG. 1 is a schematic elevational view of a first embodiment of a shift mechanism of the present invention;
FIG. 2 is a schematic cross-sectional view A-A of a first embodiment of a shift mechanism of the present invention;
FIG. 3 is a schematic view of section B-B of a first embodiment of a shift mechanism of the present invention;
FIG. 4 is a schematic view of a swing rack and a transmission gear, and a limit rod and a limit flat rod according to a first embodiment of the present invention;
FIG. 5 is a schematic view of the drive rack and drive gear and the locating bar and locating flat bar of the first embodiment of the present invention;
FIG. 6 is a schematic view of the distance between the transmission shaft and the main journal according to the first embodiment of the present invention;
FIG. 7 is a schematic view of a piston associated with a drive shaft at a top dead center when a bisecting plane of a crank arm is tangent to a reference circle of a drive gear of the drive shaft in accordance with a first embodiment of the present invention;
FIG. 8 is a schematic view showing the approximate orthogonality of the graduation marks of the oscillating rack gear meshing with the pinion gear with the bisecting plane of the crank arm when the piston associated with one of the pinion shafts starts moving toward the bottom dead center in the first embodiment of the present invention;
FIG. 9 is a schematic top-dead-center view of a piston associated with another drive shaft when the bisecting plane of the crank arm is tangent to the reference circle of the drive gear of that drive shaft in accordance with the first embodiment of the present invention;
FIG. 10 is a schematic view of the approximate orthogonality between the dividing line of the oscillating rack engaging the pinion and the medial plane of the crank arm as the piston associated with the other pinion begins to move toward bottom dead center in the first embodiment of the present invention;
FIG. 11 is a schematic view of a second embodiment of the conversion mechanism of the present invention;
fig. 12 is a schematic view of a third embodiment of the conversion mechanism of the present invention.
Detailed description of the preferred embodiments
The following describes in detail an embodiment of a swing rack-crankshaft switching mechanism provided by the present invention with reference to the accompanying drawings.
The first embodiment of the present invention is described below:
as shown in fig. 1, 2 and 3, the
As shown in fig. 1 and 4, each oscillating
As shown in fig. 4, the
As shown in fig. 5, the
As shown in fig. 7 and 9, a plane passing through the
As shown in fig. 1, 2 and 6, the two
As shown in fig. 8 and 10, by adjusting the distance between each
As shown in fig. 2 and 3, the
The operation of the first embodiment of the present invention is as follows:
the method comprises the following operation steps: as shown in fig. 1, the counter-clockwise rotating connecting
And a second operation step: as shown in fig. 7, when the two counterclockwise rotating
And a third operation step: as shown in fig. 8, when two
The operation step four: as shown in fig. 9, the two
The operation step five: as shown in fig. 10, the two
And a sixth operation step: as shown in fig. 1, the
In the above movement, the two
Theoretical calculation shows that the maximum torque output by the conversion mechanism is increased by 3 times compared with the maximum torque output by the traditional crankshaft-connecting rod mechanism, and model machine experiments show that the maximum torque output by the conversion mechanism is increased by more than 2 times compared with the maximum torque output by the traditional crankshaft-connecting rod mechanism.
The second embodiment of the present invention is described below:
as shown in fig. 11, the same three
The operation of the second embodiment of the present invention:
with reference to the operation of the first embodiment, the operation of the various components on each
Third embodiment of the invention:
as shown in fig. 12, the
The above examples are only intended to illustrate the preferred embodiments of the present invention, and are not intended to limit the scope of the present invention, and various modifications and improvements of the technical solution of the present invention may be made by those skilled in the art without departing from the design of the present invention, and all of them should fall within the protection scope defined by the claims of the present invention.
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