CN110878820A - Swing rack-crankshaft switching mechanism - Google Patents
Swing rack-crankshaft switching mechanism Download PDFInfo
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- CN110878820A CN110878820A CN201811035309.9A CN201811035309A CN110878820A CN 110878820 A CN110878820 A CN 110878820A CN 201811035309 A CN201811035309 A CN 201811035309A CN 110878820 A CN110878820 A CN 110878820A
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
- F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
Abstract
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.
Description
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 main journal 101 and the two transmission shafts 4 of the crankshaft 1, which only have one pair of crank arms 102 and end connecting rod journals 103, are mounted on two side walls of the crankcase 9, the axes 401 of the two transmission shafts 4 are on the circumference centering on the axis 104 of the main journal 101, the transmission gear 3 is coaxially mounted on the cylindrical surface of each transmission shaft 4, the two swing racks 2 are respectively meshed with the two transmission gears 3, the rack ring 200 of each swing rack 2 is mounted on the connecting rod journals 103 of the crank arms 102, and the limiting mechanisms are arranged on the transmission shafts 4 on two sides of each swing rack 2 and the transmission gear 3 meshed therewith; each transmission shaft 4 extends into an additional cylinder body 10 on one side of a crank case 9, two driving gears 5 are 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 6; four cylinders 8 are arranged on the additional cylinder 10, and a piston 7 in each cylinder 8 is hinged with one end of each driving rack 6, so that an engine unit with a plurality of cylinders 8 of only one pair of crankshafts 1 is formed.
As shown in fig. 1 and 4, each oscillating rack 2 has the same structure, each rack ring 200 is arranged at one end of the oscillating rack 2, the effective length of each oscillating rack 2 is greater than 2 times the distance between the axis 104 of the main journal 101 and the axis 105 of the journal 103, and the center line 204 of each rack ring 200 is collinear with the axis 105 of the journal 103.
As shown in fig. 4, the limit rod 12 is disposed on the toothless back surface 202 of the swing rack 2, two end portions of the limit rod 12 are respectively rotatably mounted on one end portion of a pair of limit flat rods 11, the other end portions of the pair of limit flat rods 11 are respectively limit circular rings 111, the two limit circular rings 111 are respectively mounted on the transmission shafts 4 on two sides of the swing rack 2 and the transmission gear 3 engaged therewith, a distance between inner side surfaces of the pair of limit flat rods 11 on the two end portions of the limit rod 12 is slightly larger than a width of the swing rack 2 and the transmission gear 3 engaged therewith, an inner diameter of each limit circular ring 111 is equal to a diameter of the transmission shaft 4, and an interval between the limit rod 12 on the toothless back surface 202 of the swing rack 2 and an index circle 301 of the transmission gear 3 engaged with the swing rack 2 is equal to a distance between an index line 201 of the swing rack 2 and.
As shown in fig. 5, the positioning rod 14 is disposed on the toothless back surface 601 of the driving rack 6, two end portions of the positioning rod 14 are respectively rotatably mounted on one end portion of a pair of positioning flat rods 13, the other end portions of the pair of positioning flat rods 13 are respectively positioning rings 131, the two positioning rings 131 are respectively mounted on the transmission shafts 4 on two sides of the driving rack 6 and the driving gear 5 engaged therewith, a distance between inner side surfaces of the positioning flat rods 13 on two ends of the positioning rod 14 is slightly larger than a width of the driving rack 6 and the driving gear 5 engaged therewith, an inner diameter of each positioning ring 131 is equal to a diameter of the transmission shaft 4, and an interval between the positioning rod 14 on the toothless back surface 601 of the driving rack 6 and a reference circle of the driving gear 5 engaged with the driving rack 6 is equal to a distance between a reference line 602 of the driving rack 6 and the toothless back surface.
As shown in fig. 7 and 9, a plane passing through the axis 104 of the main journal 101 and the axis 105 of the connecting rod journal 103 is defined as a median plane 107 of the crank arm 102, and when the median plane 107 of the crank arm 102 is tangent to a reference circle 301 of each transmission gear 3, the driving rack 6 driven by each driving gear 5 coaxial with the transmission gear 3 and the piston 7 at the end thereof are at the top dead center or bottom dead center, and at this time, an included angle between the median plane 107 of the crank arm 102 and a reference line 201 of each oscillating rack 2 is small.
As shown in fig. 1, 2 and 6, the two transmission shafts 4 have the same shape, 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 arc between the axes 401 of the two transmission shafts 4 on the circumference centering on the axis 104 of the main journal 101 is equal to 180 °, the interval between the reference circle 301 of the transmission gear 3 on each transmission shaft 4 and the main journal 101 is slightly larger than the distance between the axis 104 of the main journal 101 and the axis 105 of the connecting rod journal 103 plus the length of the perpendicular segment 205 from the center line 204 of the rack ring 200 on the swing rack 2 to the reference line 201 of the swing rack 2.
As shown in fig. 8 and 10, by adjusting the distance between each transmission shaft 4 and the main journal 101, when the driving rack 6 driven by each driving gear 5 coaxial with each transmission gear 3 and the piston 8 at the top dead center start moving to the bottom dead center, the graduation line 201 of the swinging rack 2 meshed with each transmission gear 3 is nearly orthogonal to the bisecting plane 107 of the crank arm 102, that is, the included angle between the swinging rack 2 meshed with each transmission gear 3 and the crank arm 102 is nearly 90 °, at this time, if the gas explosion in the cylinder 8 where the piston 7 is located occurs, the gas explosion force acting on this piston 7 is almost equally converted into the tangential force acting on the connecting rod journal 103 by the driving rack 6, the clockwise driving gear 5, the transmission gear 3 and the swinging rack 2, and the connecting rod journal 103 drives the crankshaft 1 to output the maximum torque, and the machine experiment shows that the conversion mechanism of the present invention outputs the maximum torque compared with the maximum torque output in the conventional crankshaft-connecting rod mechanism The moment is increased by more than 2 times.
As shown in fig. 2 and 3, the additional cylinder 10 is closely attached to one side of the crankcase 9, the length of the additional cylinder 10 is slightly longer than the stroke of each piston 7, and the cylinders 8 on the additional cylinder 10 are all the same.
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 rod journal 103 drives the transmission wheel 3 on the transmission shaft 4 meshed with the swing rack 2 and the two driving gears 5 coaxial therewith to rotate counter-clockwise, and the two counter-clockwise rotating driving gears 5 respectively drive the driving rack 6 and the piston 7 to move towards the top dead center; meanwhile, the driving wheel 3 meshed with the other swing rack 2 on the other transmission shaft 4 and the two driving gears 5 coaxial with the driving wheel rotate clockwise, and the two driving gears 5 rotating clockwise respectively drive the rack 6 and the piston 7 to move towards a lower dead center.
And a second operation step: as shown in fig. 7, when the two counterclockwise rotating driving gears 5 respectively drive the driving rack 6 and the piston 7 to the top dead center, the bisecting plane 107 of the crank arm 102 is tangent to the reference circle 301 of the counterclockwise rotating transmission gear 3 on the transmission shaft 4 as described in the first step; meanwhile, the two driving gears 5 rotating clockwise drive the rack 6 to drive the piston 7 to the bottom dead center.
And a third operation step: as shown in fig. 8, when two pistons 7 at the top dead center start moving to the bottom dead center, the transmission wheel 3 meshed with the swing rack 2 and two coaxial driving gears 5 start rotating clockwise, the bisecting plane 107 of the crank arm 102 is nearly orthogonal to the dividing line 201 of the swing rack 2, that is, when the swing rack 2 is nearly orthogonal to the crank arm 102, if gas explosion occurs in the cylinder 8 where one piston 7 that starts moving to the bottom dead center is located, the gas explosion force acting on the piston 7 is converted into a tangential force acting on the connecting rod journal 103 by the driving rack 6 and the clockwise driving gear 5 meshed with the driving rack, the transmission wheel 3 and the swing rack 2, and the connecting rod journal 103 drives the crankshaft 1 to output the maximum torque; at the same time, the two pistons 7 at the bottom dead center start moving towards the top dead center, and the transmission wheel 3 meshing with the other oscillating rack 2 and the two drive gears 5 coaxial therewith start rotating counterclockwise.
The operation step four: as shown in fig. 9, the two driving gears 5 which continue to rotate clockwise drive the driving rack 6 and the piston 7 at the end thereof to the bottom dead center; at the same time, the driving wheel 3 which continues to rotate counterclockwise and the two coaxial driving gears 5 drive the piston 7 at the end of the driving rack 6 to the top dead center, and the bisecting plane 107 of the crank arm 102 is tangent to the reference circle 301 of the counterclockwise rotating driving gear 3 on the other driving shaft 4.
The operation step five: as shown in fig. 10, the two pistons 7 at the bottom dead center start moving toward the top dead center, and the transmission wheel 3 engaged with the swing rack 2 and the two drive gears 5 coaxial therewith start rotating counterclockwise; at the same time, the transmission wheel 3 and the two driving gears 5 engaged with the other swing rack 2 start to rotate clockwise, the two pistons 7 at the top dead center start to move to the bottom dead center, at this time, the graduation line 201 of the swing rack 2 is nearly orthogonal to the bisecting plane 107 of the crank arm 102, that is, the swing rack 2 is nearly orthogonal to the crank arm 102, if the gas explosion in the cylinder 8 where the piston 7 which starts to move to the bottom dead center is located occurs, the gas explosion force acting on the piston 7 is transmitted to the connecting rod journal 103 by the driving rack 6, the driving gear 5 and the transmission wheel 3 rotating clockwise and the swing rack 2 engaged with the transmission wheel almost equally, and the connecting rod journal 103 drives the crankshaft 1 to output the maximum torque.
And a sixth operation step: as shown in fig. 1, the driving wheel 3 meshed with the swing rack 2 and the driving gear 5 coaxial with the driving wheel are driven by the connecting rod journal 103 which rotates anticlockwise continuously to rotate anticlockwise continuously, and the driving gear 5 which rotates anticlockwise continuously drives the piston 7 at the end of the driving rack 6 meshed with the driving gear to move towards the top dead center; at the same time, the driving gear 5 rotating clockwise drives the piston 7 at the end of the driving rack 6 meshed with the driving gear to move to the bottom dead center, and each component in the conversion mechanism repeatedly repeats the operation process from the operation step one to the operation step five, so that the reciprocating linear motion of the two pistons 8 is converted into the rotation of the crankshaft 1.
In the above movement, the two limit levers 12 are in close contact with the toothless back surfaces 202 of the two swing racks 2, so that the graduation line 201 of each swing rack 2 is always engaged with each transmission wheel 3, and each positioning lever 14 is in close contact with the toothless back surface 601 of each driving rack 6, so that the tooth surface 600 of each driving rack 6 is always engaged with the driving gear 5.
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 transmission shafts 4 are provided on the circumferences of both side walls of the crankcase (9) centering on the axis 104 of the main journal 101, the central angle corresponding to the circular arc between the axes 401 of the adjacent transmission shafts 4 is equal to 120 °, the respective parts provided on the connecting rod journal 103 and on each transmission shaft 4 are the same as those provided on the connecting rod journal 103 and on each transmission shaft 4 in the first embodiment, wherein one end portions of two drive racks 6 respectively engaged with the two drive gears 5 on each transmission shaft 4 are respectively hinged to the piston 7 in the cylinder 8 provided on the additional cylinder 10, and an engine block having only six cylinders 8 of one pair of crankshafts 1 is constituted.
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 drive shaft 4 and the piston 7 in the cylinder 8 is the same as the operation of the various components on each drive shaft 4 and the piston 7 in the cylinder 8 of the first embodiment.
Third embodiment of the invention:
as shown in fig. 12, the additional cylinder 10 is provided with a water pump cylinder 19 having a plunger 15, both ends of a driving rack 6 engaged with each driving gear 5 are connected to the plunger 15 in each water pump cylinder 19, a main journal 101 of the crankshaft 1 outside the crankcase 9 is connected to a rotating shaft 18 of a motor 17 through a connecting mechanism 16, and torque output from the rotating shaft 18 of the motor 17 converts the reciprocating linear motion of the plunger in the water pump.
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.
Claims (8)
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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811035309.9A CN110878820A (en) | 2018-09-06 | 2018-09-06 | Swing rack-crankshaft switching mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811035309.9A CN110878820A (en) | 2018-09-06 | 2018-09-06 | Swing rack-crankshaft switching mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110878820A true CN110878820A (en) | 2020-03-13 |
Family
ID=69727708
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811035309.9A Pending CN110878820A (en) | 2018-09-06 | 2018-09-06 | Swing rack-crankshaft switching mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110878820A (en) |
-
2018
- 2018-09-06 CN CN201811035309.9A patent/CN110878820A/en active Pending
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