CN116464751A - Chute-gear and rack transmission mechanism - Google Patents
Chute-gear and rack transmission mechanism Download PDFInfo
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- CN116464751A CN116464751A CN202210029488.5A CN202210029488A CN116464751A CN 116464751 A CN116464751 A CN 116464751A CN 202210029488 A CN202210029488 A CN 202210029488A CN 116464751 A CN116464751 A CN 116464751A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 53
- 230000033001 locomotion Effects 0.000 claims abstract description 41
- 230000006835 compression Effects 0.000 claims description 3
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- 238000000034 method Methods 0.000 claims description 2
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000009347 mechanical transmission Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
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Classifications
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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
- F02B75/40—Other reciprocating-piston engines
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- Combustion & Propulsion (AREA)
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Abstract
The invention relates to a chute-gear and rack transmission mechanism, a main shaft is arranged on one side wall of a support and a shell, a sector gear is arranged at the end part of the main shaft on one side of the support, a rotating arm is arranged on one side surface of the sector gear, one side surface of an A rack is connected with one side surface of a B rack by virtue of an A short cross beam, a concave chute and a B short cross beam, a guide cylinder on the rotating arm alternately enters and slides out of the concave chute, the sector gear is alternately meshed with the A rack and the B rack, a plurality of transmission shafts and two positioning shafts are sequentially arranged on the side wall of the shell on two sides of the main shaft, a transmission gear is arranged on each transmission shaft, a positioning gear is arranged on each positioning shaft, each two adjacent transmission gears are meshed with two tooth surfaces of a double-sided rack, and each positioning gear is meshed with an adjacent double-sided rack; one end or two ends of the rack A, the rack B and the double-sided racks are connected with pistons in each cylinder body on the shell through connecting rods, and the reciprocating linear motion of each piston is converted into the rotary motion of the main shaft by the mechanism.
Description
Technical Field
The present invention relates to a mechanical transmission mechanism for converting reciprocating linear motion of a piston into circular motion of a crankshaft, particularly to a chute-gear and rack transmission mechanism for replacing the existing crankshaft (handle) -connecting rod transmission mechanism.
Background
Currently, a crankshaft-connecting rod mechanism is generally adopted in a piston type internal combustion engine (engine) to convert the reciprocating linear motion of a piston into circular motion, however, the crankshaft-connecting rod mechanism has some defects which are difficult to overcome, and needs to be further improved and optimized:
1. in the traditional crankshaft connecting rod mechanism, acting force on a piston can be converted into tangential force for driving the crankshaft crank to rotate through multiple decomposition, theoretical analysis and practical application tests show that the maximum acting force acting on the piston is only about twenty percent decomposed into tangential force for driving the crankshaft crank to rotate, namely, only about one fifth of the maximum acting force drives the crankshaft to output maximum torque, otherwise, the maximum rotational inertia force of the crankshaft is only about one fifth of the acting force for driving the piston to reciprocate, so that the efficiency of converting reciprocating linear motion of the piston into circular motion by the traditional crankshaft connecting rod mechanism is very low;
2. in the traditional crankshaft (handle) connecting rod mechanism, the acting force on the piston is decomposed into acting force along the axis direction of the connecting rod and lateral pressure acting on the cylinder wall, the lateral friction force between the piston and the cylinder wall is increased by the lateral pressure acting on the cylinder wall, lateral abrasion of the cylinder wall is accelerated, the piston cannot work due to 'clamping' of the cylinder, and the service life of the cylinder is shortened;
3. unbalanced rotary mass and rotary motion generated by the swinging of the connecting rod in the traditional crankshaft connecting rod mechanism enable the transmission mechanism to generate alternating impact force, uneven friction and impact among all components are increased, the output power of the engine is affected, 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 slide-pinion and rack gear mechanism.
Disclosure of Invention
The main parts of the chute-gear and rack transmission mechanism provided by the invention comprise: the main shaft and the sector gear and the rotating arm which are arranged on the cylindrical surface of the main shaft, the A rack and the B rack, the concave sliding groove between the A rack and the B rack, the transmission shaft and the transmission gear which are arranged on the cylindrical surface of the transmission shaft, the double-sided rack, the positioning shaft and the positioning gear which are arranged on the cylindrical surface of the positioning shaft. A sector gear coaxial with the main shaft is arranged on a cylindrical surface at one end part of the main shaft, a support is arranged at one side surface close to the sector gear, the support is arranged on the inner wall of the shell, and the main shaft is arranged on the support and one side wall of the shell and extends to the outer side of the shell; a rotating arm is arranged on the cylindrical surface of the main shaft on the other side surface of the sector gear, a guide cylinder is arranged at the other end part of the rotating arm, and the axis of the guide cylinder is parallel to the axis of the main shaft; the gear sector can be alternately meshed with the short tooth surface A of the gear A and the short tooth surface B of the gear B; a concave chute formed by an A ledge, a B ledge and a bottom plate is arranged between the A rack and the B rack, and one side of the A rack is connected with one side of the B rack by virtue of an A short beam, the concave chute and a B short beam; the guide cylinder can enter and slide out of the opening end A and the opening end B of the concave chute repeatedly, and the guide cylinder drives the rack A and the rack B to do reciprocating linear motion by virtue of the concave chute; the transmission shafts and the two positioning shafts are respectively and sequentially arranged on two side walls of the shell at two sides of the main shaft, the cylindrical surface of each transmission shaft is respectively provided with a transmission gear, the A long tooth surface of the A rack and the B long tooth surface of the B rack are respectively meshed with the matched transmission gears, and other adjacent transmission gears are meshed with the two tooth surfaces of the double-sided rack; the two positioning gears are respectively meshed with the double-sided racks arranged at the outermost sides; one end or two ends of the A rack and one end or two ends of the B rack are connected with pistons in corresponding cylinder bodies on the shell through connecting rods, one end or two ends of each double-sided rack is also connected with the piston in the cylinder body on the shell through the connecting rods, and the reciprocating linear motion of each piston is converted into the rotary motion of the sector gear, otherwise, the rotary motion of the sector gear is converted into the reciprocating linear motion of each piston.
A rack is a double-sided rack formed by a short tooth surface A and a long tooth surface A, a rack B is a double-sided rack formed by a short tooth surface B and a long tooth surface B, the shapes of the rack A and the rack B are the same, the tooth surface of the rack A is parallel to the tooth surface of the rack B, and the effective lengths of the short tooth surface A of the rack A and the short tooth surface B of the rack B are equal to the length of the arc tooth surface of the sector gear; the length of the A long tooth surface of the A rack and the length of the B long tooth surface of the B rack are at least equal to the stroke of each piston.
A slide groove-gear and rack transmission mechanism, wherein, the concave slide groove is the slide groove that the cross section shape that comprises A ledge and B ledge and bottom plate is "concave" font and both ends open-ended, and two open ends of concave slide groove are A open end and B open end respectively, and the length of A ledge and B ledge and bottom plate are equal, and the width equals the diameter of guide cylinder between the inner wall of A ledge and B ledge of concave slide groove, and the height of A ledge and B ledge is slightly greater than the height of guide cylinder, and the height of A spliced pole and B spliced pole is equal to the sum of the height of guide cylinder and rotor arm thickness at least, and the well parting line of concave slide groove can be orthogonal or the skew with A short tooth face and B short tooth face.
A chute-gear and rack transmission mechanism, wherein, one end of an A short beam on one side of a middle branching line of a concave chute is rigidly connected with a bottom plate, the other end of the A short beam is rigidly connected with one end of an A connecting column, the other end of the A connecting column is rigidly connected with one side of an A rack, one end of a B short beam on the other side of the middle branching line is rigidly connected with the bottom plate, the other end of the B short beam is rigidly connected with one end of the B connecting column, the other end of the B connecting column is rigidly connected with one side of the B rack, the shapes of the A short beam and the B short beam are the same, and the distance from the left end head of an A ledge to the left end tooth of the A rack short tooth surface is equal to the distance from the right end head of the B ledge to the right end tooth of the B rack short tooth surface.
A slide-pinion and rack gear mechanism in which the axis of the main shaft, the axis of each drive shaft and the axis of the positioning shaft are all parallel to each other and lie in the same plane, which is orthogonal to the tooth face of the A-rack.
A chute-gear and rack drive mechanism wherein, if the guide cylinder is at the very middle of the concave chute, the a and B rack ends and the pistons at each double-sided rack end are at the top and bottom dead centers of their travel, respectively; when the guide cylinder passes through the middle of the concave sliding groove, the guide cylinder drives the end part of the rack A and the end part of the rack B and the piston of each double-sided rack end part to start to move towards the bottom dead center and the top dead center by virtue of the concave sliding groove, and when the guide cylinder slides out of the opening end of the concave sliding groove, the short tooth surface B of the rack B is meshed with the sector gear, and the end part of the rack A and the end part of the rack B and the piston of each double-sided rack end part continue to move towards the bottom dead center and the top dead center; when the short tooth surface B of the rack B is separated from the sector gear, the guide cylinder enters the concave chute from the opening end B, and when the guide cylinder reaches the middle of the concave chute, the end parts of the rack A and the rack B and the piston at the end part of each double-sided rack reach the bottom dead center and the top dead center of the stroke respectively; when the guide cylinder passes through the middle of the concave sliding groove, the guide cylinder drives the end part of the rack A and the end part of the rack B and the piston of each double-sided rack end part to start to move towards the upper dead point and the lower dead point by virtue of the concave sliding groove, when the guide cylinder slides out of the opening end A of the concave sliding groove, the short tooth surface A of the rack A is meshed with the sector gear, and the end part of the rack A and the end part of the rack B and the piston of each double-sided rack end part continue to move towards the upper dead point and the lower dead point; when the A short tooth surface is separated from the sector gear, the guide cylinder enters the concave chute from the opening end of the A; when the guide cylinder reaches the middle of the concave chute again, the pistons of the A rack and the B rack end and the respective double-sided rack ends reach the top dead center and the bottom dead center of the travel thereof again and again, the mechanism repeatedly repeats the above movements, converts the reciprocating linear motion of each piston into the rotational motion of the main shaft and the sector gear, or converts the rotational motion of the main shaft and the sector gear into the reciprocating linear motion of each piston.
A chute-gear and rack transmission mechanism, wherein if each cylinder body is a cylinder of a gasoline engine or a diesel engine, a gasoline engine or a diesel engine set of a plurality of cylinder bodies can be formed; if the two ends of the A rack and the two ends of the B rack and the two ends of the double-sided rack are connected with the pistons in the corresponding cylinders on the shell through connecting rods, the opposite engine unit can be formed.
A slide groove-gear and rack transmission mechanism, wherein if a main shaft is connected with a motor or other power output equipment, each cylinder body is a compression cylinder body of a reciprocating compressor or a high-pressure pump, and a set of a plurality of compressors or a set of a plurality of high-pressure pumps driven by one main shaft can be formed.
The sliding groove-gear and rack transmission mechanism provided by the invention realizes the mutual conversion between the reciprocating linear motion and the circular motion, has more reasonable power transmission and motion conversion modes, overcomes the inherent defects in the traditional crankshaft connecting rod mechanism, and has the following main advantages:
1. according to the chute-gear and rack transmission mechanism, the explosive force acting on the piston is directly transmitted to the sector gear and the guide cylinder by virtue of the rack A, the rack B, the double-sided racks and the concave chute and drives the main shaft to rotate, and the torque output by the main shaft is increased compared with that output by the traditional crankshaft-connecting rod mechanism;
2. in the transmission mechanism, the A rack, the B rack and each double-sided rack connected with the piston perform reciprocating linear motion by virtue of the sector gear and the transmission gear, so that the lateral pressure between the piston and the cylinder wall caused by the swinging of the connecting rod and the abrasion of the cylinder wall caused by the lateral pressure in the traditional crankshaft-connecting rod mechanism are thoroughly eliminated, the service life of the cylinder can be effectively prolonged, and the power conversion efficiency of the transmission mechanism is further improved;
3. in the transmission mechanism, the rack A, the rack B and each double-sided rack perform reciprocating linear motion, so that unbalanced rotary motion and alternating impact force caused by swinging of a connecting rod in the traditional crankshaft connecting rod mechanism are avoided, uneven friction and impact among all parts are eliminated, larger vibration and noise generated by an engine are reduced, and the engine runs more stably;
4. in the transmission mechanism, a plurality of transmission shafts, transmission gears matched with the transmission shafts and double-sided racks can be arranged, one end part or two end parts of each double-sided rack can be connected with a piston in a cylinder body arranged on a shell, so that a multi-cylinder super-power engine unit is formed, a crank connecting rod type engine unit with a plurality of cylinders can save a plurality of crank throws, the volume of the engine unit is reduced, and the output power of the engine unit is improved.
5. The transmission mechanism of the invention can also be used for any mechanical equipment which converts rotary motion into reciprocating linear motion, such as plunger type oil, gas, water pump, reciprocating compressor and the like.
The sliding groove-gear and rack transmission mechanism is an innovative mechanical mechanism which has reasonable structure and smooth operation and is capable of mutually converting reciprocating linear motion and circular motion, and compared with the traditional crankshaft-connecting rod mechanism, the mechanical transmission efficiency of the mechanism is obviously improved.
In summary, the chute-gear and rack transmission mechanism of the invention is innovative and meets the conditions of patent rights granted in the patent laws, and therefore, patent applications are filed.
Drawings
FIG. 1 is a schematic cross-sectional elevation of a transmission a-a of the present invention;
FIG. 2 is a schematic cross-sectional elevation view of the transmission B-B of the present invention;
FIG. 3 is a schematic top view of a section C-C of the transmission mechanism of the present invention;
FIG. 4 is a schematic right-hand cross-sectional view of the transmission D-D of the present invention;
FIG. 5 is a schematic cross-sectional right side view of the transmission E-E of the present invention;
FIG. 6 (a) is a schematic cross-sectional view of a concave chute F-F according to the present invention;
FIG. 6 (b) is a schematic left-hand view of FIG. 6 (a);
FIG. 7 (a) is a schematic view of the spindle and the sector gear and rotating arm provided on the cylindrical surface thereof according to the present invention;
FIG. 7 (b) is a schematic left-hand view of FIG. 7 (a);
FIG. 8 is a schematic view of the connection of the A rack, the B rack and the concave chute of the invention;
FIG. 9 is a schematic view of the rack A, rack B and their associated pistons of the present invention at top dead center;
FIG. 10 is a schematic view of the rack A, rack B and their associated pistons of the present invention beginning to move toward bottom dead center;
FIG. 11 is a schematic view of the rack A, rack B and their associated pistons of the present invention about to reach bottom dead center;
FIG. 12 is a schematic view of the rack A, rack B and their associated pistons of the present invention beginning to move toward top dead center;
FIG. 13 is a schematic view of the rack A, rack B and their associated pistons of the present invention about to reach top dead center;
FIG. 14 is a schematic view of an opposed cylinder configuration of the present invention;
fig. 15 is a schematic diagram of the connection of the transmission mechanism of the present invention to a power plant.
Detailed Description
The following describes in detail an embodiment of a chute-gear and rack transmission mechanism provided by the invention with reference to the accompanying drawings.
The first embodiment of the present invention is as follows:
as shown in fig. 1, 2, 3, 4, 5, the main driving members comprise: the main shaft 1 and the transmission shaft 5 and the transmission gear 501 on the cylindrical surface thereof, the sector gear 101 and the rotating arm 102 thereof, the A rack 2 and the B rack 2 'and the concave chute 3 between the A rack 2 and the B rack 2', the positioning shaft 6 and the positioning gear 601 arranged on the cylindrical surface thereof. A sector gear 101 coaxial with the sector gear is arranged on a cylindrical surface of one end part of the spindle 1, the spindle 1 close to one side surface of the sector gear 101 is arranged on a support 104, the support 104 is arranged on the inner wall of a shell 9, the other end of the spindle 1 is arranged on one side wall of the shell 9 and extends to the outer side of the shell 9, a rotating arm 102 is arranged on the other side surface of the sector gear 101, a guide cylinder 103 is arranged at the end part of the rotating arm 102, the sector gear 101 is respectively and alternately meshed with an A short tooth surface 202 of an A rack 2 and a B short tooth surface 202 'of a B rack 2', one side surface of the A rack 2 is connected with one side surface of the B rack 2 'by virtue of an A short beam 306 and a concave chute 3, and the B short beam 306', the guide cylinder 103 can repeatedly enter and slide out of an A opening end 305 and a B opening end 305 'of the concave chute 3, and the guide cylinder 103 drives the A rack 2 and the B rack 2' to perform reciprocating linear motion by virtue of the concave chute 3; the two transmission shafts 5 and the two positioning shafts 6 are respectively and sequentially arranged on two side walls of a shell 9 on two sides of the main shaft 1, transmission gears 501 are respectively arranged on cylindrical surfaces of the two transmission shafts 5, and an A long tooth surface 203 of the A rack 2 and a B long tooth surface 203 'of the B rack 2' are respectively meshed with the matched transmission gears 501; the two positioning gears 601 are engaged with the double-sided racks 502 arranged at the outermost sides, respectively.
As shown in fig. 1 and 8, the a rack 2 is a double-sided rack formed by an a short tooth surface 202 and an a long tooth surface 203, the B rack 2' is a double-sided rack formed by a B short tooth surface 202' and a B long tooth surface 203', the a rack 2 and the B rack 2' have the same shape, the tooth surfaces of the a rack 2 are parallel to the tooth surfaces of the B rack 2', and the effective lengths of the short tooth surfaces 202 and 202' of the a rack 2 and the B rack 2' are equal to the lengths of the circular arc tooth surfaces of the sector gear 101; the length of the long flanks 203 of the a-rack 2 and the length of the long flanks 203 'of the B-rack 2' and the tooth flank length of the double-sided rack 502 are at least equal to the stroke of each piston 7.
As shown in fig. 6 (a) and 6 (B), the concave chute 3 is a chute formed by an a ledge 301, a B ledge 301 'and a bottom plate 302, the cross-sectional shape of which is a "concave" shape, and the two ends of the concave chute 3 are respectively an a open end 305 and a B open end 305', the lengths of the a ledge 301, the B ledge 301 'and the bottom plate 302 are equal, the width between the inner walls of the a ledge 301 and the B ledge 301' of the concave chute 3 is equal to the diameter of the guide cylinder 103, the heights of the a ledge 301 and the B ledge 301 'are slightly larger than the height of the guide cylinder 103, and the heights of the a connecting post 304 and the B connecting post 304' are at least equal to the sum of the height of the guide cylinder 103 and the thickness of the rotating arm 102.
As shown in fig. 8, one end of an a short beam 306 on one side of a middle branching line 300 of a concave chute 3 is rigidly connected to a bottom plate 302, the other end of the a short beam 306 is rigidly connected to one end of an a connecting post 304, the other end of the a connecting post 304 is rigidly connected to one side of an a rack 2, one end of a B short beam 306 'on the other side of the middle branching line 300 is rigidly connected to the bottom plate 302, the other end of the B short beam 306' is rigidly connected to one end of a B connecting post 304', the other ends of the B connecting posts 304' are rigidly connected to one side of a B rack 2', the a short beam 306 and the B short beam 306' are identical in shape, and the distance from a left end 307 of an a ledge 301 to a left end tooth 201 of an a rack 2 short tooth 201 is equal to the distance from a right end 307 'of a ledge 301' to a right end tooth 201 'of a B rack 2' short 202', and the middle branching line 300 of the chute 3 is orthogonal to the a short tooth 202 and the B short tooth 202'.
As shown in fig. 7, the axis of the guide cylinder 103 is parallel to the axis 100 of the spindle 1.
As shown in fig. 1, the axis 100 of the main shaft 1, the axis of each drive shaft 5, and the axis of the positioning shaft 6 are all parallel to each other and lie in the same plane, which is orthogonal to the tooth surface of the a-rack 2.
As shown in fig. 1 and 9 to 13, the guide cylinder 103 can repeatedly enter from the a-opening end 305 of the concave chute 3 and slide out from the B-opening end 305 'of the concave chute 3, and then enter from the B-opening end 305' of the concave chute 3 and slide out from the a-opening end 305 of the concave chute 3.
As shown in fig. 1, one end of the same side of the rack a 2, the rack B2' and the double-sided rack 502 is connected with the piston 7 in the corresponding cylinder 8 on the housing 9 through the connecting rod 204, and the reciprocating linear motion of each piston 7 is converted into the rotary motion of the sector gear 101, whereas the rotary motion of the sector gear 101 is converted into the reciprocating linear motion of each piston 7.
The operation of the first embodiment of the present invention is as follows:
first, as shown in fig. 9, when the guide cylinder 103 on the rotating arm 102 enters from the B opening end 305 'of the concave chute 3 and slides clockwise to the right middle of the concave chute 3, the two pistons 7 connected to the end connecting rod 204 of the a-rack 2 and the B-rack 2' move to the top dead center, and the two pistons 7 connected to the end connecting rod 204 of the double-sided rack 502 move to the bottom dead center.
In the second step, as shown in fig. 10, the spindle 1 and the sector gear 101 thereof drive the rotating arm to rotate clockwise under the action of the rotational inertia couple, the guiding cylinder 103 on the rotating arm 102 slides out from the opening end 305 of the concave chute 3, the sector gear 101 starts to mesh with the short tooth surface 202 of the rack a 2, the two pistons 7 located at the top dead center are in gas burst in the cylinder 8, the gas burst force acting on the corresponding pistons 7 drives the spindle 1 to rotate clockwise by means of the rack a 2, the rack B2', the concave chute 3 and the sector gear 101, the two pistons 7 at the top dead center start to move to the bottom dead center, and the two pistons 7 at the bottom dead center start to move to the top dead center.
In the third step, as shown in fig. 11, when the sector gear 101 is disengaged from the short tooth face 202 of the a-rack 2, the guide cylinder 103 on the rotating arm 102 slides into the concave chute 3 from the a-opening end 305 of the concave chute 3, the piston 7 connected with the a-rack 2 and the B-rack 2' is about to reach the bottom dead center, and the piston 7 connected with the double-sided rack 502 is about to reach the top dead center.
Fourth, as shown in fig. 1, when the guide cylinder 103 on the rotating arm 102 slides clockwise to the middle of the concave chute 3, the two pistons 7 connected with the a rack 2 and the B rack 2' move to the bottom dead center, and the two pistons 7 connected with the double-sided rack 502 move to the top dead center.
Fifth, as shown in fig. 12, the main shaft 1 and the sector gear 101 thereof drive the rotating arm to rotate clockwise under the action of the rotational inertia couple, the guiding cylinder 103 on the rotating arm 102 slides out from the opening end 305 'of the concave chute 3, the sector gear 101 starts to mesh with the short tooth surface 202' of the B rack 2', the two pistons 7 located at the top dead center are in gas burst in the cylinder 8, the double-sided rack 502 meshed with the transmission gear 501 is driven to move in the direction of the bottom dead center by the gas burst force acting on the corresponding piston 7, and the main shaft 1 is driven to rotate clockwise by the a rack 2 and the B rack 2' meshed with the transmission gear 501 and the concave chute 3 and the sector gear 101 simultaneously, the two pistons 7 at the top dead center start to move in the direction of the bottom dead center, and the two pistons 7 at the bottom dead center start to move in the direction of the top dead center.
Sixth, as shown in fig. 13, when the sector gear 101 is disengaged from the short tooth face 202 'of the B rack 2', the guide cylinder 103 on the rotating arm 102 slides into the concave chute 3 from the B opening end 305 'of the concave chute 3, the piston 7 connected with the a rack 2 and the B rack 2' is about to reach the top dead center, and the piston 7 connected with the double-sided rack 502 is about to reach the bottom dead center.
Seventh, as shown in fig. 9, the guide cylinder 103 on the rotating arm 102 slides clockwise to the right middle position of the concave chute 3 again, the two pistons 7 connected with the a rack 2 and the B rack 2' move to the upper dead point again, the two pistons 7 connected with the double-sided rack 502 move to the lower dead point again, and each moving machine part of the chute-gear and rack transmission mechanism of the invention repeatedly repeats the operation process from the first step to the sixth step, and the reciprocating linear motion of the pistons 7 is converted into the rotation of the main shaft 1.
The second embodiment of the present invention is different from the first embodiment in that:
as shown in fig. 14, the long tooth surface 203 of the a-rack 2 and the long tooth surface 203' of the B-rack 2' are respectively engaged with positioning gears on the positioning shafts 6, and both ends of the a-rack 2 and both ends of the B-rack 2' are respectively connected with pistons 7 in corresponding cylinders 8 on the housing 9 through connecting rods 204, so as to constitute an opposed four-cylinder engine unit.
The operation of the second embodiment of the present invention is the same as that of the first embodiment of the present invention.
The third embodiment of the present invention is different from the first embodiment in that:
as shown in fig. 15, the main shaft 1 is connected to a motor 10, and each cylinder 8 is a compression cylinder of a reciprocating compressor 11 or a high-pressure pump 12, that is, a set of a plurality of compressors 11 or a set of a plurality of high-pressure pumps 12 driven by one main shaft 1.
The operation of the third embodiment of the present invention is the reverse of the operation of the first embodiment of the present invention.
The above embodiments of the transmission mechanism of the present invention are not limited to the practical scope of the transmission mechanism of the present invention, and those skilled in the art can make various modifications and improvements to the technical solution of the present invention without departing from the design of the present invention, and all the modifications and improvements fall within the protection scope of the present invention as defined in the claims.
Claims (8)
1. The main machine parts comprise a main shaft (1), a transmission shaft (5) and a transmission gear (501) thereof, a sector gear (101) and a rotating arm (102) thereof, a concave chute (3) between an A rack (2) and a B rack (2'), a positioning shaft (6) and a positioning gear (601) arranged on a cylindrical surface of the positioning shaft; the method is characterized in that: a main shaft (1) is arranged on one side wall of the shell (9) and a support (104) on the inner wall of the shell (9), one end part of the main shaft (1) is rigidly connected with one side surface of the sector gear (101), the axis (100) of the main shaft (1) is collinear with the central axis of the sector gear (101), one side surface of the sector gear (101) is close to the support (104), and the main shaft (1) extends to the outer side of the shell (9); a rotating arm (102) is arranged on the other side surface of the sector gear (101), a guide cylinder (103) is arranged at one end part of the rotating arm (102), and the axis (105) of the guide cylinder (103) is parallel to the axis (100) of the main shaft (1); one side of the A rack (2) is connected with one side of the B rack (2 ') by virtue of the A short cross beam (306) and the concave sliding groove (3) and the B short cross beam (306'), the sector gear (101) is respectively and alternately meshed with the A short tooth surface (202) of the A rack (2) and the B short tooth surface (202 ') of the B rack (2'), and the guide cylinder (103) alternately enters and slides out of the A opening end (305) and the B opening end (305 ') of the concave sliding groove (3), so that the reciprocating linear motion of the A rack (2) and the B rack (2') is converted into the circular motion of the sector gear (101); the transmission shafts (5) and the two positioning shafts (6) are respectively and sequentially arranged on two side walls of the shell (9) on two sides of the main shaft (1), the cylindrical surface of each transmission shaft (5) is respectively provided with a transmission gear (501), the A long tooth surface (203) of the A rack (2) and the B long tooth surface (203 ') of the B rack (2') are respectively meshed with the matched transmission gears (501), and other adjacent transmission gears (501) are meshed with two tooth surfaces of the double-sided rack (502); the two positioning gears (601) are respectively meshed with the double-sided racks (502) arranged at the outermost side; one end or two ends of the A rack (2) and one end or two ends of the B rack (2'), and one end or two ends of each double-sided rack (502) are respectively connected with pistons (7) in corresponding cylinder bodies (8) on the shell (9) through connecting rods (204), and the mechanical structure converts the reciprocating linear motion of each piston (7) into the rotary motion of the main shaft (1) and the sector gear (101), and conversely, converts the rotary motion of the main shaft (1) and the sector gear (101) into the reciprocating linear motion of each piston (7).
2. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: the A rack (2) is a double-sided rack formed by an A short tooth surface (202) and an A long tooth surface (203), the B rack (2 ') is a double-sided rack formed by a B short tooth surface (202 ') and a B long tooth surface (203 '), the shapes of the A rack (2) and the B rack (2 ') are the same, the tooth surfaces of the A rack (2) are parallel to the tooth surfaces of the B rack (2 '), and the effective lengths of the A short tooth surface (202) of the A rack (2) and the B short tooth surface (202 ') of the B rack (2 ') are equal to the lengths of the arc tooth surfaces of the sector gear (101); the length of the A long tooth surface (203) of the A rack (2) and the length of the B long tooth surface (203 ') of the B rack (2') and the tooth surface length of the double-sided rack (502) are at least equal to the stroke of each piston (7).
3. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: the concave chute (3) is a chute with two open ends, wherein the cross section of the chute is in a concave shape, the two open ends of the chute are respectively an A open end (305) and a B open end (305 '), the lengths of the A chute (301), the B chute (301') and the bottom plate (302) are equal, the width between the inner walls of the A chute (301) and the B chute (301 ') of the concave chute (3) is equal to the diameter of the guide cylinder (103), the height of the A chute (301) and the B chute (301') is slightly larger than the height of the guide cylinder (103), the height of the A connecting column (304) and the B connecting column (304 ') is at least equal to the sum of the height of the guide cylinder (103) and the thickness of the rotating arm (102), and the middle branching line (300) of the concave chute (3) can be orthogonal or oblique to the A short tooth surface (202) and the B short tooth surface (202').
4. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: an end of an A short beam (306) on one side of a middle branching line (300) of the concave chute (3) is rigidly connected with the bottom plate (302), the other end of the A short beam (306) is rigidly connected with one end of an A connecting column (304), the other end of the A connecting column (304) is rigidly connected with one side surface of an A rack (2), the one end of a B short beam (306 ') on the other side of the middle branching line (300) is rigidly connected with the bottom plate (302), the other end of the B short beam (306') is rigidly connected with one end of a B connecting column (304 '), the other end of the B connecting column (304') is rigidly connected with one side surface of a B rack (2 '), the shapes of the A short beam (306) and the B short beam (306') are the same, the distance from the left end (307) of an A chute (301) to the left end tooth (201) of the A rack (2) is equal to the distance from the right end (307 ') of the B chute (301') to the right end tooth (201 ') of the short tooth surface (202'), the guide cylinder (103) is circumferentially and slides out of the concave chute (305) from the opening (305) to the opening (3) from the opening (305) to the opening (305) from the opening (3) to the opening (B) to slide out of the opening (305).
5. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: the axis (100) of the main shaft (1), the axis of each transmission shaft (5) and the axis of the positioning shaft (6) are all parallel to each other and are located on the same plane, and the plane is orthogonal to the tooth surface of the A rack (2).
6. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: if each cylinder body (8) is a cylinder of a gasoline engine or a diesel engine, the gasoline engine or the diesel engine set of a plurality of cylinder bodies (8) can be formed.
7. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: if both ends of the A rack (2) and both ends of the B rack (2') and both ends of the double-sided rack (502) are respectively connected with the pistons (7) in the corresponding cylinders (8) on the shell (9) through connecting rods (204), an opposite engine unit can be formed.
8. A spout-pinion and rack drive mechanism as claimed in claim 1, characterized in that: if the main shaft (1) is connected with a motor (10) or other power output equipment, each cylinder body (8) is a compression cylinder body of a reciprocating compressor (11) or a high-pressure pump (12), a set of a plurality of compressors (11) or a set of a plurality of high-pressure pumps (12) driven by one main shaft (1) can be formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210029488.5A CN116464751A (en) | 2022-01-12 | 2022-01-12 | Chute-gear and rack transmission mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210029488.5A CN116464751A (en) | 2022-01-12 | 2022-01-12 | Chute-gear and rack transmission mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116464751A true CN116464751A (en) | 2023-07-21 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210029488.5A Pending CN116464751A (en) | 2022-01-12 | 2022-01-12 | Chute-gear and rack transmission mechanism |
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| CN (1) | CN116464751A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116651534A (en) * | 2023-07-31 | 2023-08-29 | 延边大学 | Separated noise-reducing and vibration-absorbing optical platform for patch clamp experiment |
-
2022
- 2022-01-12 CN CN202210029488.5A patent/CN116464751A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116651534A (en) * | 2023-07-31 | 2023-08-29 | 延边大学 | Separated noise-reducing and vibration-absorbing optical platform for patch clamp experiment |
| CN116651534B (en) * | 2023-07-31 | 2023-10-20 | 延边大学 | Separated noise-reducing and vibration-absorbing optical platform for patch clamp experiment |
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